CN108167415A - Automatic transmission - Google Patents
Automatic transmission Download PDFInfo
- Publication number
- CN108167415A CN108167415A CN201810040669.1A CN201810040669A CN108167415A CN 108167415 A CN108167415 A CN 108167415A CN 201810040669 A CN201810040669 A CN 201810040669A CN 108167415 A CN108167415 A CN 108167415A
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- CN
- China
- Prior art keywords
- gear
- clutch
- automatic transmission
- planetary
- power
- 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.)
- Pending
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
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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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
-
- 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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six forward speeds
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a kind of automatic transmission, including input shaft, with the jackshaft of input axis connection, output shaft, differential mechanism, with the fluid torque-converter of input axis connection, with the input axis connection and be used to implement the simple planetary arrangement of deceleration, for the drawings wiener formula planetary gear mechanism that receives the power that simple planetary arrangement and/or jackshaft transmit and for receiving the central supporting mechanism drawn the power of wiener formula planetary gear mechanism transmission and power is transferred to the output shaft.The automatic transmission of the present invention, compact-sized, power transmission line is short, so as to save space, reduces cost, improves efficiency.
Description
Technical field
The invention belongs to transmission technology field, specifically, the present invention relates to a kind of automatic transmission.
Background technology
In automatic gearbox field, it is desirable that the gear number of automotive transmission is more, transmission efficiency, compact-sized, from
And make automobile that there is low burn oilconsumption, good cornering ability.Automatic gearbox all contains planetary gear set
With the frictional gearshift component of multi-disc, such as clutch and brake, to increase gear number, transmission efficiency is improved.It is however existing
The shortcomings that automatic transmission generally existing drive path is long, overall volume is bigger than normal, the larger and cost that occupies arrangement space is higher.
Invention content
The present invention is directed at least solve one of technical problem in the prior art.For this purpose, the present invention provides one kind certainly
Dynamic speed changer, it is therefore an objective to reduce the space occupied.
To achieve these goals, the technical solution taken of the present invention is：Automatic transmission, including input shaft, with inputting
The jackshaft of axis connection, differential mechanism, the fluid torque-converter with inputting axis connection, further includes and the input axis connection output shaft
And be used to implement deceleration simple planetary arrangement, for receive simple planetary arrangement and/or jackshaft transmit it is dynamic
The drawing wiener formula planetary gear mechanism of power and for receiving the power that wiener formula planetary gear mechanism is drawn to transmit and passing power
It is handed to the central supporting mechanism of the output shaft.
The simple planetary arrangement includes the first gear ring being set on the input shaft, single planet carrier, first
Sun gear and the first planetary gear for being set on single planet carrier and being engaged with the first sun gear and the first gear ring, first too
Sun wheel is in stationary state.
Multiple third planet teeth that wiener formula planetary gear mechanism is drawn to include compound planetary frame, be set to same layer
Take turns, be set to another layer and multiple second planetary gears that one end is meshed with third planet gear, with the second planetary gear
The second sun gear for being meshed of the other end and the second gear ring and the third sun gear that is engaged with third planet gear.
The automatic transmission further includes the first clutch being connect with the single planet carrier and the third sun gear
Device is connect with the compound planetary frame and the second clutch of the intermediate axis connection, with single planet carrier and the drive disk
Third clutch, be arranged on the third clutch outside the first brake, with the compound planetary frame and automatic becoming
The second brake of the housing connection of fast device and the one-way clutch being connect with the housing of compound planetary frame and automatic transmission.
The clutch hub of the third clutch is connect by spline with the drive disk, drive disk by spline with it is described
Second sun gear connects.
It is described to draw the compound planetary frame of wiener formula planetary gear mechanism and the friction plate of the second clutch and the second system
The friction plate of dynamic device and one-way clutch connection, draw the second planetary gear of wiener formula planetary gear mechanism and central supporting machine
The second gear ring engagement in structure.
The central supporting mechanism includes the central support being connected with housing, the connection ring being connect with second gear ring
The intermediate driving gear being connected with connection ring, the intermediate driving gear are set to central branches by a pair of of angular contact ball bearing
On support body.
The automatic transmission further includes what is be set on the output shaft and be meshed with the intermediate driving gear
Driven gear, the helical gear being fixedly installed on output shaft and be set on differential casing and with the helical gear on output shaft
The differential mechanism gear ring being meshed.
The fluid torque-converter has lock-up clutch.
The automatic transmission of the present invention, compact-sized, power transmission line is short, so as to save space, reduces cost,
Reduce speed changer the space occupied.
Description of the drawings
This specification includes the following drawings, and shown content is respectively：
Fig. 1 is the principle schematic of invention automatic transmission；
Power transmission line when Fig. 2 is fourth gear；
Power transmission line when Fig. 3 is five grades；
In figure label for：1st, fluid torque-converter；2nd, input shaft；3rd, the first gear ring；4th, single planet carrier；5th, the first planet
Gear；6th, the first sun gear；7th, drive disk；8th, the second sun gear；9th, third sun gear；10th, compound planetary frame；11st, the second row
Star gear；12nd, the second gear ring；13rd, jackshaft；14th, intermediate driving gear；15th, driven gear；16th, output shaft；17th, differential mechanism
Gear ring；18th, differential casing；19th, long planet gear axis；20th, differential pinion gear；21st, differential side gear；22nd,
Three planetary gears；23rd, central support；24th, connection ring；25th, clutch hub；26th, angular contact ball bearing；B1, the first brake；
B2, second brake；C1, first clutch；C2, second clutch；C3, third clutch；F1, one-way clutch.
Specific embodiment
Below against attached drawing, by the description of the embodiment, making to the specific embodiment of the present invention further details of
Explanation, it is therefore an objective to those skilled in the art be helped to have more complete, accurate and deep reason to design of the invention, technical solution
Solution, and contribute to its implementation.
It should be noted that in embodiment disclosed below, " first ", " second " and " third " does not represent knot
Structure and/or the absolute sequence that performs distinguished relationship, also do not represent priority functionally, and merely for convenience of description.
As shown in Figure 1, the present invention provides a kind of automatic transmission, the jackshaft including input shaft 2, with input axis connection
13rd, 1, six output shaft 16, the fluid torque-converter that is connect with input shaft 2 gearshift component, connect and be used to implement with input shaft 2 and subtract
The simple planetary arrangement of speed, the La Weina for receiving the power of simple planetary arrangement and/or the transmission of jackshaft 13
Formula planetary gear mechanism draws wiener formula planetary gear mechanism (also referred to as coupled planetary gears, Ravigneaux formula planet for receiving
Gear mechanism) power that transmits and power is transferred to central supporting mechanism, main reducing gear, differential mechanism and the shell of output shaft
Body.Simple planetary arrangement, which is arranged in, to be drawn before wiener formula planetary gear mechanism, and simple planetary arrangement is by input shaft 2
Rotating speed carry out speedup after be transmitted to the drawing wiener formula planetary gear mechanism of heel row.Six shift components include the first brake
B1, second brake B2, first clutch C1, second clutch C2, third clutch C3 and one-way clutch F1, the first system
Dynamic device B1 is band brake, and second brake B2 is multi-disc friction type brake, first clutch C1, second clutch C2 and
Third clutch C3 is multidisc clutch, and one-way clutch F1 is column type one-way clutch；First brake B1, second
Brake B2, first clutch C1, second clutch C2, third clutch C3 and one-way clutch F1 structure belong to existing skill
Art, therefore details are not described herein.Six shift components enable the premise that speed changer overall structure is held in the torque for meeting delivery request
Under, reduce speed changer overall volume.Central supporting mechanism is with drawing wiener formula planetary gear mechanism to connect, and by central supporting machine
Structure is arranged in the centre position of the entire power transmission line of speed changer, the output route of power is shortened, so as to save sky
Between, cost is reduced, reduces speed changer entirety the space occupied.
Specifically, as shown in Figure 1, fluid torque-converter 1 have lock-up clutch, input shaft 2 by fluid torque-converter 1 with
Engine is connected, while input shaft 2 is connected with jackshaft 13, and torque and rotating speed from engine output are become by fluid power
Square device 1 is transferred to input shaft 2 and jackshaft 13, and input shaft 2 and jackshaft 13 is made to rotate together, selectable by control strategy
Make first clutch C1, second clutch C2 and third clutch C3 is combined or separation, while selectively makes the first brake
B1, second brake B2 and one-way clutch F1 work, and pass through simple planetary arrangement and with draw wiener formula planetary gear
The central supporting mechanism passing power that mechanism is connected, so that output shaft 16 exports different directions and the torque and rotating speed of size,
Final power is transferred to differential side gear so as to export through the helical gear on output shaft and differential mechanism.
As shown in Figure 1, simple planetary arrangement include being set to the first gear ring 3 on input shaft 2, single planet carrier 4,
First sun gear 6 and the first planet tooth for being set on single planet carrier 4 and being engaged with the first sun gear 6 and the first gear ring 3
Wheel 5, the first sun gear 6 be in stationary state, and the first planetary gear 5 is helical gear and the first planetary gear 5 setting five, and first
Planetary gear 5 is between the first sun gear 6 and the first gear ring 3.The structure of wiener formula planetary gear mechanism is drawn such as this field
As well known to technical staff, wiener formula planetary gear mechanism is drawn mainly to include compound planetary frame 10, be set to same layer
Multiple third planet gears 22, be set to another layer and multiple second planetary gears that one end is meshed with third planet gear
11st, the second sun gear 8 and the second gear ring 12 that are meshed with the other end of the second planetary gear 11 and with third planet gear
The third sun gear 9 of 22 engagements.Second planetary gear 11 and third planet gear 22 are set on compound planetary frame 10, the second row
Star gear 11 is between the second sun gear 8 and the second gear ring 12, one end and the third planet gear 22 of the second planetary gear 11
It is meshed, the other end the second sun gear 8 and the second gear ring 12 of the second planetary gear 11 are meshed.All second planetary gears 11
Be set to same layer refer to all second planetary gears 11 be in in the same plane of its axis perpendicular, all third planets
Gear 22 be set to same layer refer to all third planet gears 22 be in in the same plane of its axis perpendicular, as
Preferably, the second planetary gear 11 sets five altogether and the second planetary gear 11 is helical gear, and third planet gear 22 is set altogether
Five and third planet gear 22 are also helical gear.
As shown in Figure 1, the automatic transmission of the present invention further includes the connect with single planet carrier 4 and third sun gear 9
One clutch C1, the compound planetary frame 10 with drawing wiener formula planetary gear mechanism and intermediate axis connection second clutch C2, with
Third clutch C3 that single planet carrier 4 and drive disk 7 connect, be arranged on third clutch C3 outside the first brake
B1, the second brake B2 being connect with the housing of compound planetary frame 10 and automatic transmission and with compound planetary frame 10 and automatic
The one-way clutch F1 of the housing connection of speed changer.The clutch hub 25 of third clutch C3 is connect by spline with drive disk 7,
Drive disk 7 is connect by spline with the second sun gear 8.Fluid torque-converter 1 is connected by spline with input shaft 2, the first gear ring 3
It is fixedly connected with input shaft 2, single planet carrier 4 connects first clutch C1 and third clutch C3 simultaneously, in third clutch
The outside of the clutch hub 25 of C3 is around the brake band of the first brake B1, and the brake band of the first brake B1 is by the first system
The piston control of dynamic device B1, the piston of the first brake B1 control the brake band of the first brake B1 to fix or unclamp third clutch
The clutch hub of device C3.The clutch hub 25 of third clutch C3 is connect by spline with drive disk 7, and drive disk 7 passes through spline
It is connect with the second sun gear 8.The clutch hub of first clutch C1 is connect by spline with third sun gear 9, compound planetary frame
10 connect with the friction plate of second clutch C2 and the friction plate of second brake B2, the second gear ring 12 by connection ring 24 with
Intermediate driving gear is connected, and the brake hub of second brake B2 is fixedly connected with the housing of automatic transmission.One-way clutch
The periphery of F1 is fixedly connected by spline with the housing of automatic transmission, and inner ring and the compound planetary frame 10 of one-way clutch F1 connect
It connects.
As shown in Figure 1, central supporting mechanism is located at the inside of housing, central supporting mechanism includes the center being connected with housing
Supporter 23, the connection ring 24 being connect with the second gear ring 12 and the intermediate driving gear 14 being connected with connection ring 24, intermediate active
For gear 14 to be rotatably arranged on central support 23, central support 23 is located at the inside of housing and central support 23
It is fixedly connected with the casing, jackshaft 13 passes through central support 23,24 and second gear ring 12 of connection ring and intermediate driving gear 14
It connects and 14 and second gear ring 12 of intermediate driving gear is coaxial arrangement, the setting of connection ring 24 so that intermediate driving gear 14
It can synchronous rotary with the second gear ring 12.As preference, intermediate driving gear 14 is mounted on by a pair of of angular contact ball bearing 26
On central support 23.Connection ring 24 is cirque structure, and connection ring 24 is to be connect by spline with the second gear ring 12, connection ring
24 have external splines, and the second gear ring 2 has the internal spline engaged with the external splines in connection ring 24；Connection ring 24 is to pass through spline
Connect with intermediate driving gear 14, intermediate driving gear 14 have external splines, connection ring 24 have on intermediate driving gear 14
External splines engagement internal spline.
As shown in Figure 1, the present invention automatic transmission also further include be set on output shaft 16 and with intermediate driving gear
14 driven gears 15 being meshed, the helical gear being fixedly installed on output shaft and be set on differential casing and with output
The differential mechanism gear ring 17 that helical gear on axis is meshed.Jackshaft 13 is coaxial arrangement with input shaft 2, and second clutch C2 leads to
Combination and separation are crossed, to control the transmission of the power between compound planetary frame 10 and jackshaft 13 and interruption, second clutch C2
Clutch hub be fixed on jackshaft 13, jackshaft 13 is connect by spline with input shaft 2, and the second gear ring 12 passes through connection ring
24 are connected with intermediate driving gear 14, the second gear ring 12 and 14 synchronous rotary of intermediate driving gear.The axis of output shaft 16 is in
Countershaft 13 is parallel with the axis of input shaft 2, and driven gear 15 is fixed on output shaft, intermediate driving gear 14 with it is driven
Gear 15 is meshed.The helical gear engaged there are one being set on output shaft with the differential mechanism gear ring 17 on differential mechanism, differential mechanism gear ring
17 are bolted on the differential casing 18 of differential mechanism, and differential casing 18 passes through the long planet gear axis that is fixed thereon
It is connected with differential pinion gear 20, differential pinion gear 20 is meshed with differential side gear 21, differential side tooth
Wheel 21 is connected with the transmission shaft on vehicle by spline, so as to finally transmit power on wheel.
Each gear switch of the automatic transmission of the present invention and power transmission line will be described in detail below：
Power transmission line at one grade is：
At one grade, first clutch C1 and one-way clutch F1 work make third sun gear 9 be connected with single planet carrier 4,
Remain stationary as compound planetary frame 10 simultaneously, power is transmitted according to the route of lower section：
2 → the first gear ring 3 of input shaft → single 4 → third of planet carrier sun gear, 9 → the second gear ring 12 → intermediate driving tooth
Take turns 14 → driven gear, 15 → differential mechanism gear ring, 17 → differential side gear 21.
At one grade, after input shaft 2 rotates, the power of input shaft 2 through simple planetary arrangement and draws wiener formula planet
Gear mechanism is transferred to intermediate driving gear 14, and then power is transferred to output shaft, and last power is transferred to differential through differential mechanism
Device axle shaft gear and export.
Power transmission line at two grades is：
At two grades, first clutch C1 and the first brake B1 work make third sun gear 9 be connected with single planet carrier 4,
Remain stationary as the second sun gear 8 simultaneously, power is transmitted according to the route of lower section：
2 → the first gear ring 3 of input shaft → single 4 → third of planet carrier, 9 → compound planetary of sun gear frame, 10 → the second gear ring
12 → intermediate driving gear 14 → driven gear, 15 → differential mechanism gear ring, 17 → differential side gear 21.
At two grades, after input shaft 2 rotates, the power of input shaft 2 through simple planetary arrangement and draws wiener formula planet
Gear mechanism is transferred to intermediate driving gear 14, and then power is transferred to output shaft, and last power is transferred to differential through differential mechanism
Device axle shaft gear and export.
Power transmission line during third gear is：
During third gear, first clutch C1 and third clutch C3 work make third sun gear 9 be connected with single planet carrier 4,
Single planet carrier 4 is made to be connected with the second sun gear 8 simultaneously, power is transmitted according to the route of lower section：
2 → the first gear ring 3 of input shaft → single 4 → the second sun gear 8 of planet carrier and third sun gear 9 → compound planetary frame
10 → the second 12 → intermediate driving gear 14 → driven gear, 15 → differential mechanism gear ring of gear ring, 17 → differential side gears 21.
In third gear, after input shaft 2 rotates, the power of input shaft 2 through simple planetary arrangement and draws wiener formula planet
Gear mechanism is transferred to intermediate driving gear 14, and then power is transferred to output shaft, and last power is transferred to differential through differential mechanism
Device axle shaft gear and export.
Power transmission line during fourth gear is：
During fourth gear, first clutch C1 and second clutch C2 work make single planet carrier 4 be connected with third sun gear 9,
Compound planetary frame 10 is made to be connected with input shaft 2 simultaneously, power is transmitted according to the route of Fig. 2.
In fourth gear, after input shaft 2 rotates, the power of input shaft 2 is divided into two-way, all the way successively through single planet carrier and the
Three sun gears 9 are transferred to the second gear ring 12, and another way is transferred to the second gear ring 12 through compound planetary frame 10, and then power passes successively
Intermediate driving gear 14 and output shaft are handed to, last power is transferred to differential side gear through differential mechanism and exports.
Power transmission line at five grades is：
At five grades, second clutch C2 and third clutch C3 work make single planet carrier 4 be connected with the second sun gear 8,
Compound planetary frame 10 is made to be connected with input shaft 2 simultaneously, power is transmitted according to the route of Fig. 3.
At five grades, after input shaft 2 rotates, the power of input shaft 2 is divided into two-way, all the way successively through single planet carrier and the
Two sun gears 8 are transferred to the second gear ring 12, and another way is transferred to the second gear ring 12 through compound planetary frame 10, and then power passes successively
Intermediate driving gear 14 and output shaft are handed to, last power is transferred to differential side gear through differential mechanism and exports.
Power transmission line at six grades is：
At six grades, second clutch C2 and the first brake B1 work make compound planetary frame 10 be connected with input shaft 2, together
When make the second sun gear 8 fixed, power according to lower section route transmit：
2 → compound planetary of input shaft frame, 10 → the second 12 → centre of gear ring driving gear 14 → driven gear, 15 → differential
17 → differential side gear of device gear ring 21.
At six grades, after input shaft 2 rotates, the power of input shaft 2 is transferred to the second gear ring 12 through compound planetary frame 10, so
Power is transferred to intermediate driving gear 14 and output shaft successively afterwards, last power through differential mechanism be transferred to differential side gear and
Output.
Power transmission line during reverse gear is：
During reverse gear, third clutch C3 and second brake B2 work make single planet carrier 4 be connected with the second sun gear 8,
And making compound planetary frame 10 fixed, power is transmitted according to the route of lower section：
2 → the first gear ring 3 of input shaft → single 4 → the second sun gear of planet carrier, 8 → the second gear ring 12 → intermediate driving tooth
Take turns 14 → driven gear, 15 → differential mechanism gear ring, 17 → differential side gear 21.
In reverse gear, after input shaft 2 rotates, the power of input shaft 2 is transferred to the second sun gear 8 through single planet carrier 4, so
Power is transferred to the second gear ring 12, intermediate driving gear 14 and output shaft, last power and is transferred to differential through differential mechanism successively afterwards
Device axle shaft gear and export.
The present invention is exemplarily described above in association with attached drawing.Obviously, present invention specific implementation is not by above-mentioned side
The limitation of formula.As long as employ the improvement of the various unsubstantialities of inventive concept and technical scheme of the present invention progress；Or not
It is improved, the above-mentioned design of the present invention and technical solution are directly applied into other occasions, in protection scope of the present invention
Within.
Claims (9)
1. automatic transmission, including input shaft, with the jackshaft of input axis connection, output shaft, differential mechanism and with inputting axis connection
Fluid torque-converter, it is characterised in that：Further include with the input axis connection and be used to implement the single planetary gear machine of deceleration
Structure, drawing wiener formula planetary gear mechanism and use for receiving the power of simple planetary arrangement and/or jackshaft transmission
The power of wiener formula planetary gear mechanism transmission is drawn in reception and power is transferred to the central supporting mechanism of the output shaft.
2. automatic transmission according to claim 1, it is characterised in that：The simple planetary arrangement includes being set to
The first gear ring (3), single planet carrier (4), the first sun gear (6) on the input shaft and it is set to single planet carrier (4)
The first planetary gear (5) that is upper and being engaged with the first sun gear (6) and the first gear ring (3), the first sun gear (6) is in fixing shape
State.
3. automatic transmission according to claim 1, it is characterised in that：The drawing wiener formula planetary gear mechanism includes multiple
Formula planet carrier (10), the multiple third planet gears (22) for being set to same layer, be set to another layer and one end and the third line
Multiple second planetary gears (11) that star gear is meshed, second sun being meshed with the other end of the second planetary gear (11)
Wheel (8) and the second gear ring (12) and the third sun gear (9) engaged with third planet gear (22).
4. automatic transmission according to claim 3, it is characterised in that：It further includes and the single planet carrier (4) and institute
State third sun gear (9) connection first clutch (C1), the with the compound planetary frame (10) and the intermediate axis connection
Two clutches (C2), the third clutch (C3) being connect with single planet carrier (4) and the drive disk (7) are arranged on described
First brake (B1) in the outside of three clutches (C3) is connect with the housing of the compound planetary frame (10) and automatic transmission
Second brake (B2) and the one-way clutch (F1) that is connect with the housing of compound planetary frame (10) and automatic transmission.
5. automatic transmission according to claim 4, it is characterised in that：The clutch hub of the third clutch (C3)
(25) it is connect by spline with the drive disk (7), drive disk (7) is connect by spline with second sun gear (8).
6. automatic transmission according to claim 4 or 5, it is characterised in that：The drawing wiener formula planetary gear mechanism
The friction plate of compound planetary frame (10) and the second clutch (C2) and the friction plate of second brake (B2) and unidirectionally from
Clutch (F1) connects, the second planetary gear (11) and the second gear ring in central supporting mechanism for drawing wiener formula planetary gear mechanism
(12) it engages.
7. according to any automatic transmission of claim 4 to 6, it is characterised in that：The central supporting mechanism include with
Central support (23) that housing is connected, the connection ring (24) being connect with second gear ring (12) and it is connected with connection ring (24)
Intermediate driving gear (14), the intermediate driving gear is set to central support by a pair of of angular contact ball bearing (26)
On.
8. automatic transmission according to claim 7, it is characterised in that：Further include be set on the output shaft (16) and
The driven gear (15) that is meshed with the intermediate driving gear (14), the helical gear being fixedly installed on output shaft (16) and
The differential mechanism gear ring (17) for being set on differential casing and being meshed with the helical gear on output shaft.
9. automatic transmission according to any one of claims 1 to 8, it is characterised in that：The fluid torque-converter has locking
Clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810040669.1A CN108167415A (en) | 2018-01-16 | 2018-01-16 | Automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810040669.1A CN108167415A (en) | 2018-01-16 | 2018-01-16 | Automatic transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108167415A true CN108167415A (en) | 2018-06-15 |
Family
ID=62514940
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810040669.1A Pending CN108167415A (en) | 2018-01-16 | 2018-01-16 | Automatic transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108167415A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109780149A (en) * | 2019-03-13 | 2019-05-21 | 吉林大学 | A kind of speed change gear based on small teeth number difference planet gear |
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| CN110529569A (en) * | 2019-09-26 | 2019-12-03 | 吉孚汽车技术(浙江)有限公司 | Hybrid power gearbox |
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