CN110159707A - Axle driving device - Google Patents
Axle driving device Download PDFInfo
- Publication number
- CN110159707A CN110159707A CN201811579398.3A CN201811579398A CN110159707A CN 110159707 A CN110159707 A CN 110159707A CN 201811579398 A CN201811579398 A CN 201811579398A CN 110159707 A CN110159707 A CN 110159707A
- Authority
- CN
- China
- Prior art keywords
- gear
- pinion gear
- axle
- ladder
- driving device
- 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
Classifications
-
- 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
-
- 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
-
- 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
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The present invention provides a kind of axle driving device, in planetary gear reducing mechanism, in the case where obtaining high reduction ratio, it is necessary to make planetary gear high speed rotation, thus need the countermeasure for resulting high-frequency vibration.Therefore, in view of above-mentioned previous disadvantage, project is to provide the axle driving device that high reduction ratio can be obtained and be not susceptible to high-frequency vibration.In axle driving device of the invention, into the 1st axle (5) and the driving force transmission path of the planet-shaped deceleration mechanism (3) of the 2nd axle (6) transmitting driving force, there are the multiple stepped gears (31,32) for being connected in series and slowing down by differential attachment (4).
Description
Technical field
The present invention relates to a kind of axle driving devices.
Background technique
In the axle driving device using electric motor, it is known that subtracted using power of the deceleration mechanism to electric motor
Speed and the axle driving device for being transferred to output shaft.
Also, in deceleration mechanism, in order to obtain high reduction ratio with small-scale structure, planetary gear reducing mechanism has been used.
In addition, as shown in Patent Document 1, it is known that higher reduction ratio in order to obtain, planetary gear reducing mechanism use two
The structure of grade gear.
Patent document 1: Japanese Unexamined Patent Publication 2009-36365 bulletin.
Summary of the invention
However, in planetary gear reducing mechanism, in the case where obtaining high reduction ratio, it is necessary to revolve planetary gear high speed
Turn, thus needs the countermeasure for resulting high-frequency vibration.
In the structure shown in patent document 1, also for using vehicle etc. to obtain sufficient reduction ratio, it is necessary to make planet tooth
Take turns high speed rotation.
In view of above-mentioned previous disadvantage, the object of the present invention is to provide obtain high reduction ratio and be not susceptible to high frequency
The axle driving device of vibration.
It is a feature of the present invention that subtracting by differential gearing to the planet-shaped of the 1st axle and the 2nd axle transmitting driving force
In the driving force transmission path of fast mechanism, there are the multiple stepped gears for being connected in series and slowing down.
As a result, by engaging the big side gear of stepped gear with the small side gear of other stepped gears, driving force is subtracted
Speed.Further, since having used makes big side gear and stepped gear that small side gear is integrated, the case where with independent gear is used
It compares, saves space.
In addition, the present invention can be, the driving force transmission path of planet-shaped deceleration mechanism is by means of the multiple rank
Terraced gear and turn back on the extending direction of the support shaft in the stepped gear.
Engage the big side gear of stepped gear with the small side gear of other stepped gears, by other stepped gears
Big side gear configuration stepped gear previous small side, thus complete repeatedly to slow down in the width of stepped gear.
In addition, the present invention can be, the stepped gear in the downstream side of the power transfer path of planet-shaped deceleration mechanism
It is engaged by planetary gear with the gear ring of planet-shaped deceleration mechanism.
As a result, with the allocation position of the stepped gear in downstream side accordingly distributing planetary gear, the thus ladder in downstream side
The driving force of gear is passed to gear ring.
Furthermore, it is possible to be between the big side gear of the stepped gear in the planetary gear and the downstream side, to be provided with
The component for supporting one end of the planetary gear support shaft, on the rotating shaft direction of the 1st axle, the planetary gear
Support shaft be configured in the position being overlapped with the big side gear of the stepped gear in the downstream side.
The big side gear for avoiding the stepped gear in downstream side as a result, is contacted with planetary gear support shaft.
Furthermore, it is possible to be the big side tooth of the stepped gear of the sun gear and downstream side of planet-shaped deceleration mechanism
Wheel be staggered on the rotating shaft direction of the 1st axle, on the rotating shaft direction of the 1st axle, with the sun gear
The big side gear of the stepped gear in the downstream side is configured on the position of coincidence.
Thereby, it is possible to configure the stepped gear in downstream side close to the rotation axis of the 1st axle.
In addition, the present invention can be, it is arranged on the planetary gear bearing part of planet-shaped deceleration mechanism
There is oil circuit, which is arranged in the opposite side configured with the planetary gear side, is set to the described of the bearing part
Oil circuit is with the oil circuit in support shaft described in the planetary gear by the holding planetary gear branch of the bearing part
It holds the bearing portion of axis and connects.
As a result, in the opposite side with distributing planetary gear, no matter how planetary gear is configured, and is both provided with oil circuit.
Invention effect
The big axle driving device of reduction ratio can be obtained in axle driving device according to the present invention.Also, utilize multiple ranks
Terraced gear increases reduction ratio, therefore does not need to make planetary gear high speed rotation, can reduce planetary gear high speed rotation and cause
High-frequency vibration.
The turning moment of planet-shaped deceleration mechanism can be reduced, can compactly constitute axle driving device.
In addition, the driving force transmission path by means of the multiple stepped gear the stepped gear support shaft
It turns back on extending direction, driving force transmission path can be reduced according to this structure.Thereby, it is possible to reduce planet-shaped deceleration mechanism
Turning moment can compactly constitute axle driving device.
In addition, according to the stepped gear in the downstream side of the power transfer path by planetary gear and with the planet-shaped
The structure of the gear ring engagement of deceleration mechanism, can be improved the freedom degree in the configuration of gear.Thereby, it is possible to increase the rank in downstream side
Terraced gear, to obtain big retarding ratio.
In addition, being provided with bearing institute between the big side gear of the stepped gear in the planetary gear and the downstream side
The component for stating one end of planetary gear support shaft, on the rotating shaft direction of the 1st axle, the planetary gear bearing
Axis is configured in the position being overlapped with the big side gear of the stepped gear in the downstream side, according to this structure, the ladder in downstream side
Freedom degree in the configuration of gear is improved, further, it is possible to make the stepped gear enlargement in downstream side, to obtain big subtract
Speed ratio.
In addition, the big side gear of the sun gear of planet-shaped deceleration mechanism and the stepped gear in the downstream side is described
It is staggered on the rotating shaft direction of 1st axle, on the rotating shaft direction of the 1st axle, in the position being overlapped with the sun gear
The big side gear for configuring the stepped gear in the downstream side is set, according to this structure, the stepped gear in downstream side can be made close
The rotation axis of 1st axle and configure.Thereby, it is possible to reduce the turning moment of planet-shaped deceleration mechanism.
In addition, it is provided with oil circuit on the planetary gear bearing part of planet-shaped deceleration mechanism, the oil circuit
Opposite side configured with the planetary gear side is set, the oil circuit and the planet of the bearing part are set to
Oil circuit in the support shaft of gear by the bearing portion of the holding planetary gear support shaft of the bearing part and
Connection, thereby, it is possible to supply lubricating oil to planetary gear in simple structure.Thereby, it is possible to improve the resistance to of vehicle drive unit
Long property.
Detailed description of the invention
Fig. 1 is the main view for showing the axle driving device of the 1st embodiment of the invention.
Fig. 2 is the left view of axle driving device.
Fig. 3 is the cross-sectional view of the III-III line in Fig. 1.
Fig. 4 is the cross-sectional view of the IV-IV line in Fig. 1.
Fig. 5 is the cross-sectional view of the V-V line in Fig. 1.
Fig. 6 is the cross-sectional view of the line VI -- VI in Fig. 2.
Fig. 7 is the cross-sectional view of the VII-VII line in Fig. 2.
Fig. 8 is the skeleton drawing for schematically showing the structure of the axle driving device in the 1st embodiment.
Fig. 9 is the perspective view for showing the left side of axle driving device.
Figure 10 is the perspective view for showing the right side of axle driving device.
Figure 11 is the perspective view for showing the left side of planet carrier of the 1st embodiment of the invention.
Figure 12 is the main view of planet carrier.
Figure 13 is the perspective view for showing the right side of planet carrier.
Figure 14 is to show to assemble the perspective view of the state of pinion gear in planet carrier.
Figure 15 is the partial sectional view shown in the method for the 2nd ladder pinion gear of planet carrier over-assemble.
Figure 16 is the partial sectional view shown in the method for the 1st ladder pinion gear of planet carrier over-assemble.
Figure 17 is the perspective view for showing the lubricant passage way of planet carrier.
Figure 18 is the cross-sectional view for showing the lubricant passage way of the 1st ladder pinion gear.
Figure 19 is the perspective view for showing the left side of axle driving device of the 2nd embodiment of the invention.
Figure 20 is the perspective view for showing the right side of axle driving device of the 2nd embodiment.
Figure 21 is the main view of the axle driving device of the 2nd embodiment.
Figure 22 is the cross-sectional view of the XXII-XXII line in Figure 21.
Figure 23 is the cross-sectional view of the XXIII-XXIII line in Figure 21.
Figure 24 is the skeleton drawing for schematically showing the structure of the axle driving device in the 2nd embodiment.
Label declaration
1: axle driving device；
2: motor drive shaft；
3: planetary mechanism；
4: differential attachment；
5: the 1 axles；
6: the 2 axles；
7: planet carrier；
9: side plate；
21: sun gear；
31: the 1 ladder pinion gears；
31a: gear；
31b: gear；
32: the 2 ladder pinion gears；
32a: gear；
32b: gear；
33: outer pinion gear；
34: gear ring；
41: the 1 pinion gears；
42: the 2 pinion gears；
43: gear ring；
44: differential carrier；
51: gear.
Specific embodiment
Referring to the drawings, embodiments of the present invention will be described.
[embodiment 1]
Using Fig. 1 to Figure 10, illustrate the axle driving device 1 of embodiments of the present invention.
Fig. 1 is the main view for showing the axle driving device of the 1st embodiment of the invention, and Fig. 2 is axle driving device
Left view.Fig. 3 is the cross-sectional view of the III-III line in Fig. 1, and Fig. 4 is the cross-sectional view of the IV-IV line in Fig. 1.Also,
Fig. 5 is the cross-sectional view of the V-V line in Fig. 1.Also, Fig. 6 is the cross-sectional view of the line VI -- VI in Fig. 2, and Fig. 7 is along Fig. 2
The cross-sectional view of VII-VII line.
In addition, Fig. 8 is the skeleton drawing for schematically showing the structure of the axle driving device in the 1st embodiment.Also, scheme
9 be the perspective view for showing the left side of axle driving device, and Figure 10 is the perspective view for showing the right side of axle driving device.
Axle driving device 1 has differential attachment 4 and the planetary mechanism 3 as planet-shaped deceleration mechanism, drives in axle
The 1st axle 5 is connected on the left of device 1, and the 2nd axle 6 is connected on the right side of axle driving device 1.Also, axle driving device 1 and work
Motor drive shaft 2 for the input shaft of driving force connects, so that driving force is entered axle driving device 1.
The driving force inputted by motor drive shaft 2 is slowed down by planetary mechanism 3, and is output to the 1st axle via differential attachment 4
5 and the 2nd axle 6.
Motor drive shaft 2 is the hollow axis extended in left-right direction, and the 1st axle 5 is inserted into 2 inside of motor drive shaft.
It can be in the rotor of the outer peripheral surface of motor drive shaft 2 installation electric motor.Thereby, it is possible to directly drive motor drive shaft 2, and
And from pass through motor drive shaft 2 in 5 output driving power of the 1st axle.
In addition it is possible to input driving force to motor drive shaft 2 by other structures.
Next, being described in detail using Fig. 3 to Fig. 7 to the internal structure of axle driving device 1.
The planetary mechanism 3 of axle driving device 1 is small by sun gear 21, the 1st ladder that one end of motor drive shaft 2 is arranged in
Gear 31, the 2nd ladder pinion gear 32, outer pinion gear 33, gear ring 34 and planet carrier 7 are constituted.
1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 are planetary gears.
1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 are respectively arranged with 3, at equal intervals
Configuration is around motor drive shaft 2.
In addition, planet carrier 7 is made of differential carrier 44 and the side plate integrally fixed by stay with substrate plate 70 9.?
On side plate 9, cover board 8 is installed using 3 fastening points 81.
In addition, stay by be respectively arranged with 3 the 1st stay 71, the 2nd stay 72, the 3rd stay 73, the 4th stay 74 and
5th stay 75 is constituted.
Planet carrier 7 rotatably supports the 1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33.
Also, the rotary shaft of the 1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 is parallel with motor drive shaft 2
Ground configuration.
Gear with teeth is arranged in the outside that sun gear 21 is directed towards motor drive shaft 2, integrally turns with motor drive shaft 2
It is dynamic.Also, sun gear 21 is engaged with the gear wheel 31a of the 1st ladder pinion gear 31.
1st ladder pinion gear 31 has the gear wheel 31a and pinion gear 31b integrally rotated.Gear wheel 31a is big side tooth
Wheel, pinion gear 31b is small side gear.Also, the 1st ladder pinion gear 31 is supported by support shaft 31c in a rotatable manner, branch
Axis 31c is held to be supported by side plate 9 and differential carrier 44.
The gear wheel 31a and pinion gear 31b of 1st ladder pinion gear 31 are integrally rotated, and driving force is passed from pinion gear 31b
It is handed to the 2nd ladder pinion gear 32.
In addition, the gear wheel 31a configuration of the 1st ladder pinion gear 31 is left side in 9 side of side plate, pinion gear 31b is configured in difference
Fast 44 side of device shell is right side.
2nd ladder pinion gear 32 is made of the gear wheel 32a and pinion gear 32b integrally rotated, the 2nd ladder pinion gear 32
It is engaged by gear wheel 32a with the 1st ladder pinion gear 31.Gear wheel 32a is big side gear, and pinion gear 32b is small side gear.
Also, the 2nd ladder pinion gear 32 is supported by support shaft 32c in a rotatable manner, and support shaft 32c is by side plate 9
It is supported with differential carrier 44.In addition, the gear wheel 32a of the 2nd ladder pinion gear 32 is configured in 44 side of differential carrier, pinion gear 32b
Configuration is in 9 side of side plate.
The pinion gear 32b of 2nd ladder pinion gear 32 is engaged with outer pinion gear 33.Also, the outer configuration of pinion gear 33 is in side plate 9
Between substrate plate 70.
The end of the support shaft 33c of outer pinion gear 33 is supported by side plate 9 and substrate plate 70 respectively, and outer pinion gear 33 is supported
To rotate freely.
Also, as shown in figure 5 and figure 7, in the left and right directions observation along axle driving device 1, the branch of outer pinion gear 33
Axis 33c configuration is held in the position being overlapped with the gear wheel 32a of the 2nd ladder pinion gear 32.
In addition, the configuration of substrate plate 70 is between side plate 9 and differential carrier 44.Substrate plate 70 is on a left side for axle driving device 1
Configuration is between the gear wheel 31a of the 1st ladder pinion gear 31 and the gear wheel 32a of the 2nd ladder pinion gear 32 in right direction.
In addition, the support shaft 33c of outer pinion gear 33 centered on the rotation axis of planet carrier 7, is configured in tooth smaller than the 2nd ladder
The support shaft 32c of wheel 32 locates in the outer part.
Configured with the 1st stay 71 and the 2nd stay 72 extended from substrate plate 70 near outer pinion gear 33.Also,
Outer pinion gear 33 configures between the 1st stay 71 and the 2nd stay 72 on the direction of rotation of side plate 9.In addition, outer pinion gear 33 with
1st stay 71 and the 2nd stay 72 separate the gap for the gear clearance amount for being equivalent to outer pinion gear 33 and configure.
Also, outer pinion gear 33 is in the inside of gear ring 34 and the interior tooth engagement of gear ring 34.
Gear ring 34 configures between side plate 9 and differential carrier 44 in 9 side of side plate.Also, it is configured in the inside of gear ring 34
Pinion gear 32b, sun gear 21 and the outer pinion gear 33 of the gear wheel 31a of 1st ladder pinion gear 31, the 2nd ladder pinion gear 32.This
Outside, gear ring 34 is fixed using fixed cell (not shown) relative to axle driving device 1.For example, can be fixed by gear ring 34
In the shell of covering axle driving device 1.
The gear wheel 32a of 2nd ladder pinion gear 32 is wrong on the left and right directions of axle driving device 1 relative to gear ring 34
It opens.Also, the tooth top for being configured to the external tooth of gear wheel 32a (leaves gear wheel 32a in the outer part from the tooth root of the internal tooth than gear ring 34
Hollow shaft side) at pass through.
In addition, the gear wheel 32a of the 2nd ladder pinion gear 32 is relative to sun gear 21 in the right and left of axle driving device 1
It is staggered upwards, is configured to the tooth top of gear wheel 32a from the tooth root than sun gear 21 in the inner part (close to the hollow shaft of gear wheel 32a
Side) at pass through.
Gear ring 34 is fixed in axle driving device 1, to not be able to rotate.
Here, planet carrier 7 is configured to motor drive shaft 2 as rotation axis rotation.It is supported on planet carrier 7 as a result,
1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 can carry out revolution fortune relative to motor drive shaft 2
It is dynamic.
Therefore, by means of being transmitted to the driving force of outer pinion gear 33, the planet carrier 7 for supporting outer pinion gear 33 is rotated.
Planet carrier 7 is connect by differential carrier 44 with differential attachment 4, and differential carrier 44 becomes planet carrier 7 and differential attachment 4
Shared component.Driving force is transmitted to differential attachment 4 from planet carrier 7 as a result,.
Differential attachment 4 is by differential carrier 44, gear ring 43, the 1st pinion gear gear 41, the 2nd pinion gear gear 42, support plate
61 and the 1st axle 5 is constituted.Also, the center of rotation of differential carrier 44, gear ring 43 and support plate 61 and the 1st axle 5
Center of rotation is consistent.
Rack gear 43 is fixed on differential carrier 44, gear ring 43 is configured with the 1st pinion gear gear 41, the 2nd small tooth in inside
The gear 51 of wheel gear 42 and the 1st axle 5.
Gear ring 43 is engaged with the 1st pinion gear gear 41, and the 1st pinion gear gear 41 is supported on bearing in a rotatable manner
Axis 41c.The end of support shaft 41c is kept at support plate 61 and from the extension 61a that support plate 61 extends.
1st pinion gear gear 41 is also engaged with the 2nd pinion gear gear 42.2nd pinion gear gear 42 also with the 1st pinion gear teeth
Similarly not shown support shaft supports, support shaft are held in support plate 61 and extension to wheel 41 in a rotatable manner
61a.The rotation axis of 1st pinion gear gear 41 and the 2nd pinion gear gear 42 is configured along the left and right directions of axle driving device 1.
Also, the 2nd pinion gear gear 42 is engaged with the gear 51 of the 1st axle 5.
In addition, the side opposite with the 1st axle 5 in support plate 61 is connected with the 2nd axle 6.
The rotation axis of support plate 61 is identical as the 2nd axle 6.
Next, being illustrated using Figure 11 to Figure 18 to the structure of planet carrier 7.
Figure 11 is the perspective view for showing the left side of planet carrier of the 1st embodiment of the invention, and Figure 12 is the master of planet carrier
View.Figure 13 is the perspective view for showing the right side of planet carrier, and Figure 14 is to show to be assembled with the vertical of the state of pinion gear in planet carrier
Body figure.Figure 15 is the partial sectional view shown in the method for the 2nd ladder pinion gear of planet carrier over-assemble, and Figure 16 is shown in planet
The partial sectional view of the method for the 1st ladder pinion gear of frame over-assemble.Figure 17 is the perspective view for showing the lubricant passage way of planet carrier, figure
18 be the cross-sectional view for showing the lubricant passage way of the 1st ladder pinion gear.
Planet carrier 7 be by the side plate 9 of the disc-shape in the plane vertical with rotation axis, differential carrier 44 and
It is integrally fixed and formation in the substrate plate 70 of the plate in the plane vertical with rotation axis.
Substrate plate 70 is made of annulus 70a, extension 70b and terminal part 70e.
Annulus 70a is arranged circlewise centered on the rotation axis of planet carrier 7, and 3 are connected on annulus 70a from ring-type
The extension 70b that portion 70a extends outward.
Extension 70b is configured at equal intervals in a circumferential direction centered on the rotation axis of planet carrier 7.Also, prolonging
In extending portion 70b, in the side opposite with rotation axis side of planet carrier 7, it is provided with and extends along the circumference centered on rotation axis
Terminal part 70e.
In substrate plate 70, the notch section 70c of U-shaped is made of annulus 70a, extension 70b and terminal part 70e.
Also, the pinion gear 32b of the 2nd ladder pinion gear 32 is configured at notch section 70c.
In addition, the arc sections 70d being recessed in arc-shaped is provided in the opposite side of notch section 70c on extension 70b,
Pinion gear 31b configured with the 1st ladder pinion gear 31.
Also, on annulus 70a, in the rotation axis side of planet carrier 7, the mode vertical with substrate plate 70 is provided with
4 stays 74 and the 5th stay 75.
In addition, being provided with the 3rd stay 73 on extension 70b in the mode vertical with substrate plate 70.Also, in end
On portion 70e, the 1st stay 71 and the 2nd stay 72 are arranged in the mode vertical with substrate plate 70.
Also, the 1st stay 71, the 2nd stay 72, the 3rd stay 73, the 4th stay 74 and the 5th stay 75 are from 70 edge of substrate plate
The left and right directions of axle driving device 1 extends.
1st stay 71, the 2nd stay 72, the 3rd stay 73, the 4th stay 74 and the 5th stay 75 are respectively arranged with 3,
It is configured at equal intervals on the direction of rotation of planet carrier 7.
1st stay 71, the 2nd stay 72, the 3rd stay 73, the 4th stay 74 and the 5th stay 75 are from the edge of substrate plate 70
It stretches out.Therefore, it can use punch forming etc. to be bent to from the plate part that substrate plate 70 stretches out, to form the 1st stay
71, the 2nd stay 72, the 3rd stay 73, the 4th stay 74 and the 5th stay 75.And it is possible to constitute side plate 9 and poor by forging
Fast device shell 44, and substrate plate 70 is fixed on by welding.
1st stay 71, the 2nd stay 72 and the 5th stay 75 extend from substrate plate 70 to the left side of axle driving device 1,
The fixed side panel 9 on substrate plate 70.1st stay 71 and the 2nd stay 72 are connect with the outer peripheral edge portion of side plate 9.
In addition, the 1st stay 71 and the configuration of the 2nd stay 72 (leave side plate in the outer part in the support shaft 33c than outer pinion gear 33
The side of 9 rotation axis) at.In addition, the 1st stay 71 and the 2nd stay 72 are along the shape of the outer peripheral edge portion of side plate 9, on edge
It is circular shape when the left and right directions observation of axle driving device 1.
Also, the 5th stay 75 is connect with the edge of the opening 92 of side plate 9, inserted with motor drive shaft 2 in opening 92.And
And the 5th sun gear 21 of the stay 75 to surround motor drive shaft 2 outer peripheral surface in a manner of configure.
Sun gear 21 engages between the 5th stay 75 with the gear wheel 31a of the 1st ladder pinion gear 31.
3rd stay 73 and the 4th stay 74 are stretched out from substrate plate 70 to the right side of axle driving device 1, by differential carrier 44
It is fixed on substrate plate 70.
Differential carrier 44 is provided with the circular opening 44b for the insertion of the 1st axle 5, is connected with around opening 44b
4th stay 74.In addition, the 4th stay 74 is configured to that cross sectional shape is formed as arc-shaped along the shape of the edge of opening 44b.
In addition, the peripheral part of the gear wheel 32a of the 2nd ladder pinion gear 32 is between the 4th stay 74.
3rd stay 73 is arranged on substrate plate 70 along the direction in the rotation axis from planet carrier 7 towards outside.Also,
In the face vertical with the rotation axis of planet carrier 7, the 3rd stay 73 is formed as the circular shape for making 70 side convex of substrate plate.
3rd stay 73 configures between the 1st ladder pinion gear 31 and the 2nd ladder pinion gear 32.
As shown in figure 15, in the case where the 1st ladder pinion gear 31 of 7 over-assemble of planet carrier and the 2nd ladder pinion gear 32,
2nd ladder pinion gear 32 is inserted between side plate 9 and differential carrier 44.Also, as shown in figure 16, so that the 2nd ladder pinion gear
32 pinion gear 32b is located at the notch section 70c of substrate plate 70.
It is provided with the bearing portion 94 of the support shaft 32c of the 2nd ladder pinion gear 32 of insertion on side plate 9, is inserted from bearing portion 94
Enter support shaft 32c, the 2nd ladder pinion gear 32 is fixed on planet carrier 7 in a rotatable manner.In addition, in differential carrier 44
On, position corresponding with bearing portion 94 is formed with the bearing for keeping support shaft 32c on the left and right directions of axle driving device 1.
Support shaft 32c is maintained between side plate 9 and differential carrier 44 as a result,.
After the 2nd ladder pinion gear 32 is assembled in planet carrier 7, the 1st ladder pinion gear 31 is inserted into side plate 9 and differential
Between device shell 44.Also, the pinion gear 31b of the 1st ladder pinion gear 31 is located at the arc sections 70d of substrate plate 70.
As shown in figure 13, the bearing portion 93 of the support shaft 31c of the 1st ladder pinion gear 31 of insertion is provided on side plate 9.And
And it is inserted into support shaft 31c from bearing portion 93, the 1st ladder pinion gear 31 is fixed on planet carrier 7 in a rotatable manner.Separately
Outside, on differential carrier 44, position corresponding with bearing portion 93 is formed with holding branch on the left and right directions of axle driving device 1
Hold the bearing of axis 31c.Support shaft 31c is maintained between side plate 9 and differential carrier 44 as a result,.
Also, outer pinion gear 33 is inserted between side plate 9 and substrate plate 70.The outer pinion gear of insertion is provided on side plate 9
The bearing portion 95 of 33 support shaft 33c is inserted into support shaft 33c from bearing portion 95, in a rotatable manner by outer pinion gear 33
It is fixed on planet carrier 7.In addition, on substrate plate 70, the position corresponding with bearing portion 93 on the left and right directions of axle driving device 1
Install the support holes 76 for being equipped with and keeping support shaft 31c.Support shaft 33c is maintained between side plate 9 and substrate plate 70 as a result,.
In the structure of above-mentioned planet carrier 7, substrate plate 70 is configured between side plate 9 and differential carrier 44.It is outer small as a result,
One end of the support shaft 33c of gear 33 is kept by substrate plate 70.Therefore, the configuration structure regardless of 44 side of differential carrier, all
Outer pinion gear 33 can be configured, can be improved the freedom degree in the configuration of the support shaft 33c of outer pinion gear 33.
It, can be heavy with the gear wheel 32b of the 2nd ladder pinion gear 32 also, on the left and right directions of axle driving device 1
The position of conjunction configures support shaft 33c.
Thereby, it is possible to increase the gear wheel 32b of the 2nd ladder pinion gear 32, the big planetary mechanism of reduction ratio can be realized
3。
In addition, the 1st stay 71 and the 2nd stay 72 are configured near outer pinion gear 33, it can be in the 1st close stay
Outer pinion gear 33 is configured between 71 and the 2nd stay 72.Thereby, it is possible to improve the supporting rigidity of outer pinion gear 33, row can be improved
The durability of star mechanism 3.
Also, the 1st stay 71 is provided between outer 33 and the 1st ladder pinion gear 31 of pinion gear.In addition, in outer pinion gear
The 2nd stay 72 is provided between 33 and the 2nd ladder pinion gear 32.Outer pinion gear 33, the 1st ladder pinion gear 31, Yi Ji as a result,
Supporting rigidity between 2 ladder pinion gears 32 is improved.
The assembly precision of axle driving device 1 improves as a result, and can be improved durability, can reduce noise.
Next, being illustrated to the structure of the lubrication of planetary mechanism 3.
As shown in Figure 11 and Figure 17, on side plate 9, the opposite side with the side configured with differential carrier 44 is provided with oil
Road 91.
Oil circuit 91 is made of the recess portion on the surface of side plate 9, by be set to around opening 92 cyclic annular oil circuit 91a, from ring
Linear oil circuit 91b, the oil circuit 91c and oil circuit 91d that shape oil circuit 91a radially extends are constituted.
The end of oil circuit 91b is connect with the bearing portion 95 of outer pinion gear 33, is supplied and is lubricated so as to outside pinion gear 33
Oil.Oil circuit 91c is connect with the bearing portion 93 of the 1st ladder pinion gear 31, is lubricated so as to supply to the 1st ladder pinion gear 31
Oil.Also, oil circuit 91d is connect with the bearing portion 94 of the 2nd ladder pinion gear 32, so as to supply to the 2nd ladder pinion gear 32
Lubricating oil.
By taking the structure to the 1st ladder pinion gear 31 supply lubricating oil as an example, it is illustrated using Figure 18.
Cover board 8 is installed on side plate 9, on side plate 9, is configured with the 1st ladder pinion gear 31 in the opposite side of cover board 8.
On side plate 9, it is provided in the rotation axis side of side plate 9 and extends on rotating shaft direction along motor drive shaft 2
Rising portions 96.The outside of rising portions 96 is provided with cyclic annular oil circuit 91a, cyclic annular oil circuit 91a and the oil connecting with cyclic annular oil circuit 91a
Road 91c is covered by cover board 8.
Cover board 8 has the offset portion 82 being staggered to the opposite side of the 1st ladder pinion gear 31 in 96 side of rising portions.Offset portion 82
By from offset portion 82 to the inclined interconnecting piece 84 in 31 side of the 1st ladder pinion gear, and connect with the mounting portion 83 for being installed on side plate 9
It connects.
In the state that the mounting portion 83 of cover board 8 is installed on side plate 9, offset portion 82 is maintained at not to be contacted with side plate 9
Position.Opening 85 is provided between offset portion 82 and side plate 9 as a result,.
Opening 85 is annularly arranged in around the rising portions 96 of side plate 9, is connected to cyclic annular oil circuit 91a.
In addition, being internally provided with lubricant passage way 31d, lubricant passage way on the support shaft 31c of the 1st ladder pinion gear 31
31d and oil circuit connection (not shown), can supply lubricating oil between the 1st ladder pinion gear 31 and support shaft 31c.
Next, being illustrated to the effect of planetary mechanism 3 and differential attachment 4 in the 1st embodiment of the invention.
When transmitting driving force from motor drive shaft 2, the sun gear 21 by being fixed on motor drive shaft 2 drives the 1st ladder
Pinion gear 31.Sun gear 21 is engaged with the gear wheel 31a of the 1st ladder pinion gear 31, and the 1st ladder pinion gear 31 utilizes pinion gear
31b transmits driving force to the 2nd ladder pinion gear 32.The driving force of gear wheel 31a is input to from pinion gear 31b transmitting, therefore
In the 1st ladder pinion gear 31, driving force is completed to slow down.
Also, driving force is similarly set to slow down in the 2nd ladder pinion gear 32, outside pinion gear 33 transmits driving force.
Outer pinion gear 33 carries out revolution motion using the gear ring 34 of the outer pinion gear more than 33 of gear ratio, therefore driving force is further decelerated.
Driving force is passed the planet carrier 7 of the pinion gear 33 to outside bearing from outer pinion gear 33, to be input to differential attachment
4。
Differential carrier 44 is rotated by the rotation of planet carrier 7, and the gear ring 43 being integrally provided with differential carrier 44 rotates.
Gear ring 43 is engaged with the 1st pinion gear gear 41, and the 1st pinion gear gear 41 is engaged with the 2nd pinion gear gear 42.
Also, the 2nd pinion gear gear 42 is engaged with the gear 51 for being fixed on the 1st axle 5.
In addition, support plate 61 is fixed on one end of the 2nd axle 6, integrally rotated with the 2nd axle 6.
The driving force for being input to differential carrier 44 as a result, is transmitted by differential attachment 4 to the 1st axle 5 and the 2nd axle 6.
In above-mentioned driving force transmission path, it is connected in series the 1st ladder pinion gear 31 and the 2nd ladder pinion gear 32,
To slow down.Also, the 2nd ladder pinion gear is configured in the side gear wheel 31a of the 1st ladder pinion gear 31 of planetary mechanism 3
32 pinion gear 32b configures gear wheel 32a in the side pinion gear 31b.
Driving force is transmitted the pinion gear 31b to the right side for being located at axle driving device 1 by the 1st ladder pinion gear 31 as a result,
Side, driving force are transmitted the side pinion gear 32b to the left side for being located at axle driving device 1 by the 2nd ladder pinion gear 32.
Therefore, in planetary mechanism 3, multiple stepped gears i.e. the 1st ladder pinion gear 31 and the 2nd ladder pinion gear is utilized
32, can make driving force its support shaft 31c, support shaft 32c extending direction on turn back.It is filled further, it is possible to be driven in axle
Setting makes the deceleration path slowed down to driving force turn back on 1 left and right directions, can be obtained simultaneously big using seldom space
Reduction ratio.
In addition, interior in a limited space can efficiently configure the 1st ladder pinion gear 31 and the 2nd rank in planetary mechanism 3
Terraced pinion gear 32.
In addition, the pinion gear 32b of the 2nd ladder pinion gear 32 in the downstream side in driving power path is by outer pinion gear 33
And it is connect with gear ring 34.Increased by the freedom degree in the configuration by outer the 33, the 2nd ladder pinion gear 32 of pinion gear, can be made
2nd ladder pinion gear, 32 major diameter, to increase reduction ratio.
Also, the gear wheel 32a of the 2nd ladder pinion gear 32 and the sun gear 21 of motor drive shaft 2 is set to be staggered, therefore can
Rotation axis by the 2nd ladder pinion gear 32 relative to planetary mechanism 3 is configured in inside.Furthermore it is possible to increase gear wheel 32a, energy
Enough realize the big planetary mechanism 3 of reduction ratio.
Also, by the support shaft 33c of outer pinion gear 33 configuration the support shaft 32c than the 2nd ladder pinion gear 32 in the outer part
Place, therefore the 2nd ladder pinion gear 32 can be configured in the rotation axis side of planetary mechanism 3.Thereby, it is possible to reduce planetary mechanism 3
Torque when rotation.Furthermore it is possible to reduce vibration when planet carrier 7 rotates.
Next, being illustrated to the effect of the lubrication system of planetary mechanism 3.
By the rotation of planet carrier 7, the interior lubricating oil splash stored of axle driving device 1.It splashes and reaches opening 85
Lubricating oil flows into cyclic annular oil circuit 91a.Also, oil circuit 91b, oil circuit 91c are flowed by means of the centrifugal force of the rotation generation of planet carrier 7
And oil circuit 91d.
In addition, from opening 85 flow into lubricating oil due to cover board 8 without to oil circuit 91b, oil circuit 91c and oil circuit 91d with
Outer outflow, but it is fed into bearing portion 95, bearing portion 93, bearing portion 94 respectively.
The lubricating oil of oil circuit 91c is flowed into flow into and be arranged in the 1st small tooth of ladder by the bearing portion 93 connecting with oil circuit 91c
In lubricant passage way 31d in the support shaft 31c of wheel 31.Also, oil circuit (not shown) is utilized, lubricating oil is supplied to the 1st ladder
Between pinion gear 31 and support shaft 31c.
In addition, in the oil circuit 91d being connect with bearing portion 94 similarly, to the 2nd ladder pinion gear 32 and support shaft 32c
Between supply lubricating oil.
Also, in outer pinion gear 33 similarly by the oil circuit 91b being connect with bearing portion 95 and outward pinion gear 33
Lubricating oil is supplied between support shaft 33c.
Thereby, it is possible to the lubricating structure of planetary mechanism 3 is constituted using easy structure.Planetary mechanism can reliably be lubricated
3 the 1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33.
In addition, utilizing the oil being linearly arranged near the rotation axis of the bearing part of support shaft 33c, i.e. side plate 9
The support shaft 33c of road 91b, outside pinion gear 33 supply lubricating oil.Therefore, the feed path of lubricating oil, Neng Gouke can be shortened
The supply of oil is lubricated by ground.
Also, by disassembly cover board 8, it can easily be done cyclic annular oil circuit 91a, oil circuit 91b, oil circuit 91c and oil circuit
The maintenance of 91d.
[embodiment 2]
Next, illustrating the axle driving device 11 of the 2nd embodiment of the invention using Figure 19 to Figure 24.
Figure 19 is the perspective view for showing the left side of axle driving device of the 2nd embodiment of the invention, and Figure 20 is to show
The perspective view on the right side of the axle driving device of the 2nd embodiment.Figure 21 is the main view of the axle driving device of the 2nd embodiment
Figure, Figure 22 is the cross-sectional view of the XXII-XXII line in Figure 21.Also, Figure 23 is cuing open for the XXIII-XXIII line in Figure 21
View, Figure 24 are the skeleton drawings for schematically showing the structure of the axle driving device in the 2nd embodiment.
Difference in the axle driving device 11 of the 2nd embodiment, with the axle driving device 1 of the 1st embodiment
It is planetary mechanism 35 and differential attachment 45, other structures are identical.
Therefore, the planetary mechanism 35 of axle driving device 11 and differential attachment 45 are illustrated.
As shown in figure 19, the planetary mechanism 35 of axle driving device 11 is by being arranged in the sun of one end of motor drive shaft 2
The 21, the 1st ladder pinion gear 31, the 2nd ladder pinion gear 32, outer pinion gear 33, gear ring 34 and planet carrier 17 is taken turns to constitute.
1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 are respectively arranged with 3, drive in motor
It is configured at equal intervals around moving axis 2.
In addition, planet carrier 17 is made of side plate 19 and differential carrier 44.
Planet carrier 17 rotates the bearing of the 1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 certainly
Such as.Also, the rotary shaft and motor drive shaft 2 of the 1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 are flat
It configures capablely.
1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 are supported on side in a rotatable manner
Between plate 19 and differential carrier 44.
The gear wheel 31a side bearing of 1st ladder pinion gear 31 is in side plate 19, the side pinion gear 31b of the 1st ladder pinion gear 31
Differential carrier 44 is supported on by axis 17c.
The side gear wheel 32a of 2nd ladder pinion gear 32 is supported on side plate 19 by axis 17d, the 2nd ladder pinion gear 32 it is small
Gear 32b side bearing is in differential carrier 44.
The one end of outer pinion gear 33 is connect by axis 17b with side plate 19, the another side and differential mechanism of outer pinion gear 33
Shell 44 connects.
Sun gear 21 is the gear that tooth is arranged towards the outside of motor drive shaft 2,2 one of sun gear 21 and motor drive shaft
Ground rotation.Sun gear 21 is engaged with the gear wheel 31a of the 1st ladder pinion gear 31.
The gear wheel 31a and pinion gear 31b of 1st ladder pinion gear 31 are integrally rotated, and driving force is passed from pinion gear 31b
It is presented to the 2nd ladder pinion gear 32.
2nd ladder pinion gear 32 is made of the gear wheel 32a and pinion gear 32b integrally rotated, the 2nd ladder pinion gear 32
It is engaged by gear wheel 32a with the pinion gear 31b of the 1st ladder pinion gear 31.
The pinion gear 32b of 2nd ladder pinion gear 32 is engaged with outer pinion gear 33.
Outer pinion gear 33 is engaged with gear ring 34.
Gear ring 34 configures between side plate 19 and differential carrier 44 in 44 side of differential carrier.Also, in the inside of gear ring 34
Pinion gear 32b and outer pinion gear 33 configured with the 2nd ladder pinion gear 32.In addition, gear ring 34 utilizes fixed list (not shown)
Member and be fixed in axle driving device 11.
Gear ring 34 be in axle driving device 11 it is fixed, be not able to rotate.
Also, side plate 19 is integrally fixed with differential carrier 44 by axis 17b, axis 17c and axis 17d.Also, side plate
19 and enough become of differential carrier 44 can be that rotation axis be rotated with motor drive shaft 2.
The 1st ladder pinion gear 31, the 2nd ladder pinion gear 32 and outer pinion gear 33 can drive relative to motor as a result,
Axis 2 carries out revolution motion.
Therefore, differential carrier 44 is rotated by means of being transmitted to the driving force of outer pinion gear 33.
Differential attachment 45 is by differential carrier 44, gear ring 43, the 1st pinion gear gear 41, the 2nd pinion gear gear 42, support plate
The gear 6a of 52 and the 2nd axle 6 is constituted.
Also, the center of rotation of differential carrier 44, gear ring 43 and support plate 52 is consistent with the center of rotation of the 2nd axle 6.
Rack gear 43 is fixed on differential carrier 44, and the 1st pinion gear gear 41, the 2nd small tooth are configured on the inside of gear ring 43
The gear 6a of wheel gear 42 and the 2nd axle 6.
Gear ring 43 is engaged with the 1st pinion gear gear 41, and the 1st pinion gear gear 41 is engaged with the 2nd pinion gear gear 42.
1st pinion gear gear 41 and the 2nd pinion gear gear 42 are rotatably supported on support plate 52, the 1st axle 5 with
Support plate 52 connects.
Also, the 2nd pinion gear gear 42 is engaged with the gear 6a of the 2nd axle 6.
The effect of axle driving device 11 in the 2nd embodiment of the invention is illustrated.
When transmitting driving force from motor drive shaft 2, the 1st ladder pinion gear 31 is fixed in the sun of motor drive shaft 2
21 driving of wheel.Sun gear 21 is engaged with the gear wheel 31a of the 1st ladder pinion gear 31, and the 1st ladder pinion gear 31 utilizes pinion gear
31b transmits driving force to the 2nd ladder pinion gear 32.Due to being input to the driving force of gear wheel 31a from pinion gear 31b transmitting,
Therefore driving force is decelerated.
Also, similarly driving force is slowed down in the 2nd ladder pinion gear 32 and transmits outside pinion gear 33.Outer small tooth
Wheel 33 carries out revolution motion by means of the gear ring 34 of pinion gear more than 33 outside gear ratio, therefore driving force is further slowed down.
Driving force is passed the differential carrier 44 of the pinion gear 33 to outside bearing from outer pinion gear 33, to be input to differential machine
Structure 4.
Differential carrier 44 rotates, so that the gear ring 43 being integrally provided with differential carrier 44 rotates.Gear ring 43 and the 1st small tooth
Wheel gear 41 engages, and the 1st pinion gear gear 41 is engaged with the 2nd pinion gear gear 42.
Also, the 2nd pinion gear gear 42 is engaged with the gear 6a for being fixed on the 2nd axle 6.
In addition, support plate 52 is fixed on one end of the 1st axle 5, support plate 52 is integrally rotated with the 1st axle 5.
The driving force for being input to differential carrier 44 as a result, is passed to the 1st axle 5 and the 2nd axle 6 by differential attachment 4.
In this way, configuring the 1st ladder pinion gear 31 and the 2nd ladder pinion gear 32 in planetary mechanism 35, therefore can make to go
Star mechanism 35 is compact, while can obtain big reduction ratio.Furthermore it is possible to make the 1st ladder pinion gear 31 and the 2nd ladder pinion gear
32 configure close to the 1st axle 5 and the 2nd axle 6, therefore can reduce the turning moment of planetary mechanism 35.
Above-mentioned embodiment only shows one embodiment of the present invention, can be in the range for not departing from purport of the invention
Inside arbitrarily is deformed and applied.
Claims (7)
1. a kind of axle driving device, which is characterized in that
Road is being transmitted to the driving force of the 1st axle and the planet-shaped deceleration mechanism of the 2nd axle transmitting driving force by differential attachment
In diameter, there are the multiple stepped gears for being connected in series and slowing down.
2. axle driving device according to claim 1, which is characterized in that
The driving force transmission path of planet-shaped deceleration mechanism is by means of the multiple stepped gear and in the stepped gear
Support shaft extending direction on turn back.
3. axle driving device according to claim 1 or 2, which is characterized in that
The stepped gear in the downstream side of the power transfer path of planet-shaped deceleration mechanism by planetary gear and with the row
The gear ring of star-like deceleration mechanism engages.
4. axle driving device according to claim 3, which is characterized in that
Between the big side gear of the stepped gear in the planetary gear and the downstream side, it is provided with the bearing planetary gear
Support shaft one end component, on the rotating shaft direction of the 1st axle, the planetary gear support shaft is configured in
The position being overlapped with the big side gear of the stepped gear in the downstream side.
5. axle driving device according to claim 3, which is characterized in that
The big side gear of the stepped gear of the sun gear and downstream side of planet-shaped deceleration mechanism is in the 1st axle
It is staggered on rotating shaft direction,
On the rotating shaft direction of the 1st axle, the rank in the downstream side is configured on the position being overlapped with the sun gear
The big side gear of terraced gear.
6. axle driving device according to claim 4, which is characterized in that
The big side gear of the stepped gear of the sun gear and downstream side of planet-shaped deceleration mechanism is in the 1st axle
It is staggered on rotating shaft direction,
On the rotating shaft direction of the 1st axle, the rank in the downstream side is configured on the position being overlapped with the sun gear
The big side gear of terraced gear.
7. axle driving device according to claim 3, which is characterized in that
It is provided with oil circuit on the planetary gear bearing part of planet-shaped deceleration mechanism,
The opposite side configured with the planetary gear side is arranged in the oil circuit,
Be set to the bearing part the oil circuit and the planetary gear described in oil circuit in support shaft by the branch
The bearing portion of the holding planetary gear support shaft of bearing portion part and connect.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2018025917A JP6559818B1 (en) | 2018-02-16 | 2018-02-16 | Axle drive |
| JP2018-025917 | 2018-02-16 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110159707A true CN110159707A (en) | 2019-08-23 |
| CN110159707B CN110159707B (en) | 2021-03-05 |
Family
ID=67614863
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201811579398.3A Active CN110159707B (en) | 2018-02-16 | 2018-12-24 | Axle drive device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP6559818B1 (en) |
| CN (1) | CN110159707B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110296188A (en) * | 2018-03-22 | 2019-10-01 | 本田技研工业株式会社 | Axle driving device |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2021024887A1 (en) | 2019-08-05 | 2021-02-11 | 株式会社小糸製作所 | Vehicular lamp and vehicle |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009036365A (en) * | 2007-08-03 | 2009-02-19 | Yamatake Corp | Planetary gear deceleration mechanism and electric actuator |
| WO2013013841A1 (en) * | 2011-07-28 | 2013-01-31 | Schaeffler Technologies AG & Co. KG | Drive device for a motor vehicle |
| WO2015087750A1 (en) * | 2013-12-12 | 2015-06-18 | Ntn株式会社 | Reduction gear |
| DE102015106503A1 (en) * | 2014-05-13 | 2015-11-19 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Vehicle gearbox with planetary gear set with common carrier |
| CN107685340A (en) * | 2016-08-05 | 2018-02-13 | 发那科株式会社 | Rotating shaft assembly and articulated robot |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002104001A (en) * | 2000-09-29 | 2002-04-09 | Exedy Corp | Reduction gear of electric vehicle and its reduction ratio setting method |
| JP4981694B2 (en) * | 2008-01-08 | 2012-07-25 | 株式会社ユニバンス | Power transmission device |
-
2018
- 2018-02-16 JP JP2018025917A patent/JP6559818B1/en not_active Expired - Fee Related
- 2018-12-24 CN CN201811579398.3A patent/CN110159707B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2009036365A (en) * | 2007-08-03 | 2009-02-19 | Yamatake Corp | Planetary gear deceleration mechanism and electric actuator |
| WO2013013841A1 (en) * | 2011-07-28 | 2013-01-31 | Schaeffler Technologies AG & Co. KG | Drive device for a motor vehicle |
| WO2015087750A1 (en) * | 2013-12-12 | 2015-06-18 | Ntn株式会社 | Reduction gear |
| DE102015106503A1 (en) * | 2014-05-13 | 2015-11-19 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Vehicle gearbox with planetary gear set with common carrier |
| CN107685340A (en) * | 2016-08-05 | 2018-02-13 | 发那科株式会社 | Rotating shaft assembly and articulated robot |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110296188A (en) * | 2018-03-22 | 2019-10-01 | 本田技研工业株式会社 | Axle driving device |
| CN110296188B (en) * | 2018-03-22 | 2021-11-05 | 本田技研工业株式会社 | Axle drive device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110159707B (en) | 2021-03-05 |
| JP2019143656A (en) | 2019-08-29 |
| JP6559818B1 (en) | 2019-08-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US8641568B2 (en) | Electric machine for an electric axle of a motor vehicle | |
| CN103185108B (en) | Be used for epicyclic train of gears and the relevant aircraft of the aircraft that can hover | |
| CN105650215A (en) | Gear, motor-gear unit, vehicle, generator with a gear, and force transmitting element | |
| US10843770B2 (en) | Bicycle having electric drive with power distribution | |
| JP6377282B2 (en) | Transmission assembly and electric drive comprising such a transmission assembly | |
| CN101963213B (en) | Multi-speed transmission with multi-axis transfer | |
| CN110159707A (en) | Axle driving device | |
| CN110291309A (en) | Transmission device | |
| JP6487664B2 (en) | Differential | |
| CN109681587A (en) | Compound planetary gear arrangement | |
| CN112344003B (en) | Power transmission device | |
| JP2016080152A5 (en) | ||
| CN103429931B (en) | Speed change gear | |
| US20100236347A1 (en) | Gear transmission apparatus | |
| CN110296188A (en) | Axle driving device | |
| CN106481787A (en) | There is the traction motor of independent drive end bearing lubrication | |
| JP6265096B2 (en) | Vehicle drive device | |
| US20200256439A1 (en) | Axle center transmission | |
| CN203335738U (en) | Power transmission device | |
| CN105857507A (en) | Novel bicycle internal transmission hub | |
| WO2018180806A1 (en) | Differential device | |
| CN101405522B (en) | Transmission assembly for a motor vehicle | |
| US20240066980A1 (en) | Wheel side | |
| CN110296184A (en) | The assemble method of axle driving device and axle driving device | |
| JP2014052065A (en) | Lubrication structure of planetary gear mechanism |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |