CN104494425B - A kind of variator with transfer case - Google Patents
A kind of variator with transfer case Download PDFInfo
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- CN104494425B CN104494425B CN201410782454.9A CN201410782454A CN104494425B CN 104494425 B CN104494425 B CN 104494425B CN 201410782454 A CN201410782454 A CN 201410782454A CN 104494425 B CN104494425 B CN 104494425B
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Abstract
The invention discloses a kind of variator with transfer case, belong to technical field of mechanical transmission, including locking and damping clutch assembly, fluid torque-converter, rotary clutch assembly, planetary transmission, PTO, built-in cycloid gear pump and turbine output shaft, the locking and damping clutch assembly pass through its locking and damping clutch is connected with the turbine seat of fluid torque-converter, turbine seat is connected with turbine output shaft, turbine output shaft is connected with planetary transmission by rotary clutch assembly, simultaneously, the pump impeller of fluid torque-converter is connected with PTO and built-in cycloid gear pump respectively, planetary transmission end is also associated with transfer box assembly.The technical program is by power is exported from former and later two directions of variator simultaneously, and torque fluctuation is distributed, outfan not on the same axis, can reasonably be assigned to front and back wheel driving torque with input, the driving force of front and back wheel is given full play to, the driveability and stability of vehicle is improve.
Description
Technical field
The invention belongs to technical field of mechanical transmission, is related to a kind of variator, more particularly, to a kind of change with transfer case
Fast device.
Background technology
At present engineering truck and special vehicle using automatic transmission be typically made up of fluid torque-converter and change speed gear box, its
Feature is coaxial transmission, it is adaptable to the machine driving of coaxially arranged, unidirectional output；It is and planetary drive system structure is compact, single
Position volumetric power density is big, it is adaptable to high-power machinery and the machinery and system of vehicle transmission that require characteristics of compact layout.Also there is part speed change
Case can be exported in front and back, realize that vehicular four wheels drive, but as its moment of torsion is fixed allocation, it is impossible to adjusted according to track situation
Suitable moment of torsion, and on good road surface and need not be very big driving force, the wasting of resources is caused using four-wheel drive.Together
When with development and increasingly sophisticated, the particularly ride characteristic and control stability of special vehicle of field operation environment of technology
Require more and more higher, such as highway traveling by property, the steering of vehicle, the stability in direction and acceleration etc., typically
Automatic transmission can not meet job requirements in certain circumstances.Therefore, need badly a kind of with higher field work adaptation
The automatic transmission of property, good acceleration and the characteristic such as handling capacity, structure be compacter, the fluid drive before taking into account
While device advantage, realize that variable torque is distributed, and when improving plant equipment field work by property, stability, steering property
Etc. performance.
The content of the invention
In order to solve the above problems, the invention provides a kind of variator with transfer case, so as to reach variable torque
The effect that distribution, gearshift performance are optimized and improved.
The present invention is achieved by following technical solution.
A kind of variator with transfer case, including locking and damping clutch assembly, fluid torque-converter, rotary clutch it is total
Into, planetary transmission, PTO, built-in cycloid gear pump and turbine output shaft, the locking and damping clutch it is total
Into being connected with the turbine seat of fluid torque-converter by its locking and damping clutch, the turbine seat is connected with turbine output shaft,
The turbine output shaft is connected with planetary transmission by rotary clutch assembly, meanwhile, the pump impeller point of the fluid torque-converter
It is not connected with PTO and built-in cycloid gear pump, the planetary transmission end is also associated with transfer box assembly.
The transfer box assembly includes driving gear, P4 gear rings, P4 sun gears, P4 planet carriers, driven gear and idle pulley, main
Moving gear is engaged with idle pulley, and idle pulley is engaged with driven gear, driven gear and P4 planet carrier spline connections, while P4 planets
Frame is engaged with P4 gear rings and P4 sun gears, and P4 gear rings are connected with rear output shaft by spline, and P4 sun gears are defeated with front by spline
Shaft connects；Driven gear another side and bell housing spline connection, bell housing pass through the 3rd rotation clutch with clutch hub
Device floating connection, clutch hub are connected with front output shaft by spline.
The rotary clutch assembly includes the first rotary clutch and the second rotary clutch, using nesting type structure,
First rotary clutch is nested in the second rotary clutch.
The planetary transmission includes P1 planet rows, P2 planet rows and P3 planet rows, and P1 planet rows include P1 gear rings, P1 rows
Carrier and P1 sun gears, P1 gear rings pass through the first brake；P2 planet rows include P2 gear rings, P2 sun gears and P2 planets
Frame, P2 gear rings are braked by second brake；P3 planet rows include P3 gear rings, P3 planet carriers and P3 sun gears, and P3 gear rings pass through
3rd brake.
The P2 sun gears and P3 sun gears are connected with jackshaft, jackshaft two ends connect respectively the first rotary clutch and
4th brake.
The invention has the beneficial effects as follows：
A kind of variator with transfer case of the present invention, by power is simultaneously defeated from former and later two directions of variator
Go out, and torque fluctuation distributed, outfan and input not on the same axis, before and after driving torque being reasonably assigned to
Wheel, gives full play to the driving force of front and back wheel, improves the driveability and control stability of vehicle；Can be abundant on smooth-riding surface
Using engine power, meet smooth-ride demand, and under more severe road conditions can by change moment of torsion distribution come
Its driving force is improved, raising engine fuel performance is reached and is improved driveability of the vehicle under poor road conditions and manipulate steady
Qualitatively effect.
Description of the drawings
Fig. 1 is the structural representation of the present invention.
In figure：1- lockings and damper clutch, 2- turbines, 3- guide wheels, 4- pump impellers, 5- PTO, 6- are built-in
Gerotor pump, 7-P1 gear rings, 8-P2 gear rings, 9-P3 gear rings, 10- driving gears, 11- rear output shafts, 12-P4 gear rings, the 13-P4 sun
Wheel, 14-P4 planet carriers, 15- driven gears, 16- idle pulleys, 17- front output shafts, 18-P3 planet carriers, 19-P3 sun gears, 20-P2
Sun gear, 21-P2 planet carriers, 22-P1 planet carriers, 23-P1 sun gears, 24- rotary clutch ring gears, 25- jackshafts, 26-
Turbine output shaft, 27- turbine seats, A- lockings and vibration damper assembly, B- fluid torque-converters, C- rotary clutch assemblies, C1- first
Rotary clutch, the second rotary clutch of C2-, the first brakes of C3-, C4- second brakes, the 3rd brakes of C5-, C6-
Four brakes, the 3rd rotary clutch of C7-, D- planetary transmissions, E- transfer box assemblies.
Specific embodiment
Technical scheme is further described below in conjunction with the accompanying drawings, but claimed scope is not limited to institute
State.
As shown in figure 1, a kind of variator with transfer case of the present invention, including locking and damping clutch assembly A,
Fluid torque-converter B, rotary clutch assembly C, planetary transmission D, PTO 5, built-in cycloid gear pump 6 and turbine are defeated
Shaft 26, locking and damping clutch assembly A pass through its locking and damping clutch 1 is connected with the turbine seat 27 of fluid torque-converter B
Connect, the turbine seat 27 is connected with turbine output shaft 26 by spline, turbine output shaft 26 passes through rotary clutch assembly C and row
Star change speed gear box D connects, and transfers power at planetary transmission D, meanwhile, the pump impeller 4 of fluid torque-converter B respectively with power output
Device 5 and built-in cycloid gear pump 6 connect, and drive built-in cycloid gear pump 6 to provide power oil for whole variator by spline
And lubricating oil, this built-in oil pump, can be with the space of effectively save hydraulic transmission system inside drive mechanism；The row
Star change speed gear box D ends are also associated with transfer box assembly E, and the fluid torque-converter B adopts traditional biphase three-element structure of single-stage.
Under locking operating mode, the pressure oil that system is provided can promote locking and damping clutch piston, realize that power is defeated
Go out device 5 to be rigidly connected with turbine 2, make turbine 2 synchronous rotary be reached with electromotor, while turbine seat 27 drives whirlpool by spline
Wheel 26 synchronous rotary of output shaft；When load is larger, locking and damping clutch piston can be disengaged, and torque-converters can be in bending moment work
Work under condition, improve the utilization rate of electromotor.
The rotary clutch assembly C includes the first rotary clutch C1 and the second rotary clutch C2, using nested type
Structure, the first rotary clutch C1 are nested in the second rotary clutch C2, share a piston shell.
First rotary clutch C1 is connected with jackshaft 25 by spline, and the second rotary clutch C2 and P2 planet carriers 21 connect
Connect, rotary clutch assembly C is bonded with P1 sun gears 23 by its rotary clutch ring gear 24.
P1 sun gears 23 are engaged with P1 gear rings 7, and P1 gear rings 7 are floating gear ring, and it is braked by the first brake C3；P1 rows
Carrier 22 is connected with P2 gear rings 8 by helical gear, and carries out axially position by thrust bearing；P2 gear rings 8 pass through second brake
C4 is braked, and carries out axially position with back-up ring.
P2 sun gears 20 and 25 spline connection of jackshaft, P2 planet carriers 21 are connected with P3 gear rings 9 by helical teeth, and lean on thrust
Bearing carries out axially position；P3 gear rings 9 are braked by the 3rd brake C5, and carry out axially position with back-up ring.
P3 sun gears 19 and 25 spline connection of jackshaft, P3 planet carriers 18 are connected to driving gear 10, wherein the 4th braking
Clutch hub floating connections of the device C6 with jackshaft 25 by the 4th brake C6.
The transfer box assembly E includes driving gear 10, P4 gear rings 12, P4 sun gears 13, P4 planet carriers 14, driven gear
15 and idle pulley 16, driving gear 10 is engaged with idle pulley 16, and idle pulley 16 is engaged with driven gear 15, driven gear 15 and P4 rows
14 spline connection of carrier, while P4 planet carriers 14 are engaged with P4 gear rings 12 and P4 sun gears 13, P4 gear rings 12 by spline with it is rear
Output shaft 11 connects, and P4 sun gears 13 are connected with front output shaft 17 by spline；Spend with bell housing 15 another side of driven gear
Bonded, with clutch hub by the 3rd rotary clutch C7 floating connections, clutch hub is defeated with front by spline for bell housing
Shaft 17 connects.
During work, pump impeller 4 is connected with electromotor, and when the engine speed is lower, fluid torque-converter B is in bending moment work
Condition, the output of electromotor are absorbed by the turbine 2 of fluid torque-converter B Jing after transmission oil effect, then by turbine output shaft 26
Output；When engine speed is higher, fluid torque-converter B is in locking operating mode, and locking and damping clutch piston are in pressure oil
Effect is lower to be connected with turbine seat 27, and engine output end is formed with turbine 2 and is rigidly connected, the power Jing turbines that electromotor is provided
Seat 27 is directly passed to turbine output shaft 26, and electromotor realizes synchronous rotary with turbine output shaft 26.Jing different transmission combinations
Different rotating ratios are reached, the power output of seven drive shifts and a reverse gear is capable of achieving, and each forward gear is capable of achieving two kinds
Moment of torsion distributes, when moment of torsion is assigned as 3:When 7, it is adapted in good road traveling, makes full use of moment of torsion, reduces oil consumption, and when torsion
Square is assigned as 1:When 1, it is adapted in the more severe road conditions downward driving such as snowfield, ladder road, ice face, mire, improves vehicle traction
Power, strengthen vehicle by performance.
Embodiment
1st, neutral gear, the 3rd brake C5 are combined under the pressure oil effect that cycloid gear pump 6 is provided, and P3 gear rings 9 are braked.By
Disengaged condition is in the first rotary clutch C1 and the second rotary clutch C2, the moment of torsion exported by turbine output shaft 26 can not
Pass to planetary transmission D, whole change speed gear box inactivity output.
2nd, one grade, the first brake C3 and the 4th brake C6 is combined under the pressure oil effect that cycloid gear pump 6 is provided,
Jackshaft 25 is braked.P1 sun gears 23 are passed to by rotary clutch ring gear 24 by the moment of torsion that turbine output shaft 26 is exported,
Then P2 gear rings 8 are passed to by P1 planet carriers 22, P2 gear rings 8 deliver torque to P3 gear rings 9 by P2 planet carriers 21, then
9 moment of torsion of P3 gear rings is exported by P3 planet carriers 18, and moment of torsion Jing driving gears 10 and idle pulley 16 are passed to driven by P3 planet carriers 18
Gear 15；When the 3rd rotary clutch C7 is combined, bell housing is connected with clutch hub, then driven gear 15 is by moment of torsion one
Side passes to front output shaft 17 by bell housing and clutch hub, and another side passes to rear output shaft 11 by P4 gear rings 12,
The rotating speed of both sides output is identical, and output torque ratio is 1 in front and back:1；When the 3rd rotary clutch C7 is not combined, bell housing with
Clutch hub disconnects, then driven gear 15 passes to front output shaft 17 by moment of torsion by P4 sun gears 13, and another side passes through
P4 gear rings 12 pass to rear output shaft 11, and both sides output speed is identical, and output torque ratio is 3 in front and back:7.
3rd, two grades, the first rotary clutch C1 and the 3rd brake C5 is combined under pressure oil effect, and P3 gear rings 9 are braked.
Jackshaft 25 is passed to by the first rotary clutch C1 by the moment of torsion that turbine output shaft 26 is exported, is transmitted by P3 sun gears 19
To P3 planet carriers 18, moment of torsion Jing driving gears 10 and idle pulley 16 are passed to driven gear 15 by P3 planet carriers 18；When the 3rd rotation
When clutch C7 is combined, bell housing is connected with clutch hub, then driven gear 15 by moment of torsion by bell housing and
Clutch hub passes to front output shaft 17, and another side is crossed P4 gear rings 12 and passes to rear output shaft 11, and the rotating speed of both sides output is identical,
Output torque ratio is 1 in front and back:1；When the 3rd rotary clutch C7 is not combined, bell housing is disconnected with clutch hub, then driven
Gear 15 is by moment of torsion while by P4 sun gears 13, passing to front output shaft 17, another side is defeated after passing to by P4 gear rings 12
Shaft 11, both sides output speed are identical, and output torque ratio is 3 in front and back:7.
4th, third gear, the first rotary clutch C1 and second brake C4 are combined under pressure oil effect, and P2 gear rings 8 are braked.
Jackshaft 25 is passed to by the first rotary clutch C1 by the moment of torsion that turbine output shaft 26 is exported, a part of moment of torsion passes through P2 too
Sun wheel 20 passes to P2 planet carriers 21, passes to P3 gear rings 9 by P2 planet carriers 21, and another part moment of torsion Jing jackshafts 25 are directly passed
P3 sun gears 19 are passed, as P3 gear rings 9 are differential with P3 sun gears 19, moment of torsion Jing P3 planet carriers 18 are exported；P3 planet carriers 18
Moment of torsion Jing driving gears 10 and idle pulley 16 are passed to into driven gear 15；When the 3rd rotary clutch C7 is combined, bell housing
It is connected with clutch hub, then moment of torsion is passed to front output shaft by bell housing and clutch hub by driven gear 15
17, another side is crossed P4 gear rings 12 and passes to rear output shaft 11, and the rotating speed of both sides output is identical, and output torque ratio is 1 in front and back:1；When
When 3rd rotary clutch C7 is not combined, bell housing is disconnected with clutch hub, then moment of torsion is passed through P4 by driven gear 15
Sun gear 13, passes to front output shaft 17, and another side passes to rear output shaft 11, both sides output speed phase by P4 gear rings 12
Together, output torque ratio is 3 in front and back:7.
5th, fourth gear, the first rotary clutch C1 and the first brake C3 are combined under pressure oil effect, and P1 gear rings 7 are braked.
P1 sun gears 23, Jing P1 planets are passed to by rotary clutch ring gear 24 by the moment of torsion part that turbine output shaft 26 is exported
Frame 22 passes to P2 gear rings 8, and another part moment of torsion passes to the P2 sun gears on jackshaft 25 by the first rotary clutch C1
20 and P3 sun gears 19；Due to P2 sun gears 20 it is differential with P2 gear rings 8,21 output torque of P2 planet carriers, and pass to P3 teeth
Circle 9, as P3 gear rings 9 are differential with P3 sun gears 19, moment of torsion Jing P3 planet carriers 18 are exported；P3 planet carriers 18 by moment of torsion Jing actively
Gear 10 and idle pulley 16 pass to driven gear 15；When the 3rd rotary clutch C7 is combined, bell housing and clutch hub phase
Connection, then moment of torsion is passed to front output shaft 17 by bell housing and clutch hub by driven gear 15, and P4 is crossed in another side
Gear ring 12 passes to rear output shaft 11, and the rotating speed of both sides output is identical, and output torque ratio is 1 in front and back:1；When the 3rd rotation clutch
When device C7 is not combined, bell housing is disconnected with clutch hub, then driven gear 15 is transmitted by moment of torsion by P4 sun gears 13
To front output shaft 17, another side passes to rear output shaft 11 by P4 gear rings 12, and both sides output speed is identical, in front and back output torque
Than for 3:7.
6th, five grades, the first rotary clutch C1 and the second rotary clutch C2 is combined under pressure oil effect, defeated by turbine
A moment of torsion part for the output of shaft 26 passes to P3 gear rings 9, another part by the second rotary clutch C2 Jing P2 planet carriers 21
Moment of torsion passes to P3 sun gears 19 by the first rotary clutch C1, due to P3 sun gears 19, P3 gear rings 9 and P3 planet carriers 18 with
26 synchronized equidirectional rotation of turbine output shaft, moment of torsion are exported by P3 planet carriers 18；P3 planet carriers 18 are by moment of torsion Jing driving gears 10
Driven gear 15 is passed to idle pulley 16；When the 3rd rotary clutch C7 is combined, bell housing is connected with clutch hub, then
Driven gear 15 is by moment of torsion while passing to front output shaft 17 by bell housing and clutch hub, another side is crossed P4 gear rings 12 and passed
Rear output shaft 11 is passed, the rotating speed of both sides output is identical, and output torque ratio is 1 in front and back:1；When the 3rd rotary clutch C7 is not tied
During conjunction, bell housing is disconnected with clutch hub, then driven gear 15 passes to front output by moment of torsion by P4 sun gears 13
Axle 17, another side pass to rear output shaft 11 by P4 gear rings 12, and both sides output speed is identical, and output torque ratio is 3 in front and back:7.
7th, six grades, the second rotary clutch C2 and the first brake C3 is combined under pressure oil effect, and P1 gear rings 7 are braked.
P1 sun gears 23, then Jing P1 rows are passed to by rotary clutch ring gear 24 by the moment of torsion part that turbine output shaft 26 is exported
Carrier 22 passes to P2 gear rings 8；Another part passes to P2 planet carriers 21 by the second rotary clutch C2.Due to P2 planet carriers
21 pass through spline connection with P3 gear rings 9, and moment of torsion is passed on P3 gear rings 9, simultaneously because the difference of P2 planet carriers 21 and P2 gear rings 8
It is dynamic, a part of moment of torsion is exported from P2 sun gears 20, P3 sun gears 19 are passed to by jackshaft 25；Due to 19 He of P3 sun gears
P3 gear rings 9 it is differential, moment of torsion is exported by P3 planet carriers 18.Moment of torsion Jing driving gears 10 and idle pulley 16 are passed to by P3 planet carriers 18
Driven gear 15；When the 3rd rotary clutch C7 is combined, bell housing is connected with clutch hub, then driven gear 15 will be turned round
Square is while pass to front output shaft 17 by bell housing and clutch hub, another side is crossed P4 gear rings 12 and passes to rear output shaft
11, the rotating speed of both sides output is identical, and output torque ratio is 1 in front and back:1；When the 3rd rotary clutch C7 is not combined, bell housing
Disconnect with clutch hub, then driven gear 15 passes to front output shaft 17 by moment of torsion by P4 sun gears 13, and another side leads to
Cross P4 gear rings 12 and pass to rear output shaft 11, both sides output speed is identical, output torque ratio is 3 in front and back:7.
8th, seven grades, the second rotary clutch C2 and second brake C4 is combined under pressure oil effect, and P2 gear rings 8 are braked.
P2 planet carriers 21 are delivered to by the second rotary clutch C2 by the moment of torsion that turbine output shaft 26 is exported, then by P2 planet carriers 21
P3 gear rings 9 and P2 sun gears 20 are delivered separately to, Jing jackshafts 25 pass to P3 sun gears 19 to the moment of torsion of P2 sun gears 20 again, by
Differential with P3 sun gears 19 in P3 gear rings 9, moment of torsion is exported by the third line carrier 18.P3 planet carriers 18 are by moment of torsion Jing driving gears
10 and idle pulley 16 pass to driven gear 15；When the 3rd rotary clutch C7 is combined, bell housing is connected with clutch hub,
Then driven gear 15 by moment of torsion while passing to front output shaft 17 by bell housing and clutch hub, P4 gear rings 12 are crossed in another side
Rear output shaft 11 is passed to, the rotating speed of both sides output is identical, and output torque ratio is 1 in front and back:1；When the 3rd rotary clutch C7 not
With reference to when, bell housing and clutch hub disconnect, then moment of torsion is passed through P4 sun gears 13 by driven gear 15, is passed to front defeated
Shaft 17, another side pass to rear output shaft 11 by P4 gear rings 12, and both sides output speed is identical, and output torque ratio is 3 in front and back:
7。
9th, reverse gear, the first brake C3 and the 3rd brake C5 are combined under pressure oil effect, P1 gear rings 7 and P3 gear rings 9
Braking, passes to P1 sun gear 23 by rotary clutch ring gear 24 by the moment of torsion that turbine output shaft 26 is exported, then Jing P1
Planet carrier 22 passes to P2 gear rings 8, as P2 planet carriers 21 and P3 gear rings 9 are braked, the P2 sun gears of 8 Jing P2 planet rows of P2 gear rings
20 pass to jackshaft 25, and P2 sun gears 20 are rotated forward, and drive jackshaft 25 and P3 sun gears 19 to rotate forward, so that
P3 planet carriers 18 reversely rotate output.Moment of torsion Jing driving gears 10 and idle pulley 16 are passed to driven gear 15 by P3 planet carriers 18；
When the 3rd rotary clutch C7 is combined, bell housing is connected with clutch hub, then moment of torsion is passed through by driven gear 15
Bell housing and clutch hub pass to front output shaft 17, and another side is crossed P4 gear rings 12 and passes to rear output shaft 11, both sides output
Rotating speed it is identical, in front and back output torque ratio be 1:1；When the 3rd rotary clutch C7 is not combined, bell housing and clutch hub
Disconnect, then driven gear 15 passes to front output shaft 17 by moment of torsion by P4 sun gears 13, and another side passes through P4 gear rings 12
Rear output shaft 11 is passed to, both sides output speed is identical, output torque ratio is 3 in front and back:7.
The combination situation of clutch during each gear, brake is realized in 1 the technical program of table
Note：In table+represent clutch closure or brake engagement.
Claims (4)
1. a kind of variator with transfer case, including locking and damping clutch assembly (A), fluid torque-converter (B), rotation clutch
Device assembly (C), planetary transmission (D), PTO (5), built-in cycloid gear pump (6) and turbine output shaft (26), institute
Locking and damping clutch assembly (A) are stated by its locking and the turbine seat (27) of damping clutch (1) and fluid torque-converter (B)
Connection, the turbine seat (27) are connected with turbine output shaft (26), and the turbine output shaft (26) is by rotary clutch assembly
(C) be connected with planetary transmission (D), meanwhile, the pump impeller (4) of the fluid torque-converter (B) respectively with PTO (5) and
Built-in cycloid gear pump (6) connection, it is characterised in that：Planetary transmission (D) end is also associated with transfer box assembly (E)；
The transfer box assembly (E) including driving gear (10), P4 gear rings (12), P4 sun gears (13), P4 planet carriers (14), from
Moving gear (15) and idle pulley (16), driving gear (10) are engaged with idle pulley (16), and idle pulley (16) is engaged with driven gear (15), from
Moving gear (15) while with P4 planet carriers (14) spline connection, while P4 planet carriers (14) and P4 gear rings (12) and P4 sun gears
(13) engage, P4 gear rings (12) are connected with rear output shaft (11) by spline, and P4 sun gears (13) are by spline and front output shaft
(17) connect；Driven gear (15) another side and bell housing spline connection, bell housing is with clutch hub by the 3rd rotation
Clutch (C7) floating connection, clutch hub are connected with front output shaft (17) by spline.
2. a kind of variator with transfer case according to claim 1, it is characterised in that：The rotary clutch assembly
(C) including the first rotary clutch (C1) and the second rotary clutch (C2), using nesting type structure, the first rotary clutch
(C1) it is nested in the second rotary clutch (C2).
3. a kind of variator with transfer case according to claim 1, it is characterised in that：Planetary transmission (D) bag
P1 planet rows, P2 planet rows and P3 planet rows are included, P1 planet rows include P1 gear rings (7), P1 planet carriers (22) and P1 sun gears
(23), P1 gear rings (7) are braked by the first brake (C3)；P2 planet rows include P2 gear rings (8), P2 sun gears (20) and P2 rows
Carrier (21), P2 gear rings (8) are braked by second brake (C4)；P3 planet rows include P3 gear rings (9), P3 planet carriers (18) and
P3 sun gears (19), P3 gear rings (9) are braked by the 3rd brake (C5).
4. a kind of variator with transfer case according to claim 3, it is characterised in that：The P2 sun gears (20) and P3
Sun gear (19) is connected with jackshaft (25), and jackshaft (25) two ends connect the first rotary clutch (C1) and the 4th braking respectively
Device (C6).
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410782454.9A CN104494425B (en) | 2014-12-16 | 2014-12-16 | A kind of variator with transfer case |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410782454.9A CN104494425B (en) | 2014-12-16 | 2014-12-16 | A kind of variator with transfer case |
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| CN104494425A CN104494425A (en) | 2015-04-08 |
| CN104494425B true CN104494425B (en) | 2017-03-29 |
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Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN104534033B (en) * | 2014-12-17 | 2018-02-06 | 贵州凯星液力传动机械有限公司 | A kind of transfer case |
| DE102016211945A1 (en) * | 2016-06-30 | 2018-01-04 | Zf Friedrichshafen Ag | The torque transfer device |
| CN114263732A (en) * | 2021-12-16 | 2022-04-01 | 贵州凯星液力传动机械有限公司 | Method for solving difficulty in engaging transfer case gear caused by belt row of special automobile gearbox |
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| JPS601027A (en) * | 1983-06-20 | 1985-01-07 | Aisin Seiki Co Ltd | Transmission with transfer |
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|---|---|---|---|---|
| DE2747786A1 (en) * | 1976-10-25 | 1978-04-27 | Nissan Motor | TRANSFER BOX |
| US5061229A (en) * | 1989-10-18 | 1991-10-29 | Aisin Aw Kabushiki Kaisha | Four-wheel drive device |
| CN101255906A (en) * | 2007-03-01 | 2008-09-03 | 通用汽车环球科技运作公司 | Powertrain with torque converter and axially compact seven speed dual clutch transmission |
| CN101319715A (en) * | 2007-06-06 | 2008-12-10 | 通用汽车公司 | Seven speed transmission with six torque-transmitting mechanisms and three planetary gear sets |
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| CN104494425A (en) | 2015-04-08 |
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