CN102494102A - Hydraulic-control limited rotational speed difference differential - Google Patents
Hydraulic-control limited rotational speed difference differential Download PDFInfo
- Publication number
- CN102494102A CN102494102A CN2011104273019A CN201110427301A CN102494102A CN 102494102 A CN102494102 A CN 102494102A CN 2011104273019 A CN2011104273019 A CN 2011104273019A CN 201110427301 A CN201110427301 A CN 201110427301A CN 102494102 A CN102494102 A CN 102494102A
- Authority
- CN
- China
- Prior art keywords
- gear
- cover plates
- planetary pinion
- differential
- cover plate
- 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
Images
Landscapes
- Retarders (AREA)
Abstract
A hydraulic-control limited rotational speed difference differential transmission device is used in a transmission system for resolving and transmitting one revolution motion to two output shafts, and is typically applied in the dynamic input and the differential output for a vehicle driving wheel. In the invention, twelve respective sealed spaces are formed between a wheel train comprising a plurality of cylindrical gears and two plate-shaped cover plates, so as to convert the three operation states of the differential in a self adapting manner, that is, when the resistance of the two output shafts is the same, the two shafts turn around synchronously; when the difference of the resistance of the two output shafts is small and the difference of the rotational speed of the two input shafts is smaller, oil flows from six high-pressure zones to six low-pressure zones through a clearance, the flowing resistance of liquid is smaller, differential motion of the two shafts is realized; and when the rotational speed difference of the two output shafts is bigger, the flowing resistance of liquid is obviously increased, so that the differential speed of the two output shafts is prevented from being too big, the two shafts can transmit different rotary moment and effectively transmit dynamic force, as a result, the characteristic of differential speed and differential driving force is realized, the problem of differential speed and no driving force difference of the common differential is solved, the market prospect is wide.
Description
Technical field
The present invention relates to a kind of transmission device; Be used for transmission system same rotation motion is delivered to two output shafts simultaneously; Two output shafts can turn round synchronously, can also allow two output shafts that speed discrepancy is to a certain degree arranged simultaneously, and typical application is the power input of driving wheel of vehicle and realizes differential motion.
Background technique
When by a wheel input power, and need diaxon output and two output wheels to need run-in synchronism sometimes, when satisfying certain differential sometimes again and requiring, then must use differential mechanism.Differential mechanism typical structure commonly used at present is the founder Louis of French Renault before 100 years. the Reynolds invention, its basic comprising part is cone gear and cross axle.Be characterized in the not poor power of differential, though promptly two output wheels can be realized differential motion well, the output drive strength of two-wheeled is identical, and effective driving force of final output is by the less wheel decision of suffered frictional force.Thereby, to take turns when occurring skidding one, cause vehicles can't be advanced.The limited differential mechanism of Torsen is to utilize two worm gears, worm structure; Realize differential function, utilized different these principles of the forward and reverse transmission efficiency of worm drive, when realizing differential motion; The driving force of two-wheeled also can have bigger difference, thus the single wheel drive problem when having solved differential.
Summary of the invention
Technical problem to be solved by this invention is: through the reasonable combination of cylindrical gears; Not only realize under the situation of single power source input; Realize that the same speed output of diaxon exports two kinds of working staties with differential, and when differential is exported, overcome the characteristic defective of " the not poor power of differential " that open differential is difficult to overcome; Realize the self adaption conversion of three kinds of states of differential mechanism working procedure preferably: when promptly two output shaft resistances were identical, diaxon turned round synchronously; Two output shaft resistances have a small amount of difference, two output shaft speed discrepancies again hour, diaxon can carry out differential motion; And when two output shaft speed discrepancies arrive to a certain degree greatly, realize the characteristic of " not only differential but also poor power ", can there be bigger torque differences in diaxon.
Technical solution of the present invention is:
The limited slip differential mechanism of a kind of hydraulic control comprises power input wheel, two disc type cover plates, 3～6 pairs of compound planet gear assemblies, two output wheel, centers sealing axle, central gears that are made up of the internal tooth cylindrical gears, is used to support the rotating bearing of each part, joint bolt and shell.
Power input wheel is a ring-type, and outer rim has the gear teeth or race to realize the power input; Endoporus is circular hole or outer selenodont hole; On the both ends of the surface of power input wheel, pass through joint bolt fixed disc type cover plate respectively.The cover plate center is porose, and 3～6 pairs of circular holes evenly distribute on the same circumference outside center hole on the end face; Periphery hole on two cover plates aligns each other, and the compound planet gear assembly is housed in the periphery hole of two cover plates.The quantity of the periphery hole on the quantity of compound planet gear assembly and the cover plate is identical.The compound planet gear assembly is made up of two planetary pinions inside and outside two sections axles that cooperate with two cover plate periphery holes and two cover plates, forms the structural type of " shaft part-gear-shaft part-gear "; All planetary pinions between two cover plates mesh successively, have constituted the sealing Transmitted chains of an annular.Planetary top circle between two cover plates is just tangent with the bore area of power input wheel, thereby forms six each self-enclosed spaces between the interior edge face of the bore area of wheel for inputting, two cover plates, the planetary pinion gear teeth between two cover plates.Overhanging planetary pinion in the compound planet gear assembly is positioned at the then outer of cover plate, and they alternately stretch out from the left and right sides, promptly stretches out from the cover plate left side like first, the 3rd, the 5th gear, and then second, the 4th, the 6th gear stretches out from the cover plate right side.Simultaneously; In the center hole of cover plate, run through center sealing axle; And the outer cylinder surface of center sealing axle too and the planetary tooth top between two cover plates tangent, thereby can form other six each self-enclosed spaces again between the planetary gear of the interior edge face of the outer surface of center sealing axle, two cover plates, compound planet gear assembly.After the assembling, with the fluid that is full of certain viscosity in 12 enclosed spaces, like thick oil or silicone oil.Central gear is equipped with at the two ends of sealing axle in the outer side center of cover plate respectively, the overhanging gear outer gearing of central gear and compound planet gear assembly, engagement in the overhanging gear of compound planet gear assembly and the output gear simultaneously.Output gear connects with outside through its center hole or outrigger shaft.Power input wheel overlaps with the rotational axis of output gear, and connects with shell through bearing respectively.
Technique effect of the present invention is: it have simple in structure, cost of production is low, easy for installation.Not only can make two output shafts realize the function of differential through the train that constitutes between gear, but also can make the different torque of two output shafts output, realize the effect of " not only differential but also poor power ".When two output wheels have when differential, 12 enclosed space interval ground have six to form zone of high pressure, and other six form low pressure areas, and viscosity fluid is flowed to low pressure area by the zone of high pressure through the gap.When speed was low, the fluid flow resistance was less, thereby can not impact differential function; And when differential speed was big, oil transportation flow dynamic resistance then can significantly increase, thereby can prevent that two output shaft differential velocities are excessive; Make diaxon can transmit different torques, realize difference power function.
Description of drawings
The limited slip differential axle of Fig. 1 hydraulic control is to the sectional structure schematic representation.What wherein cylindrical upper half part of power input wheel was drawn is the gear teeth of cylindrical gears, and it is the grooved of belt wheel that lower half portion is drawn; Figure medium power wheel for inputting endoporus is a circular hole, and the sealing axle is independently cylindrical.
The limited slip differential axle of Fig. 2 hydraulic control is to the sectional structure schematic representation; What wherein outer rim upper half part of power input wheel was drawn is the gear teeth of cone gear, and it is the gear teeth of worm gear that lower half portion is drawn; And the cover plate structure to Fig. 1 changes: protruding shaft part is made in the inside and outside both sides of discoid Cover center section; Accomplish Fig. 1 center sealing spindle speed function; Mounting center gear on the cover plate central shaft that give prominence in the cover plate outside, side-prominent shaft part is a selenodont sealing axle 25 in the cover plate in the cover plate.
Fig. 3 is corresponding A-A cross-sectional view in the limited slip differential mechanism of Fig. 1 and Fig. 2 hydraulic control.
Fig. 4 is a corresponding B-B cross-sectional view in the limited slip differential mechanism of Fig. 1 hydraulic control.
Fig. 5 is a corresponding B-B cross-sectional view in the limited slip differential mechanism of Fig. 2 hydraulic control.Be with the difference of Fig. 4: figure medium power wheel for inputting endoporus is outer selenodont hole, selenodont sealing axle in the side-prominent shaft part cover plate in the cover plate, and the crescent moon number of outer selenodont hole and interior crescent moon profile shaft is identical with the planetary pinion number between two cover plates.Match between the planetary pinion between outer selenodont hole and interior crescent moon profile shaft and cover plate, further improved the sealing between them, thereby improved " difference power " ability of the limited slip differential of hydraulic control differential mechanism.
Fig. 6 is a corresponding C-C cross-sectional view in Fig. 1 and the limited slip differential of Fig. 2 hydraulic control differential mechanism.Among the figure: 1 power input wheel, 2 disc type cover plates, 3 compound planet gear assemblies, 4 output gears, 5 centers sealing axle, 6 central gears; 7 bearings, 8 joint bolts, 11 gear teeth, 12 races, 14 circular holes; 15 outer selenodont holes, 21 cover central holes, 22 cover plate periphery holes, 23 cover plate tapped holes, 24 cover plate central shafts; Selenodont sealing axle in 25 plates, 31 shaft parts, the planetary pinion between 32 shaft parts, 33 liang of cover plates, 34 overhanging planetary pinions; The gear teeth in 41 output gears, 42 output gear outrigger shafts, 43 output gear center holes, 44 output gear outer cylinder surfaces, the outer cylinder surface of 51 centers sealing axle.
Embodiment
Be described in detail specific embodiment of the present invention below in conjunction with technological scheme and accompanying drawing.
Embodiment 1
Among Fig. 1, what cylindrical upper half part of power input wheel was drawn is the gear teeth of cylindrical gears, and it is the grooved of belt wheel that lower half portion is drawn; Figure medium power wheel for inputting endoporus is a circular hole, and the sealing axle is independently cylindrical.
As shown in Figure 1, power input wheel 1, two disc type cover plates 2, three～six pairs of compound planet gear assemblies 3, two output wheel 4, center sealing axle 5 and central gears 6 that constitute by the internal tooth cylindrical gears and be used to support the rotating bearing of each part 7, joint bolt 8 and shell and constitute.
Power input wheel 1 is a ring-type, and outer rim has the gear teeth 11 or race 12 to realize the power input, and endoporus is circular hole 14 or outer selenodont hole 15; At the tapped hole 23 fixed disc type cover plates 2 that pass through respectively on the both ends of the surface of power input wheel 1 on joint bolt 8 and the cover plate 2; Cover plate 2 centers porose 21; 3～6 pairs of circular holes 22 evenly distribute on the same circumference outside center hole on the end face; Below be that example explains that all the other are similar with 3 pairs, explanation no longer one by one.Periphery hole 22 on two cover plates 2 aligns each other, in the periphery hole 22 of two cover plates duplex planet wheel assembly 3 is housed.The quantity of the periphery hole 22 on the quantity of duplex planet wheel assembly 3 and the cover plate 2 is identical.Compound planet gear assembly 3 is made up of the two sections axles 31,32 that cooperate with two cover plate periphery holes 22 and two cover plates, 2 inside and outside two planetary pinions 33,34, forms the structural type of " shaft part-gear-shaft part-gear "; Gear 33 has 6 between two cover plates 2, they mesh successively, has constituted the sealing Transmitted chains of an annular.The top circle of the planetary pinion 33 between two cover plates is just tangent with the internal surface of the circular hole 14 of power input wheel 1, thereby will form six each self-enclosed spaces between the interior edge face of the internal surface of circular hole 14, two cover plates 2, planetary pinion 33 gear teeth between two cover plates.34 of overhanging planetary pinions in the compound planet gear assembly 3 lay respectively at the then outer of cover plate 2; And alternately stretch out from the left and right sides; Promptly stretch out from the cover plate left side like first, the 3rd, the 5th gear 34, then second, the 4th, the 6th gear 34 stretches out from the cover plate right side.Simultaneously, in the center hole 21 of cover plate 2, run through center sealing axle 5, and the tooth top of the outer cylinder surface of center sealing axle 5 and the planetary pinion 33 between two cover plates is tangent; Thereby can form other six each self-enclosed spaces again between the gear teeth of the outer cylinder surface 51 of center sealing axle, the interior edge face of two cover plates 2, the planetary pinion 33 between two cover plates.After the assembling, with the fluid that is full of certain viscosity in 12 enclosed spaces, like thick oil or silicone oil.Central gear 6 is equipped with at the two ends of sealing axle 5 in the outer side center of cover plate 2 respectively, overhanging gear 34 outer gearings of central gear 6 and compound planet gear assembly 3, the interior gear teeth 41 interior engagements of the overhanging gear 34 of compound planet gear assembly 3 and output gear 4 simultaneously.Output gear 4 connects with outside through its center hole 43 or outrigger shaft 42.Power input wheel 1 overlaps with the rotational axis of output gear 4, and output gear 4 is installed bearing 7 through its outer cylinder surface 44 and connected with shell.
Embodiment 2
Among Fig. 2, what outer rim upper half part of power input wheel was drawn is the gear teeth of cone gear, and it is the gear teeth of worm gear that lower half portion is drawn; And the cover plate structure to Fig. 1 changes: protruding shaft part is made in the inside and outside both sides of discoid Cover center section; Accomplish Fig. 1 center sealing spindle speed function; Mounting center gear on the cover plate central shaft that give prominence in the cover plate outside, side-prominent shaft part is a selenodont sealing axle in the cover plate in the cover plate.
As shown in Figure 2, this mode of execution is with the difference of Fig. 1: power input wheel 1 is ring-type, and its outer rim can be upper half part during the gear teeth 11 of cone gear are schemed, or lower half portion among the gear teeth figure of worm gear, realizes the power input through power input wheel 1.Power input wheel 1 endoporus inner periphery is along the planetary pinion 33 the same number of selenodonts that circumferentially are uniformly distributed with between manufacturing and two cover plates; Make power input wheel 1 endoporus become outer selenodont hole 15; The tip cylinder of the corresponding planetary pinion 33 between its selenodont curved surface and cover plate is isometrical and concentric, thereby makes their appearance curved surface match.
Simultaneously, the cover plate structure to Fig. 1 changes.As shown in Figure 2; Protruding shaft part is made in the inside and outside both sides of discoid Cover center section; The outstanding laterally shaft part in cover plate center is a cover plate central shaft 24; Central gear 6 is installed, overhanging gear 34 outer gearings of central gear 6 and compound planet gear assembly 3, engagement in the interior gear teeth 41 of the overhanging gear 34 of compound planet gear assembly 3 and output gear 4 simultaneously on it.Output gear 4 connects with outside through its center hole 43 or outrigger shaft 42.Power input wheel 1 overlaps with the rotational axis of output gear 4, and output gear 4 is installed bearing 7 through its outer cylinder surface 44 and connected with shell.Outstanding to the inside shaft part periphery is along the planetary pinion 33 the same number of selenodonts that circumferentially are uniformly distributed with between manufacturing and two cover plates at the cover plate center; Make the outstanding to the inside shaft part in cover plate center become selenodont sealing axle 25 in the cover plate; The tip cylinder of the corresponding planetary pinion 33 between its selenodont curved surface and cover plate is isometrical and concentric, thereby makes their appearance curved surface match.
The difference of Fig. 5 and Fig. 4 is: figure medium power wheel for inputting endoporus is outer selenodont hole, selenodont sealing axle in the side-prominent shaft part cover plate in the cover plate, and the crescent moon number of outer selenodont hole and interior crescent moon profile shaft is identical with the planetary pinion number between two cover plates.Match between the planetary pinion between outer selenodont hole and interior crescent moon profile shaft and cover plate, further improved the sealing between them, thereby improved " difference power " ability of the limited slip differential of hydraulic control differential mechanism.
Claims (5)
1. limited slip differential mechanism of hydraulic control; Comprise power input wheel (1), two disc type cover plates (2), three～six pairs of compound planet gear assemblies (3), two power output wheels (4); It is characterized in that power input wheel (1) is annular; Its external peripheral surface is useful on the tooth or the groove of transferring power, and the center portion is a cavity; Each cover plate (2) is a disc, with the coaxial circumference of external cylindrical surface on distributing and the identical circular port of compound planet gear assembly (3) quantity; Compound planet gear assembly (3) is the assemblying body of shaftgear, is shaped as the structural type of " axle-tooth-axle-tooth "; Power output wheel (4) one ends are made up of the internal tooth cylindrical gears, and the other end is axle or the hole that links with other; Shrouding disc (2) is fixed on the both ends of the surface of power input wheel (1) coaxially; Compound planet gear assembly (3) is installed in the circular hole that circumferentially is uniformly distributed with of shrouding disc (2); Planetary pinion (33) between two cover plates in all compound planet gear assemblies (3) is positioned between two shrouding discs (2); Overhanging planetary pinion (34) alternately stretches out in shrouding disc (2) both sides; And the planetary pinion (33) between each two cover plate all with two two cover plates of adjacent component between planetary pinion (33) be meshed, thereby form a gear engagement chain link; The interior gear teeth (41) of a power output gear (4) and engagement in the overhanging planetary pinion (34) in a shrouding disc (2) outside, and the interior gear teeth (41) of another power output gear (4) and engagement in the overhanging planetary pinion (34) in another shrouding disc (2) outside.
2. the limited slip differential mechanism of hydraulic control as claimed in claim 1 is characterized in that power input wheel (1) endoporus is a cylindrical hole, and also there is cylindrical hole at the center of shrouding disc (2), and Yu Kongzhong is equipped with sealing axle (5); Planetary pinion (33) top circle between two cover plates in all compound planet gear assemblies (3) is all tangent with power input wheel (1) central cylindrical hole; The width of the planetary pinion between two cover plates (33) equates with the distance between shrouding disc; Sealing axle (5) has two sections to cooperate with the center hole of shrouding disc 2 respectively, the shaft part periphery that is positioned at two shrouding discs centre then and the top circle of the planetary pinion between two cover plates (33) tangent; Be full of fluid in the space between two cover plates (2).
3. the limited slip differential mechanism of hydraulic control as claimed in claim 1; It is characterized in that power input wheel (1) endoporus is that the inner periphery edge circumferentially is uniformly distributed with the same number of selenodont of planetary pinion (33) hole that produces between two cover plates, the outstanding to the inside shaft part periphery in cover plate center is along the same number of selenodont of planetary pinion (33) that circumferentially is uniformly distributed with between manufacturing and two cover plates; Planetary pinion (33) top circle between all two cover plates is all isometrical and concentric with power input wheel (1) selenodont hole; Simultaneously; The outstanding to the inside shaft part in cover plate (2) center is isometrical and concentric, and the width of the planetary pinion between two cover plates (33) equates with the distance that lid two coils between (2); Be full of fluid in the space between two cover plates (2).
4. the limited slip differential mechanism of hydraulic control as claimed in claim 2 is characterized in that on the two ends shaft part of power sealing axle (5) central gear (6) being housed respectively, overhanging gear (34) outer gearing of central gear (6) and compound planet gear assembly (3).
5. the limited slip differential mechanism of hydraulic control as claimed in claim 3 is characterized in that the cover plate center is extruded with cover plate central shaft (24) laterally, and central gear (6) is installed on it, overhanging gear (34) outer gearing of central gear (6) and compound planet gear assembly (3).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110427301 CN102494102B (en) | 2011-12-19 | 2011-12-19 | Hydraulic-control limited rotational speed difference differential |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110427301 CN102494102B (en) | 2011-12-19 | 2011-12-19 | Hydraulic-control limited rotational speed difference differential |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102494102A true CN102494102A (en) | 2012-06-13 |
| CN102494102B CN102494102B (en) | 2013-12-25 |
Family
ID=46185949
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201110427301 Expired - Fee Related CN102494102B (en) | 2011-12-19 | 2011-12-19 | Hydraulic-control limited rotational speed difference differential |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102494102B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500687A (en) * | 2014-10-30 | 2015-04-08 | 张惠杰 | Torque guide differential |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08285047A (en) * | 1995-04-19 | 1996-11-01 | Tochigi Fuji Ind Co Ltd | Torque distributor |
| US6402656B1 (en) * | 2000-03-03 | 2002-06-11 | Mark Peralta | Limited slip differential |
| JP2002195383A (en) * | 2001-11-16 | 2002-07-10 | Tochigi Fuji Ind Co Ltd | Power system for four-wheel drive vehicle |
| CN101504065A (en) * | 2008-02-05 | 2009-08-12 | 洪涛 | Differential gear with limited differential ratio |
| CN101660597A (en) * | 2008-08-29 | 2010-03-03 | 李国铭 | Limited slip differential for cylindrical gear set |
| CN101994812A (en) * | 2009-08-11 | 2011-03-30 | 洪涛 | Differential with limited differential ratio |
| CN102022515A (en) * | 2010-12-24 | 2011-04-20 | 天津君晟成套设备有限公司 | Central differential speed reducer |
-
2011
- 2011-12-19 CN CN 201110427301 patent/CN102494102B/en not_active Expired - Fee Related
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08285047A (en) * | 1995-04-19 | 1996-11-01 | Tochigi Fuji Ind Co Ltd | Torque distributor |
| US6402656B1 (en) * | 2000-03-03 | 2002-06-11 | Mark Peralta | Limited slip differential |
| JP2002195383A (en) * | 2001-11-16 | 2002-07-10 | Tochigi Fuji Ind Co Ltd | Power system for four-wheel drive vehicle |
| CN101504065A (en) * | 2008-02-05 | 2009-08-12 | 洪涛 | Differential gear with limited differential ratio |
| CN101660597A (en) * | 2008-08-29 | 2010-03-03 | 李国铭 | Limited slip differential for cylindrical gear set |
| CN101994812A (en) * | 2009-08-11 | 2011-03-30 | 洪涛 | Differential with limited differential ratio |
| CN102022515A (en) * | 2010-12-24 | 2011-04-20 | 天津君晟成套设备有限公司 | Central differential speed reducer |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500687A (en) * | 2014-10-30 | 2015-04-08 | 张惠杰 | Torque guide differential |
| CN104500687B (en) * | 2014-10-30 | 2017-05-10 | 张惠杰 | Torque guide differential |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102494102B (en) | 2013-12-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100418732C (en) | Transmission for driving a multishaft extruder | |
| CN100465476C (en) | Main gear down device | |
| US20100167862A1 (en) | Power-dividing gear train assembly for motor vehicles | |
| AU2010238326A1 (en) | Gear train with split torque | |
| CN105051419B (en) | Transmission for a motor vehicle | |
| CN202746502U (en) | Rotary planetary reducer of mining excavator | |
| CN103797262A (en) | Clutch | |
| CN201779229U (en) | Inter-wheel differential assembly using anti-rotation washers | |
| CN203067711U (en) | Differential gear mechanism of bevel gears | |
| US3611833A (en) | Differential | |
| CN106641135B (en) | A kind of 12 speed automatic transmissions | |
| CN102619939B (en) | Centrifugal force controlled planet gear stepless transmission | |
| CN202251727U (en) | Precise cycloid oscillating tooth transmission reducer | |
| CN202901250U (en) | Forward gear and reverse gear switching mechanism of continuously variable transmission (CVT) for automobile | |
| CN102494102B (en) | Hydraulic-control limited rotational speed difference differential | |
| CN206522408U (en) | A kind of industrial robot joint reductor | |
| CN209818660U (en) | Planet wheel hub reduction gear | |
| US20050054471A1 (en) | Drive axle assembly and differential | |
| CN210617849U (en) | Novel differential transmission rear axle between parallel shafts | |
| CN203023426U (en) | Cylindrical gear power-shunting type limited slip differential | |
| CN103335069B (en) | Sieve run-out tolerance speed reducer | |
| CN102287491B (en) | Vertical type planet gearbox transmission device | |
| CN202170968U (en) | Vertical planetary gear box transmission device | |
| CN201034149Y (en) | Main retarding apparatus | |
| CN105715785A (en) | Power drive unit for motor vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131225 Termination date: 20161219 |