CN203686047U - Differential gear train - Google Patents

Differential gear train Download PDF

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Publication number
CN203686047U
CN203686047U CN201320740595.5U CN201320740595U CN203686047U CN 203686047 U CN203686047 U CN 203686047U CN 201320740595 U CN201320740595 U CN 201320740595U CN 203686047 U CN203686047 U CN 203686047U
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CN
China
Prior art keywords
differential
carrier body
output shaft
counter mass
limits
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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.)
Expired - Lifetime
Application number
CN201320740595.5U
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Chinese (zh)
Inventor
M·G·福克斯
G·L·希特沃勒
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Eaton Intelligent Power Ltd
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Eaton Corp
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Filing date
Publication date
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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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/22—Arrangements for suppressing or influencing the differential action, e.g. locking devices using friction clutches or brakes
    • 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
    • F16H48/00—Differential gearings
    • F16H48/06—Differential gearings with gears having orbital motion
    • F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
    • 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
    • F16H48/00—Differential gearings
    • F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
    • F16H48/30—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means
    • F16H48/32—Arrangements for suppressing or influencing the differential action, e.g. locking devices using externally-actuatable means using fluid pressure actuators

Abstract

The utility model relates to a differential gear train. The differential gear train structured according to one embodiment of the utility model comprises a first differential shell part and a second differential shell part, wherein the first differential shell part is used for limiting a first output shaft opening; the second differential shell part is used for limiting a second output shaft opening; the first differential shell part can comprise an annular concave part formed in the first differential shell part; the annular concave part is limited by an outer peripheral wall, an inner peripheral wall and an end wall; a piston is glidingly arranged in the annular concave part, and is configured into an actuating clutch assembly; a first side gear and a second side gear are rotatably arranged in a differential shell; the first side gear and the second side gear can be coaxially aligned along the spin axis of the differential shell.

Description

Differential gear train
Technical field
The utility model relates in general to differential gear train, and relates more particularly to a kind of case of differential with integrated piston shell.
Background technique
Differential gear train can be arranged in axle assembly and for from transmission shaft to a pair of output shaft transmitting torque.Transmission shaft can be by using the bevel gear driving differential mechanism engaging with the gear ring being arranged on differential casing.In automobile application, differential mechanism allows the tire that is arranged on axle assembly two ends to rotate with friction speed.When Ackermann steer angle, this is important, because outside tire moves larger camber line distance than inside tire.Thereby, outside tire must with than inside tire faster speed rotate to compensate this larger operating range.Differential mechanism comprises the case of differential and the gearing that allows from transmission shaft to output shaft transmitting torque and allow output shaft to rotate with friction speed as required simultaneously.This gearing can comprise generally and being mounted to and a pair of side gear (differential gear) rotating together with output shaft separately.A series of cross pivot pins or pinion shaft are fixedly installed on the case of differential therewith to rotate.Corresponding multiple small gear is mounted to and rotates together with pinion shaft and engage with two side gears.
Some differential gear trains comprise tractive force amendment type differential mechanism.Typically, between a side gear and the adjacent surface of differential carrier, can be provided with clutch pack.Clutch pack or lockable mechanism can be worked with relatively rotating between limiting gear case and this side gear.In this differential mechanism, realize the joint (delay differential) of clutch pack or lockable mechanism by one of several distinct methods.Some configurations comprise piston, and this plunger actuation move clutch pack between disconnection, locking and part lockup state.
Here the background providing is described for general description content of the present utility model.Inventor's the work of describing in background technique part, and the All aspects of of prior art can not submit to as the application in specification time, not both also impliedly being identified as is ambiguously with respect to prior art of the present utility model.
Model utility content
Can comprise the differential casing with the first differential carrier body and the second differential carrier body according to the differential gear train of an example constructions of the present utility model, this the first differential carrier body limits the first output shaft opening, and this second differential carrier body limits the second output shaft opening.Described the first differential carrier body can have annular recess formed thereon, and this annular recess is limited by periphery wall, inner circle wall and end wall.Piston can be slidably disposed in annular recess and be configured to activate clutch pack.The first and second side gears can be rotatably installed in differential casing.Described the first and second side gears can be along the spin axis co-axially align of differential casing.The first side gear can limit the first axle opening, and this first axle opening is configured to provide the first transmission of torque with being received in the first output shaft in the first output shaft opening to be connected.The second side gear can limit the second axle opening, and this second axle opening is configured to provide the second transmission of torque with being received in the second output shaft in the second output shaft opening to be connected.
According to supplementary features, described differential gear assembly also can comprise the counter mass being arranged on the first differential carrier body.This counter mass can be configured to the first side gear Separating force to pass to the first differential carrier body.The first differential carrier body also can comprise the annular lip partly being formed by inner circle wall.Counter mass can be arranged on annular lip.
According to other features, described counter mass can comprise radial arm and flange.Described flange can be resisted against on the annular lip of counter mass.Described radial arm is opposite to relative with the inner circle wall of the annular recess of the first differential carrier body.Described the first side gear limits annular pass, and this annular pass is nestedly received counter mass therein.Counter mass can limit the hole of multiple perforations.Described counter mass can be taper.
According to other features, the first differential carrier body can limit multiple blind holes that receive planet pin from planetary gear set.Differential assembly also can comprise the O shape circle being arranged between piston and the periphery wall of annular recess.Between piston and the inner circle wall of annular recess, can be provided with the 2nd O shape circle.Between counter mass and the first side gear, can be provided with packing ring.
Can comprise the differential casing with the first differential carrier body and the second differential carrier body according to the differential gear train of another example constructions of the present utility model, this first differential carrier body limits the first output shaft opening and this second differential carrier body limits the second output shaft opening.Described the first differential carrier body can comprise annular recess formed thereon.Piston can be slidably disposed in annular recess and be configured to activate clutch pack.The first and second side gears can be rotatably installed in differential casing.Described the first and second side gears can be along the spin axis co-axially align of differential casing.The first side gear can limit the first axle opening, and this first axle opening is configured to provide the first transmission of torque with being received in the first output shaft in the first output shaft opening to be connected.The second side gear can limit the second axle opening, and this second axle opening is configured to provide the second transmission of torque with being received in the second output shaft in the second output shaft opening to be connected.On the first differential carrier body, can be provided with counter mass.Counter mass can be configured to the first side gear Separating force to pass to the first differential carrier body.
According to supplementary features, described annular recess is limited by periphery wall, inner circle wall and end wall.The first differential carrier body also can comprise the annular lip partly being formed by inner circle wall.Counter mass can be arranged on annular lip.Described counter mass can comprise radial arm and flange.Described flange can be resisted against the annular lip of counter mass.Described radial arm can be relative with the inner circle wall of the annular recess of the first differential carrier body.
According to other features, described the first side gear limits annular pass, and this annular pass is nestedly received counter mass therein.The first differential carrier body can limit multiple blind holes that receive planet pin from planetary gear set.Described differential assembly also can comprise the O shape circle being arranged between piston and the periphery wall of annular recess.Between piston and the inner circle wall of annular recess, can be provided with the 2nd O shape circle.
Can comprise the differential casing with the first differential carrier body and the second differential carrier body according to the differential gear train of another example constructions of the present utility model, this the first differential carrier body limits the first output shaft opening, and this second differential carrier body limits the second output shaft opening.Described the first differential carrier body can comprise annular recess formed thereon.Described the first differential carrier body also can limit multiple blind holes that receive planet pin from planetary gear set.Piston can be slidably disposed in annular recess and be configured to activate clutch pack.The first and second side gears can be rotatably installed in differential casing.Described the first and second side gears can be along the spin axis co-axially align of differential casing.The first side gear can limit the first axle opening, and this first axle opening is configured to provide the first transmission of torque with being received in the first output shaft in the first output shaft opening to be connected.Described the second side gear can limit the second axle opening, and this second axle opening is configured to provide the second transmission of torque with being received in the second output shaft in the second output shaft opening to be connected.On the first differential carrier body, can be provided with counter mass.Counter mass can be configured to the first side gear Separating force to pass to the first differential carrier body.
According to other features, described counter mass can comprise radial arm and flange.Described flange can be resisted against on the annular lip of counter mass.Described radial arm can be relative with the inner circle wall of the annular recess of the first differential carrier body.
Accompanying drawing explanation
Can more fully understand the utility model from following detailed description and accompanying drawing, wherein:
Fig. 1 is the schematic diagram comprising according to the example vehicle power train of the differential gear train of the utility model one example constructions;
Fig. 2 is according to the front perspective view of the limited-slip differential assembly of the utility model one example constructions;
Fig. 3 is the sectional view along the limited-slip differential assembly of the line 3-3 of Fig. 2;
Fig. 4 is the detailed section view of the first differential carrier body, piston, counter mass and the side gear of Fig. 3;
Fig. 5 is the front perspective exploded view of a part for the case of differential of Fig. 2; With
Fig. 6 is the rear perspective exploded view of a part for the case of differential shown in Fig. 5;
Embodiment
First with reference to figure 1, show the example vehicle power train totally being represented by reference character 10.Example vehicle power train 10 described here is for having the f-w-d vehicle of motor 12 of horizontal installation, but other configurations also can use the utility model.Motor 12 provides rotation output to speed changer 14.
Power train 10 also can comprise transaxle 22 and have the limited-slip differential assembly 30 of planetary gear set 16, clutch assembly 32 and differential gear assembly 34.This limited-slip differential assembly 30 is contained in housing 36 and moves to drive a pair of semiaxis 40 and 42 being connected with front driving wheel 44 and 48 respectively.Generally speaking, limited-slip differential assembly 30 is used as traditional open type differential in normal working, until need the event of deviation moment.In the time detecting or anticipate loss of traction, clutch assembly 32 can optionally be activated to produce the deviation ratio for this situation optimum.
Speed changer 14 can receive rotation output and provide rotation input to limited-slip differential assembly 30 from motor 12.In addition between the rotation input that, speed changer 14 can be worked with the rotation output at motor 12 and limited-slip differential assembly 30, provide various velocity ratios.
Planetary gear set 16 comprises gear ring 46, sun gear 20 and the multiple planetary pinions 50 that supported by planet carrier 52.Gear ring 46 is non-rotatably fixed on housing 36, and sun gear 20 engages with the multiple planetary pinions 50 that supported by planet carrier 52.Planetary pinion 50 engages with gear ring 46.Planet carrier 52 is connected into the case of differential 54 of differential gear assembly 34 and rotates.Planetary gear set 16 provides from sun gear 20 to planet carrier 52 and and then to the step-down ratio of the case of differential 54.Sun gear 20 is rotatably by being attached to speed changer 14 such as the coupling arrangement of chain or band, the output of speed changer 14 driven and rotate sun gear 20, and this sun gear converts the rotation output from speed changer 14 to the rotation input of sun gear 20.
Differential gear assembly 34 comprise be mounted to respectively and semiaxis 40 and 42(and the first and second driving wheels 44 and 48) together with a pair of side gear 60 and 62 that rotates. Side gear 60 and 62 limits the first and second semiaxis openings 64 and 65(Fig. 3).Multiple cross pivot pins or pinion shaft 66 are fixedly mounted on the case of differential 54 for rotate thereupon.Corresponding multiple small gear 70 is mounted for rotating together with pinion shaft 66 and all engaging with two side gears 60 and 62.In greater detail in open configuration, differential gear assembly 34 works to allow semiaxis 40 and 42 to rotate with friction speed below.
Clutch assembly 32 connects planetary gear set 16 and differential gear assembly 34.Clutch assembly 32 comprises clutch pack 72 and clutch actuator 73.Clutch pack 72 comprises the multiple annular disks 74 between multiple annular friction sheets 78 arranged in a crossed manner.Multiple annular disks 74 can be connected into one of the case of differential 54 and differential gear assembly 34 and rotate.Multiple annular friction sheets 78 can be connected into the another one in the case of differential 54 and differential gear assembly 34 and rotate.In the embodiment shown, multiple annular disks 74 are for example connected into, for (rotating with the case of differential 54, spline joint is to the internal diameter 76 of the case of differential 54) and multiple annular friction sheet 78 be for example connected into, for rotate (, spline joint is to the external diameter 80 of side gear 60) with differential gear assembly 34.Be appreciated that annular friction sheet 78 can be supported to rotate by any one or both in side gear 60 or 62 simultaneously.
When clutch assembly 32 is during in its off position, thus multiple annular disk 74 and annular friction sheet 78 setting intersected with each other work and tie up to each other and rotate with substantially discontiguous pass.But, it will be understood by those skilled in the art that it is relative that term used herein " does not contact ", do not mean that and must represent absolutely not to contact with annular friction sheet 78 when clutch assembly 32 annular disk 74 in the time disconnecting situation.When clutch assembly 32 is in engaging or when part engagement configuration, annular disk 74 can move axially into frictional engagement relative to each other with annular friction sheet 78, reduces thus relatively rotating between annular disk 74 and annular friction sheet 78.Like this, when clutch assembly 32 is during in its engagement positio, side gear 60 with 62 and semiaxis 40 rotate together with 48 with driving wheel 44 with 42.
Clutch assembly 32 can for example be rotated independently of one another with friction speed with permission side gear 60 and 62 under disconnection configuration in operation.Clutch assembly 32 also can engage or part engagement configuration under move, in this configuration, side gear 60 rotates with together with essentially identical speed for example or partly together (namely dependently) with 62.For example, clutch assembly 32 can be hydraulic coupling assembly 32, and it utilizes pressurized hydraulic fluid to make piston 82 optionally activate clutch pack 72 in disconnection, joint and part engagement configuration.
With reference now to Fig. 2-6,, will the additional technical feature of differential gear assembly 34 be described.The case of differential 54 can comprise limit first output shaft opening 92(Fig. 3) the first differential carrier body 90, and limit second output shaft opening 96(Fig. 2) the second differential carrier body 94.The first and second differential carrier bodies 90 and 94 can be linked together by multiple fastening pieces 98.In the example shown, fastening piece comprises hex head bolt, but also can consider other configurations.Should be appreciated that from content below, the first differential carrier body 90 can comprise the piston shell 100 being integrally formed.And the first differential carrier body 90 can share the common wall 102(Fig. 3 between planetary gear set 16 and piston shell 100).
The first differential carrier body 90 can limit annular recess 110(Fig. 4) and multiple blind hole 114(Fig. 3).Annular recess 110 can be limited by periphery wall 120, inner circle wall 112 and end wall 124.End wall 124 can be integral with common wall 102.The first differential carrier body 90 also can comprise the annular lip 128 partly being formed by inner circle wall 122.Blind hole 114 receivabilities are for the planet pin 130 of the planetary pinion 50 of support planetary gears assembly 16.
The one O shape circle 134 can be set between piston 82 and the periphery wall 120 of annular recess 110.In an example, piston 82 can limit outer ring groove 136.The one O shape circle 134 can be nested in outer ring groove 136.The 2nd O shape circle 140 can be set between piston 82 and the inner circle wall 122 of annular recess 110.In an example, piston 82 limits interior annular groove 142.The 2nd O shape circle 140 can be nested in interior annular groove 142.
At clutch assembly 32 run durations, piston 82 can activated with (in substantially horizontal as shown in Figure 3) toward or away from clutch pack 72 in annular recess 110.The actuating of piston 82 can cause by the prearranging quatity hydraulic pressure that is delivered to clutch assembly 32, this prearranging quatity hydraulic pressure generation for the optimum deviation ratio of this situation for to keep suitable kinology difference in wheel speed, as two wheels by predictable clamping.In the example shown, piston 82 makes annular disk 74 and annular friction sheet 78 frictional engagement towards the actuating (as shown in Figure 3 to the right) of engagement positio, and locking differential gear assembly 34 thus makes side gear 60 and 62 rotate with identical speed.
On the first differential carrier body 90, counter mass 150 can be set.Counter mass 150 can be configured to transmit Separating force from the first side gear 60 to the first differential carrier body 90.Like this, counter mass 150 and the first differential carrier body 90 can be provided for the structural support of the axial position that keeps side gear 60.Counter mass 150 can nestedly be received in the annular pass 154(Fig. 4 and 6 limiting in the first side gear 60) in.In annular pass 154, can between side gear 60 and counter mass 150, packing ring 156 be set.Counter mass 150 can comprise perforation and limit the taper 160 in multiple holes 162 generally.Counter mass 150 can comprise radial arm 170(Fig. 4) and flange 172.Flange 172 is resisted against on the annular lip 128 of the first differential carrier body 90.Radial arm 170 is relative with the inner circle wall 122 of annular recess 110.
Provide to embodiment's aforementioned description only for explain and explanation.It is not detailed or is intended to limit the utility model.Indivedual elements or the feature of specific embodiment are not limited to this specific embodiment conventionally, but, be interchangeable in due course and can be applied in selected embodiment, even if do not illustrate specially or describe.Described embodiment also can have a lot of variation patterns.These variations are not considered as departing from the utility model, and all such modification are all believed to comprise in scope of the present utility model.

Claims (20)

1. a differential gear train, is characterized in that comprising:
Differential casing, this differential casing has the first differential carrier body that limits the first output shaft opening and the second differential carrier body that limits the second output shaft opening, described the first differential carrier body comprises annular recess formed thereon, and this annular recess is limited by periphery wall, inner circle wall and end wall;
Piston, this piston is slidably disposed in described annular recess and is configured to activate clutch pack; With
Be rotatably installed in the first and second side gears in described differential casing, described the first and second side gears are along the spin axis co-axially align of described differential casing, the first side gear limits the first axle opening, this the first axle opening is configured to provide the first transmission of torque with being received in the first output shaft in described the first output shaft opening to be connected, the second side gear limits the second axle opening, and this second axle opening is configured to provide the second transmission of torque with being received in the second output shaft in described the second output shaft opening to be connected.
2. differential gear train as claimed in claim 1, is characterized in that, also comprises the counter mass being arranged on described the first differential carrier body, and this counter mass is configured to the first side gear Separating force to pass to described the first differential carrier body.
3. differential gear train as claimed in claim 2, is characterized in that, described the first differential carrier body also comprises the annular lip partly being formed by described inner circle wall.
4. differential gear train as claimed in claim 3, is characterized in that, described counter mass is arranged on described annular lip.
5. differential gear train as claimed in claim 4, it is characterized in that, described counter mass comprises radial arm and flange, wherein said flange be resisted against on the annular lip of described counter mass and described radial arm relative with the inner circle wall of the annular recess of described the first differential carrier body.
6. differential gear train as claimed in claim 2, is characterized in that, described the first side gear limits annular pass, and this annular pass is nestedly received described counter mass therein.
7. differential gear train as claimed in claim 2, is characterized in that, described counter mass limits the hole of multiple perforations.
8. differential gear train as claimed in claim 2, is characterized in that, described counter mass is taper.
9. differential gear train as claimed in claim 1, is characterized in that, described the first differential carrier body limits multiple blind holes, and described blind hole receives planet pin from planetary gear set.
10. differential gear train as claimed in claim 1, characterized by further comprising:
Be arranged on the O shape circle between described piston and the periphery wall of described annular recess; With
Be arranged on the 2nd O shape circle between described piston and the inner circle wall of described annular recess.
11. differential gear trains as claimed in claim 2, is characterized in that, also comprise the packing ring being arranged between described counter mass and described the first side gear.
12. 1 kinds of differential gear trains, is characterized in that comprising:
Differential casing, this differential casing has the first differential carrier body that limits the first output shaft opening and the second differential carrier body that limits the second output shaft opening, and described the first differential carrier body comprises annular recess formed thereon;
Piston, this piston is slidably disposed in described annular recess and is configured to activate clutch pack;
Be rotatably installed in the first and second side gears in described differential casing, described the first and second side gears are along the spin axis co-axially align of described differential casing, the first side gear limits the first axle opening, this the first axle opening is configured to provide the first transmission of torque with being received in the first output shaft in described the first output shaft opening to be connected, the second side gear limits the second axle opening, and this second axle opening is configured to provide the second transmission of torque with being received in the second output shaft in described the second output shaft opening to be connected; With
Counter mass, this counter mass is arranged on described the first differential carrier body and is configured to the first side gear Separating force is passed to described the first differential carrier body.
13. differential gear trains as claimed in claim 12, is characterized in that, described annular recess is limited by periphery wall, inner circle wall and end wall.
14. differential gear trains as claimed in claim 13, is characterized in that, described the first differential carrier body also comprises the annular lip partly being formed by described inner circle wall, and wherein said counter mass is arranged on described annular lip.
15. differential gear trains as claimed in claim 14, it is characterized in that, described counter mass comprises radial arm and flange, wherein said flange be resisted against on the annular lip of described counter mass and described radial arm relative with the inner circle wall of the annular recess of described the first differential carrier body.
16. differential gear trains as claimed in claim 12, is characterized in that, described the first side gear limits annular pass, and this annular pass is nestedly received described counter mass therein.
17. differential gear trains as claimed in claim 12, is characterized in that, described the first differential carrier body limits multiple blind holes, and described blind hole receives planet pin from planetary gear set.
18. differential gear trains as claimed in claim 12, characterized by further comprising:
Be arranged on the O shape circle between described piston and the periphery wall of described annular recess; With
Be arranged on the 2nd O shape circle between described piston and the inner circle wall of described annular recess.
19. 1 kinds of differential gear trains, is characterized in that comprising:
Differential casing, this differential casing has the first differential carrier body that limits the first output shaft opening and the second differential carrier body that limits the second output shaft opening, described the first differential carrier body comprises annular recess formed thereon, wherein said the first differential carrier body also comprises multiple blind holes, and described blind hole receives planet pin from planetary gear set;
Piston, this piston is slidably disposed in described annular recess and is configured to activate clutch pack;
Be rotatably installed in the first and second side gears in described differential casing, described the first and second side gears are along the spin axis co-axially align of described differential casing, the first side gear limits the first axle opening, this the first axle opening is configured to provide the first transmission of torque with being received in the first output shaft in described the first output shaft opening to be connected, the second side gear limits the second axle opening, and this second axle opening is configured to provide the second transmission of torque with being received in the second output shaft in described the second output shaft opening to be connected; With
Counter mass, this counter mass is arranged on described the first differential carrier body and is configured to the first side gear Separating force is passed to described the first differential carrier body.
20. differential gear trains as claimed in claim 19, it is characterized in that, described counter mass comprises radial arm and flange, wherein said flange be resisted against on the annular lip of described counter mass and described radial arm relative with the inner circle wall of the annular recess of described the first differential carrier body.
CN201320740595.5U 2012-10-10 2013-10-09 Differential gear train Expired - Lifetime CN203686047U (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US201261712239P 2012-10-10 2012-10-10
US201361843531P 2013-07-08 2013-07-08
US61/843,531 2013-07-08
US61/712,239 2013-10-10

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106895127A (en) * 2015-12-18 2017-06-27 武藏精密工业株式会社 Differential gear

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6891659B2 (en) * 2017-06-21 2021-06-18 株式会社ジェイテクト Differential device
CN107795659B (en) * 2017-11-21 2024-01-12 中国第一汽车股份有限公司 Novel through axle interaxle differential mechanism structure

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106895127A (en) * 2015-12-18 2017-06-27 武藏精密工业株式会社 Differential gear

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C14 Grant of patent or utility model
GR01 Patent grant
TR01 Transfer of patent right
TR01 Transfer of patent right

Effective date of registration: 20190701

Address after: Dublin, Ireland

Patentee after: Eaton Intelligent Power Co.,Ltd.

Address before: Ohio, USA

Patentee before: Eaton Corp.

CX01 Expiry of patent term
CX01 Expiry of patent term

Granted publication date: 20140702