CN203686056U - Differential gear train - Google Patents
Differential gear train Download PDFInfo
- Publication number
- CN203686056U CN203686056U CN201320740445.4U CN201320740445U CN203686056U CN 203686056 U CN203686056 U CN 203686056U CN 201320740445 U CN201320740445 U CN 201320740445U CN 203686056 U CN203686056 U CN 203686056U
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- Prior art keywords
- lock pin
- differential
- clutch
- dish
- carrier body
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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
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- 230000013011 mating Effects 0.000 claims description 40
- 241001125879 Gobio Species 0.000 claims description 18
- 210000005069 ears Anatomy 0.000 claims description 12
- GOLXNESZZPUPJE-UHFFFAOYSA-N spiromesifen Chemical compound CC1=CC(C)=CC(C)=C1C(C(O1)=O)=C(OC(=O)CC(C)(C)C)C11CCCC1 GOLXNESZZPUPJE-UHFFFAOYSA-N 0.000 claims description 5
- 230000007246 mechanism Effects 0.000 description 11
- 230000005540 biological transmission Effects 0.000 description 5
- 230000033001 locomotion Effects 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 238000004804 winding Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000002360 explosive Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000012856 packing Methods 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
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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
- F16H48/30—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
A differential gear train structured according to one embodiment of the utility model comprises a differential shell, a clutch disk assembly and a plurality of locking pins, wherein the differential shell can comprise a first differential shell part; the first differential shell part is provided with a first output shaft opening and comprises a plurality of clutch lug guiding elements and a plurality of locking pin joint surfaces; the clutch disk assembly comprises a plurality of annular disks arranged between annular friction disks crosswise; at least one of the annular disks and the annular friction disks can comprise a plurality of disk lugs extending in a radial direction; the disk lugs can be accepted by the corresponding clutch lug guiding elements; the locking pins are accepted by the locking pin joint surfaces of the first differential shell part connected in series with the clutch lug guiding elements.
Description
Technical field
The utility model is broadly directed to differential gear mechanism and relates more particularly to a kind of differential casing of the lock pin with the ear guiding element series winding being configured to and stretch out from respective clutch dish.
Background technique
A kind of differential gear train is provided, and it is arranged in axle assembly and for from a pair of output shaft transmitting torque of driving axial.Live axle can be by using this differential mechanism of bevel gear driving engaging with the gear ring being arranged on differential casing.In automobile application, differential mechanism allows the tire that is arranged on the arbitrary end of shaft assembly to rotate with friction speed.When Ackermann steer angle, this is very important, because outboard wheel tyre sidewall inside tire moves larger camber line distance.Like this, outside tire must with than inside tire faster speed rotate to compensate larger operating range.This differential mechanism comprises a differential casing and allows the gearing that transmits torque and allow output shaft to rotate with friction speed as required simultaneously from driving axial output shaft.This gearing generally includes and is mounted to and the side gear of output shaft rotation separately.One group of cross pin or pinion shaft are fixedly mounted in the differential casing rotating for thereupon.Install respective numbers for rotate with pinion shaft and the small gear that all engages with two side gears.
Some differential gear trains comprise change tractive force differential mechanism.Typically, clutch pack can be arranged between one of side gear and the approximal surface of differential casing.Clutch pads group or lockable mechanism operationally limit relatively rotating between this gear-box and this side gear.In this differential mechanism, realize the joint of clutch pads group or lockable mechanism by one of several different modes.Some structures comprise piston, and this plunger actuation is used for making clutch pads group to move between separation, joint and part jointing state.In some instances, differential casing is configured to hold required parts is difficult by the installing space optimization on vehicle simultaneously.
The object of background note for general description the utility model content is provided here.Here the inventor's of the present utility model who mentions work, the degree that background technique part is described, and the aspect of the description can be not limiting as prior art is both indefinite is not also impliedly identified as prior art of the present utility model.
Model utility content
According to the differential gear train of the utility model one example constructions, comprise differential casing, clutch pads group and multiple lock pin.This differential casing can comprise the first differential carrier body, and this first differential carrier body has the first output shaft opening and comprises multiple clutch ear guiding elements and multiple lock pin engaging surface.The second differential carrier body has the second output shaft opening.Clutch pads group can comprise multiple annular disks, and described multiple annular slabs are arranged between multiple annular friction dishes across.In annular disk and annular friction dish, at least one can comprise multiple dish ears that radially extend, and described dish ear can be received by corresponding multiple clutch ear guiding elements.Described multiple lock pin can be by receiving with multiple first lock pin mating faces of the first differential casing of described clutch ear guiding element conllinear setting.This lock pin can be arranged between the first and second differential carrier bodies and be configured to forbid relatively rotating of the first and second differential carrier bodies.
According to additional technical feature, each can the setting along clutch ear guidance axis in described multiple clutch ear guiding elements.In described multiple the first lock pin engaging surface each along first lock pin engaging surface arrange.Each clutch ear guidance axis and corresponding the first lock pin engaging surface axis are conllinear.In a structure, whole multiple annular disks of clutch pads group comprise multiple radially extension dish ears.Described multiple radially extension dish ear can be along corresponding multiple longitudinal dish ear Axis Extensions.At least one dish gudgeon line is crossing with at least one lock pin.In another structure, each dish gudgeon line of multiple longitudinal dish gudgeon lines is crossing with lock pin.The second differential carrier body comprises multiple the second lock pin engaging surfaces.The plurality of lock pin is received by multiple the second lock pin mating faces.This second lock pin engaging surface can be formed by the blind hole being formed in the second differential carrier body.
Also, according to other features, this lock pin can be threadless.Multiple fastening pieces can be threaded togather the first and second differential casings.Each lock pin can arrange with adjacent fastening piece radially adjoining.
Comprise differential casing, clutch pads group and multiple lock pin according to the differential gear mechanism of other latent structures of the utility model.This differential casing comprises the first differential carrier body, and this first differential carrier body has the first outlet opening and comprises multiple clutch ear guiding elements and multiple the first lock pin mating face.The second differential carrier body has the second output shaft opening.Clutch pads group has multiple annular disks, and described annular disk is arranged between multiple annular friction dishes across.This clutch pads group comprises multiple radially extension dish ears, this radially extension dish ear received by corresponding multiple clutch ear guiding elements.The plurality of radially extension dish ear arranges along corresponding multiple longitudinal dish gudgeon lines.The plurality of lock pin can be received by multiple first lock pin mating faces of the first differential casing.This lock pin be arranged on first and differential carrier body between and be configured to forbid the relative movement of the first and second differential carrier bodies.The plurality of longitudinal dish gudgeon line intersects with corresponding lock pin.
According to additional technical feature, each can the setting along clutch ear guidance axis in described multiple clutch ear guiding elements.In described multiple the first lock pin engaging surface each along first lock pin engaging surface arrange.Each clutch ear guidance axis and corresponding the first lock pin engaging surface axis are conllinear.
Also, according to other feature, the second differential carrier body comprises multiple the second lock pin mating faces.The plurality of lock pin is received by multiple the second lock pin mating faces.The second lock pin mating face is formed by the blind hole being formed in the second differential carrier body.Lock pin can be threadless.Multiple fastening pieces can be threaded togather the first and second differential carrier bodies.Each lock pin can arrange with adjacent fastening piece radially adjoining.
Comprise differential casing, clutch pads group, multiple non-threaded lock pins, and multiple fastening piece according to the differential gear mechanism of the utility model additional technical feature structure.This first differential carrier body has the first output shaft opening and comprises multiple clutch ear guiding elements and multiple the first lock pin mating face.The second differential carrier body has the second output shaft opening and multiple the second lock pin mating face.This clutch pads group has multiple annular disks, and described multiple annular disks are arranged between multiple annular friction dishes across.In annular disk and annular friction sheet, at least one comprises multiple dish ears that radially extend, and this dish ear is received by corresponding multiple clutch ear guiding elements.Multiple non-threaded lock pins are received by multiple first lock pin mating faces of the first differential casing arranging with clutch ear guiding element series winding and the second lock pin mating face of the second differential casing.This lock pin is arranged between the first and second differential carrier bodies and is configured to forbid the relative movement of the first and second differential carrier bodies.The plurality of fastening piece is threaded togather the first and second differential carrier bodies.
According to additional technical feature, each can the setting along clutch ear guidance axis in described multiple clutch ear guiding elements.In described multiple the first lock pin engaging surface each along first lock pin engaging surface arrange.Each clutch ear guidance axis and corresponding the first lock pin mating face axis are conllinear.In other structure, whole multiple annular disks of clutch pads group comprise multiple radially extension dish ears.Described multiple radially extension dish ear can be along corresponding multiple longitudinal dish ear Axis Extensions.At least one dish gudgeon line is crossing with at least one lock pin.Each dish gudgeon line of multiple longitudinal dish gudgeon lines is crossing with lock pin.
Brief description of the drawings
To become and be easier to understand completely with detailed description the utility model content with reference to the accompanying drawings, wherein:
Fig. 1 is the schematic diagram comprising according to the example vehicle transmission system of the differential gear mechanism of the utility model example constructions;
Fig. 2 is according to the front perspective view of the limited-slip differential assembly of the utility model one embodiment's structure;
Fig. 3 is by the front perspective view of the limited-slip differential assembly of the Fig. 2 shown in perspective differential casing;
Fig. 4 is the side view of the limited-slip differential assembly of Fig. 2;
Fig. 5 is the sectional view along the limited-slip differential assembly of the line 5-5 of Fig. 2;
Fig. 6 is the sectional view along the limited-slip differential assembly of the line 6-6 of Fig. 4;
Fig. 7 is the explosive view of clutch pads group, lock pin and the first and second differential carrier bodies of the limited-slip differential assembly of Fig. 2;
Fig. 8 is the front perspective view of the first differential carrier body of Fig. 7;
Fig. 9 is the front perspective view of the lock pin of Fig. 7;
Figure 10 is the front perspective view of the second differential carrier body of Fig. 7;
Figure 11 is the clutch pads group of Fig. 7 and the side view of lock pin; With
Figure 12 is the clutch pads group of Fig. 7 and the detailed side view of lock pin.
Embodiment
First with reference to figure 1, it illustrates an example vehicle transmission system and represents with reference character 10 generally.Example vehicle transmission system 10 described herein is the f-w-d vehicles for having horizontal installation motor 12, although other structures also can be used for the utility model.Motor 12 provides rotation output to speed changer 14.
Transmission system 10 also comprises transaxle 22 and has the limited-slip differential assembly 30 of planetary gear set 16, clutch pack 32 and differential gear assembly 34.Limited-slip differential assembly 30 is received within housing 36 and moves to drive a pair of axletree 40 and 42 being connected with front driving wheel 44 and 48 respectively.Conventionally, limited-slip differential assembly 30 is used as traditional open type differential in normal working state, until need deflecting torque.When detecting or while anticipating loss of traction, clutch pack 32 by selectively actuatable to produce the shift ratio for this situation optimum.
Speed changer 14 receives rotation output and provides rotation input to limited-slip differential assembly 30 from motor 12.Further, speed changer 14 can move between the rotation input with the rotation output at motor 12 and limited-slip differential assembly 30 various velocity ratios are provided.
Differential gear assembly 34 comprise be mounted to respectively with axle 40 and 42(and the first and second driving wheels 44 and 48) rotate a pair of side gear 60 and 62.Side gear 60 and 62 has the first and second axle openings 64 and 65(Fig. 5).Multiple cross pins or pinion shaft 66 are fixedly mounted on differential casing 54 for rotate thereupon.Install and be applied to mutually multiple small gears 70 that rotate with pinion shaft 66 and that all engage with two side gears 60 and 62.In greater detail in open configuration, differential gear assembly 34 works to allow axle 40 and 42 to rotate with friction speed below.
Clutch pack 32 connects planetary gear set 16 and differential gear assembly 34.Clutch pack 32 comprises clutch pads group 72 and clutch actuator 73.Clutch pads group 72 comprises multiple annular disks 74 between multiple annular friction dishes 78 that is inserted in.Multiple annular disks 74 can connect into one in differential casing 54 and differential gear assembly 34 and rotate.Multiple annular friction dishes 78 can connect into the another one in differential casing 54 and differential gear assembly 34 and rotate.In the embodiment shown, multiple annular disks 74 connect into for rotating for example spline of differential casing 54(and insert the internal diameter 76 of differential casing 54) and multiple annular friction dish 78 for example connect into, for rotate (, the external diameter 80 of spline inserting side gear 60) with differential gear assembly 34.Be appreciated that annular friction dish 78 can be supported for rotating by any one or both in side gear 60 or 62 simultaneously.
In the time of the engagement positio of clutch pack 32 in it, thus multiple annular disk 74 and annular friction dish 78 setting intersected with each other work and surmount each other and rotate with substantially discontiguous relation.But, it will be appreciated by those skilled in the art that it is relative that term used herein " does not contact ", do not mean that must represent when clutch pack 32 during in separated state annular disk 74 absolutely not contact with annular friction disk 78.When clutch pack 32 is during in engagement positio or part joint construction, annular disk 74 and annular friction dish 78 relative to each other axial motion become frictional engagement, reduce thus relatively rotating between annular disk 74 and annular friction dish 78.With which, in the time of the engagement positio of clutch pack 32 in it, side gear 60 rotates together with 42 with 48 axle 40 with driving wheel 44 with 62.
With reference now to accompanying drawing 2-6,, will the additional technical feature of differential gear assembly 34 be described.Differential casing 54 comprises having first output shaft opening 92(Fig. 3) the first differential carrier body 90, and there is 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.Although other structures are also fine, in this example, fastening piece comprises hex head bolt.
In the time that clutch pack 32 is worked, piston 82 can cause the actuating towards and away from (in substantially horizontal as shown in Figure 3) clutch pads group 72.The actuating of piston 82 can cause by the predetermined hydraulic pressure amount that is delivered to clutch pack 32, and this clutch pack 32 produces optimum shift ratio for this situation to keep suitable motion difference in wheel speed, is predictably clamped as two wheels.In the example shown, piston 82 makes annular disk 74 and annular friction dish 78 frictional engagement towards the actuating (as shown in Figure 5 to the right) of engagement positio, locking differential gear assembly 34 thus, and side gear 60 and 62 rotates with identical speed like this.
Counter mass 150 is arranged on the first differential carrier body 190.This counter mass 150 is configured to transmit independent role power 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 provide structure support for keeping the axial position of side gear 60.Counter mass 150 is nestedly received in the annular pass 154(Fig. 5 being formed in the first side gear 60) in.Packing ring 156 is arranged in the annular pass 154 between side gear 60 and counter mass 150.
With reference now to Fig. 3-12, the additional technical feature of differential gear assembly 34 is described.The first differential carrier body 90 comprises multiple clutch ear guiding element 170(Fig. 8), this clutch ear guiding element arranges along corresponding multiple clutch ear guidance axis 172.The first differential carrier body 90 also comprises multiple the first lock pin mating faces 180 that arrange along corresponding multiple the first lock pin engages axle 182.In the example here providing, multiple clutch ear guiding elements 170 and multiple the first lock pin mating face 180 are formed by the part circumferential surface in the first differential carrier body 90.In the example shown, multiple clutch ear guiding elements 172 and corresponding multiple the first lock pin engages axle 182 conllinear.
Clutch ear guiding element 170 is configured to receive the radially extension dish ear 190 extending from multiple annular disks 74.Like this, multiple annular disk 74 rotates jointly with differential casing 54 spline joints.Each radially extension dish ear 190 and another extension dish ear 190 align (Figure 11) radially from adjacent annular disks 74 along corresponding multiple longitudinal dish gudgeon lines 194.
Second differential carrier body 94(Figure 10) comprise multiple the second lock pin mating faces 202.In the example shown, multiple the second locking mating faces 202 are formed by the blind hole 204 that is arranged in the second differential carrier body 94.Other geometrical constructioies are also fine.
Like this, there are multiple advantages.First, the assembling of differential casing 54 is optimised with around dish ear 190 and provide material around the critical positions of lock pin 219.The point of intersection of the first and second differential carrier bodies 90 and 94 or joint line can be to the axletree 40 and 42 whole torques of transmission (Fig. 1) separately.The lock pin 210 whole torques of common management also distribute whole torques around differential casing 54.
Provide to embodiment front description object be explain and explanation.Be not inclined to detailed or restriction the utility model.Indivedual elements or the feature of specific embodiment are not limited to this specific embodiments conventionally, still, anyly applicable be interchangeable and can be applied in selected embodiment, even if do not illustrate specially or describe.Similarly also can there be a lot of variation patterns.These variations are not considered as departing from the utility model, and all such modifications are believed to comprise and fall within the scope of the application.
Claims (20)
1. a differential gear train, is characterized in that, described differential gear train comprises:
Differential casing, described differential casing has
The first differential carrier body, this first differential carrier body has the first output shaft opening and comprises multiple clutch ear guiding elements and multiple the first lock pin mating face;
The second differential carrier body, this second differential carrier body has the second output shaft opening;
Clutch pads group, this clutch pads group has the multiple annular disks that are arranged on across between multiple annular friction dishes, at least one in wherein said annular disk and annular friction dish comprises multiple radially extension dish ears of being received by corresponding multiple clutch ear guiding elements, and
Multiple lock pins, the plurality of lock pin is by receiving with multiple first lock pin mating faces of the first differential casing of described clutch ear guiding element conllinear setting, and this lock pin is arranged between the first and second differential carrier bodies and is configured to prevent relatively rotating of the second differential carrier body.
2. differential gear train as claimed in claim 1, it is characterized in that, each can setting along clutch ear guidance axis in described multiple clutch ear guiding element, and each in wherein said multiple the first lock pin mating face arranges along the first lock pin mating face axis, wherein each clutch ear guidance axis and corresponding the first lock pin mating face axis conllinear.
3. differential gear train as claimed in claim 2, it is characterized in that, whole multiple annular disks of clutch pads group comprise multiple radially extension dish ears, and wherein said multiple radially extension dish ears are along corresponding multiple longitudinal dish ear Axis Extensions, and wherein at least one dish gudgeon line is crossing with at least one lock pin.
4. differential gear train as claimed in claim 3, is characterized in that, each dish gudgeon line of described multiple longitudinal dish gudgeon lines is crossing with lock pin.
5. differential gear train as claimed in claim 1, is characterized in that, the second differential carrier body comprises multiple the second lock pin mating faces, and wherein the plurality of lock pin is received by described multiple the second lock pin mating faces.
6. differential gear train as claimed in claim 5, is characterized in that, the second lock pin mating face is formed by the blind hole being formed in the second differential carrier body.
7. differential gear train as claimed in claim 1, is characterized in that, described lock pin is threadless.
8. differential gear train as claimed in claim 7, is characterized in that, also comprises multiple fastening pieces that the first and second differential carrier bodies are threaded togather.
9. differential gear train as claimed in claim 8, is characterized in that, each lock pin is arranged to and adjacent fastening piece radially adjoining.
10. a differential gear train, is characterized in that, described differential gear train comprises:
Differential casing, described differential casing has
The first differential carrier body, this first differential carrier body has the first output shaft opening and comprises multiple clutch ear guiding elements and multiple the first lock pin engaging surface;
The second differential carrier body, this second differential carrier body has the second output shaft opening;
There is the clutch pads group that is arranged on across the multiple annular disks between multiple annular friction dishes, described clutch pads group comprises multiple radially extension dish ears of being received by corresponding multiple clutch ear guiding elements, and described multiple radially extension dish ears arrange along corresponding multiple longitudinal dish gudgeon lines; With
Multiple lock pins of being received by multiple first lock pin mating faces of the first differential casing, lock pin is arranged between the first and second differential carrier bodies and is configured to forbid relatively rotating of the first and second differential carrier bodies, and wherein said multiple longitudinal dish gudgeon lines intersect with corresponding lock pin.
11. differential gear trains as claimed in claim 10, it is characterized in that, each can setting along clutch ear guidance axis in described multiple clutch ear guiding element, and each in wherein said multiple the first lock pin mating face arranges along the first lock pin mating face axis, wherein each clutch ear guidance axis and corresponding the first lock pin mating face axis conllinear.
12. differential gear trains as claimed in claim 10, is characterized in that, the second differential carrier body comprises multiple the second lock pin mating faces, and wherein the plurality of lock pin is received by described multiple the second lock pin mating faces.
13. differential gear trains as claimed in claim 12, is characterized in that, the second lock pin mating face is formed by the blind hole being formed in the second differential carrier body.
14. differential gear trains as claimed in claim 10, is characterized in that, described lock pin is threadless.
15. differential gear trains as claimed in claim 14, is characterized in that, also comprise multiple fastening pieces that the first and second differential carrier bodies are threaded togather.
16. differential gear trains as claimed in claim 15, is characterized in that, each lock pin is arranged to and adjacent fastening piece radially adjoining.
17. 1 kinds of differential gear trains, is characterized in that, described differential gear train comprises:
Differential casing, described differential casing has
The first differential carrier body, this first differential carrier body has the first output shaft opening and comprises multiple clutch ear guiding elements and multiple the first lock pin mating face;
The second differential carrier body, this second differential carrier body has the second output shaft opening and multiple the second lock pin mating face;
Have the clutch pads group that is arranged on across the multiple annular disks between multiple annular friction dishes, wherein at least one of annular disk and annular friction dish comprises multiple radially extension dish ears, this radially extension dish ear received by corresponding multiple clutch ear guiding elements;
Multiple without screw fastening shotpin, described multiple without screw fastening shotpin by receiving with multiple first lock pin mating faces of the first differential casing and multiple second lock pin mating faces of the second differential casing of the setting of described clutch ear guiding element conllinear, described lock pin is arranged between the first and second differential carrier bodies and is configured to forbid relatively rotating of the first and second differential carrier bodies; With
Multiple fastening pieces that the first and second differential carrier bodies are threaded togather.
18. differential gear trains as claimed in claim 17, it is characterized in that, each in described multiple clutch ear guiding element arranges along clutch ear guidance axis, and each in wherein said multiple the first lock pin mating face arranges along the first lock pin mating face axis, wherein each clutch ear guidance axis and corresponding the first lock pin mating face axis conllinear.
19. differential gear trains as claimed in claim 18, it is characterized in that, whole multiple annular disks of clutch pads group comprise multiple radially extension dish ears, wherein said multiple radially extension dish ear is along corresponding multiple longitudinal dish ear Axis Extensions, and wherein at least one dish gudgeon line is crossing with at least one lock pin.
20. differential gear trains as claimed in claim 19, is characterized in that, each dish gudgeon line of described multiple longitudinal dish gudgeon lines is crossing with lock pin.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201261712239P | 2012-10-10 | 2012-10-10 | |
| US61/712,239 | 2012-10-10 | ||
| US201361870832P | 2013-08-28 | 2013-08-28 | |
| US61/870,832 | 2013-08-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203686056U true CN203686056U (en) | 2014-07-02 |
Family
ID=50235670
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320740445.4U Expired - Lifetime CN203686056U (en) | 2012-10-10 | 2013-10-09 | Differential gear train |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN203686056U (en) |
| DE (1) | DE202013008948U1 (en) |
-
2013
- 2013-10-09 CN CN201320740445.4U patent/CN203686056U/en not_active Expired - Lifetime
- 2013-10-09 DE DE201320008948 patent/DE202013008948U1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| DE202013008948U1 (en) | 2014-02-18 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190703 Address after: Dublin, Ireland Patentee after: Eaton Intelligent Power Co.,Ltd. Address before: Ohio, USA Patentee before: Eaton Corp. |
|
| TR01 | Transfer of patent right | ||
| CX01 | Expiry of patent term |
Granted publication date: 20140702 |
|
| CX01 | Expiry of patent term |