CN106917850B - Eight speed automatic transmissions - Google Patents
Eight speed automatic transmissions Download PDFInfo
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- CN106917850B CN106917850B CN201710285778.5A CN201710285778A CN106917850B CN 106917850 B CN106917850 B CN 106917850B CN 201710285778 A CN201710285778 A CN 201710285778A CN 106917850 B CN106917850 B CN 106917850B
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- Prior art keywords
- clutch
- gear
- planet
- planet carrier
- transmission
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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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
- F16H2200/2097—Transmissions using gears with orbital motion comprising an orbital gear set member permanently connected to the housing, e.g. a sun wheel permanently connected to the housing
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention provides a kind of eight speed automatic transmissions, including input link, output link, case of transmission, first planetary gear set, the second planetary gear set, third planet gear set, fourth planet gear set, first clutch, second clutch, third clutch, the 4th clutch and the 5th clutch.Eight speed automatic transmissions of the invention, include four planetary gear sets and five clutches, it is selectively engaged or separates by five clutches, to generate eight forward gear transmissions when back gear ratio between input link and output link, that is, realize eight forward gears and one reverses gear.Eight speed automatic transmission reduces the processing and manufacture difficulty of case of transmission, is conducive to the lightweight of case of transmission, to keep entire speed changer more compact without using brake so as to avoid the processing and manufacture of internal tooth on case of transmission.
Description
Technical field
The invention belongs to technical field of automobile transmission, more particularly to a kind of eight speed automatic transmissions.
Background technique
In the prior art, it is generally included for the automatic transmission of automobile (Automatic Transmission, AT) defeated
Enter component, output link, planetary gear set, clutch/brake and connection input link, output link, planetary gear set
With the driving member of clutch/brake.Input link usually be integrated with the initiating element of lockup clutch, torsional vibration damper
It is connected, such as fluid torque-converter.By theory of mechanics it is found that it is that the quantity of mechanism power source is equal to that mechanism, which has the condition for determining movement,
Mechanism revolving speed number of degrees of freedom,.Since AT is to realize different gears by the combined engagement of different clutch/brakes, that is, pass through system
Dynamic device/clutch confining part freedom degree reduces degree of freedom in system purpose to reach, final to guarantee that mechanism has determining fortune
It is dynamic.The single power source planetary transmission for being N for a degree of freedom in system number has and determines that the condition of movement is to pass through braking
The operating elements such as device/clutch limit (N-1) a revolving speed freedom degree.
The volume of automatic transmission, weight, efficiency and bearing capacity are directly related with planetary gear mechanism.Planetary gear
Group number, clutch/brake number and driving member connection determine the complexity of transmission scheme structure arrangement to a certain extent
Degree.The operating element quantity that number of degrees of freedom, increases transformation of shifting gears between adjacent gear increases, and all will lead to HCU/TCU control
Difficulty increases.The power transmission line of each gear depends on transmission scheme, should be avoided and internal power circulation occurs, influence each gear
The case where position transmission efficiency, occurs.
With automobile emission regulation, increasingly the requirement of harshness and the requirement of fuel economy, transmission gear demand increase
It is more.For planetary automatic transmission, increase gear by two kinds of approach: first is that increasing planet row (planetary gear set) quantity；Two
It is to increase freedom degree quantity (easily leading to operating element to increase).For this purpose, seeking a kind of planet row and best group of operating element quantity
It closes, the compact-sized and efficient planetary automatic speed-changing mechanism of transmission is as major vehicle enterprise or the pass of research and development institution's product development
Key.
The fast hydraulic automatic speed variator of planetary gear type 8 that passenger car uses in the market at present is mainly the 8HP eight of ZF fast certainly
The TR-80SD eight-speed automatic transmission and the A8L/TR1 in modern times that dynamic speed changer, general 8L90 eight-speed automatic transmission, love are believed
Eight-speed automatic transmission.
TR-80SD and A8L/TR1 scheme is all made of Ravigneaux structure, and TR-80SD scheme and A8L/TR1 are 3DOF
System, using 3 clutch, two brake.And 8HP and 8L90 is 4DOF system, also uses 3 clutch, two brake.
As it can be seen that existing 8 fast hydraulic automatic speed variators are to realize using 3 clutches with two brakes, can all there is two
A brake.Brake is connected on case of transmission by the steel disc tooth that rubs, and the presence of brake undoubtedly increases
The processing and manufacture difficulty of case of transmission.And since case of transmission material is usually aluminium alloy, more brakes are undoubtedly
It can be difficult to take into account the intensity and light-weight design of case of transmission.The TR-80SD scheme and modern A8L/TR1 scheme for liking letter are adopted
With Ravigneaux structure, there is dual planetary gear structure, components are more and structure is complicated, are more unfavorable for lightweight.And due to braking
The presence of device, the idle running planetary gear set that actual transfer power is not involved under specific gear can generate band row's towing loss, drop
Low system effectiveness.
Summary of the invention
The technical problems to be solved by the present invention are: it is directed to existing 8 speed automatic transmission, due to the presence of brake,
The problem of increasing the processing and manufacture difficulty of case of transmission provides a kind of eight speed automatic transmissions.
In order to solve the above technical problems, the embodiment of the present invention provides a kind of eight speed automatic transmissions, comprising:
Input link；
Output link；
Case of transmission；
First planetary gear set, the second planetary gear set, third planet gear set and fourth planet gear set；Described first
Planetary gear set includes the first sun gear, the first planetary gear, first planet carrier and the first gear ring；First sun gear and first
Planetary gear external toothing transmission, first planetary gear and the first gear ring Inside gear drive, first planetary gear are rotatably supported on
In the first planet carrier；Second planetary gear set includes the second sun gear, the second planetary gear, the second planet carrier and second
Gear ring；Second sun gear and the second planetary gear external toothing are driven, second planetary gear and the second gear ring Inside gear drive,
Second planetary gear is rotatably supported on second planet carrier；The third planet gear set includes third sun gear,
Three planetary gears, third planet carrier and third gear ring；The third sun gear and the external toothing of the third line star-wheel are driven, described the third line
Star-wheel and third gear ring Inside gear drive, the third line star-wheel are rotatably supported in the third planet carrier；The fourth line
Star gear set includes the 4th sun gear, fourth line star-wheel, fourth line carrier and the 4th gear ring；4th sun gear and fourth line
Star-wheel external toothing transmission, the fourth line star-wheel and the 4th gear ring Inside gear drive, the fourth line star-wheel are rotatably supported on institute
It states in fourth line carrier；Second planet carrier is fixedly linked with input link, and first sun gear and the second sun gear are solid
Fixed to be connected, second gear ring is fixedly linked with third sun gear, and the third gear ring is fixedly linked with the 4th sun gear, described
Fourth line carrier is fixedly linked with output link, and first gear ring is fixedly linked with case of transmission；
First clutch, second clutch, third clutch, the 4th clutch and the 5th clutch；
The first clutch, second clutch, third clutch, the 4th clutch and the 5th clutch selectively connect
It closes or separates, to generate eight forward gears transmissions when back gear ratio between the input link and output link.
Optionally, when the third clutch engages, the third planet gear set is integrally turned round.
Optionally, the first planet carrier is connect with the 4th gear ring by the first clutch, first sun gear
It is connect with first planet carrier by the second clutch, the third planet carrier and third sun gear pass through the third clutch
Device connection, second planet carrier are connect with the 4th sun gear by the 4th clutch, the third planet carrier and the 4th
Gear ring is connected by the 5th clutch.
Optionally, the first planet carrier is connect with the 4th gear ring by the first clutch, first sun gear
It is connect with first planet carrier by the second clutch, the third planet carrier and third gear ring pass through the third clutch
Connection, second planet carrier are connect with the 4th sun gear by the 4th clutch, the third planet carrier and the 4th tooth
Circle is connected by the 5th clutch.
Optionally, the first planet carrier is connect with the 4th gear ring by the first clutch, first sun gear
It is connect with first planet carrier by the second clutch, the third sun gear and third gear ring pass through the third clutch
Connection, second planet carrier are connect with the 4th sun gear by the 4th clutch, the third planet carrier and the 4th tooth
Circle is connected by the 5th clutch.
Optionally, the first planetary gear set, the second planetary gear set, third planet gear set and the second planetary gear
Group coaxial arrangement.
Optionally, by engaging the first clutch, second clutch and the 4th clutch, the third clutch is separated
Device and the 5th clutch, to generate 1 gear transmission ratio between the input link and output link；
By engaging the first clutch, second clutch and third clutch, the 4th clutch and the are separated
Five clutches, to generate 2 gear transmission ratios between the input link and output link；
By engaging the first clutch, third clutch and the 4th clutch, the second clutch and the are separated
Five clutches, to generate 3 gear transmission ratios between the input link and output link；
By engaging the first clutch, third clutch and the 5th clutch, the second clutch and the are separated
Four clutches, to generate 4 gear transmission ratios between the input link and output link；
By engaging the first clutch, the 4th clutch and the 5th clutch, the second clutch and the are separated
Three clutches, to generate 5 gear transmission ratios between the input link and output link；
By engaging the third clutch, the 4th clutch and the 5th clutch, the first clutch and the are separated
Two clutches, to generate 6 gear transmission ratios between the input link and output link；
By engaging the second clutch, the 4th clutch and the 5th clutch, the first clutch and the are separated
Three clutches, to generate 7 gear transmission ratios between the input link and output link；
By engaging the second clutch, third clutch and the 5th clutch, the first clutch and the are separated
Four clutches, to generate 8 gear transmission ratios between the input link and output link；
By engaging the first clutch, second clutch and the 5th clutch, the third clutch and the are separated
Four clutches, to generate back gear ratio between the input link and output link.
Eight speed automatic transmissions of the embodiment of the present invention include four planetary gear sets and five clutches, pass through five
Clutch is selectively engaged or separates, to generate eight forward gear transmissions when one between input link and output link
Back gear ratio, that is, realize eight forward gears and one reverses gear.Eight speed automatic transmission does not use brake, to keep away
The processing and manufacture for having exempted from internal tooth on case of transmission reduce the processing and manufacture difficulty of case of transmission, are conducive to speed change
The lightweight of device shell, to keep entire speed changer more compact.Also, the first gear ring is directly connected to case of transmission, is kept away
Exempt from direct impact of the brake to cabinet in existing 8AT scheme shift process, so as to improve the loading conditions of case of transmission.
Increase clutch quantity in addition, reaching by using clutch substitution brake, reduce brake quantity (without system
Dynamic device) purpose.The quantity of more clutches is conducive to the nested designs of clutch for more brakes, from
And make entire speed changer more compact.Also, more clutch quantity are conducive to for more brakes
The connection between each planetary gear set is cut off under specific gear, so that the planetary gear set of redundancy is not involved in rotation, is reduced towing and is turned round
Square reduces band row's fuel oil loss, improves system effectiveness.
Detailed description of the invention
Fig. 1 is the structure diagram for eight speed automatic transmissions that first embodiment of the invention provides；
Fig. 2 is the eight speed automatic transmissions 1 gear power transmitting schematic diagram that first embodiment of the invention provides；
Fig. 3 is the eight speed automatic transmissions 2 gear power transmitting schematic diagram that first embodiment of the invention provides；
Fig. 4 is the eight speed automatic transmissions 3 gear power transmitting schematic diagram that first embodiment of the invention provides；
Fig. 5 is the eight speed automatic transmissions 4 gear power transmitting schematic diagram that first embodiment of the invention provides；
Fig. 6 is the eight speed automatic transmissions 5 gear power transmitting schematic diagram that first embodiment of the invention provides；
Fig. 7 is the eight speed automatic transmissions 6 gear power transmitting schematic diagram that first embodiment of the invention provides；
Fig. 8 is the eight speed automatic transmissions 7 gear power transmitting schematic diagram that first embodiment of the invention provides；
Fig. 9 is the eight speed automatic transmissions 8 gear power transmitting schematic diagram that first embodiment of the invention provides；
Figure 10 be first embodiment of the invention provide eight speed automatic transmissions reverse gear power transmitting schematic diagram；
Figure 11 is the structure diagram for eight speed automatic transmissions that second embodiment of the invention provides；
Figure 12 is the structure diagram for eight speed automatic transmissions that third embodiment of the invention provides.
Appended drawing reference in specification is as follows:
1, the first sun gear；2, the first planetary gear；3, first planet carrier；4, the first gear ring；5, the second sun gear；6, second
Planetary gear；7, the second planet carrier；8, the second gear ring；9, third sun gear；10, the third line star-wheel；11, third planet carrier；12,
Three gear rings；13, the 4th sun gear；14, fourth line star-wheel；15, fourth line carrier；16, the 4th gear ring；17, first clutch；
18, second clutch；19, third clutch；20, the 4th clutch；21, the 5th clutch；22, case of transmission；23, it inputs
Component；24, output link.
Specific embodiment
In order to which the technical problems, technical solutions and beneficial effects solved by the present invention is more clearly understood, engage below
Accompanying drawings and embodiments, the present invention is further described in detail.It should be appreciated that specific embodiment described herein is only
To explain the present invention, it is not intended to limit the present invention.
As shown in Figure 1, eight speed automatic transmissions that first embodiment of the invention provides, including input link 23, output structure
Part 24, case of transmission 22, first planetary gear set, the second planetary gear set, third planet gear set, fourth planet gear
Group, first clutch 17, second clutch 18, third clutch 19, the 4th clutch 20 and the 5th clutch 21.
In the present embodiment, as shown in Figure 1, each planetary gear set is single star row of interior external toothing.Specifically:
First planetary gear set includes the first sun gear 1, the first planetary gear 2, first planet carrier 3 and the first gear ring 4.It is described
First sun gear 1 and 2 external toothing of the first planetary gear are driven, and 4 Inside gear drive of first planetary gear 2 and the first gear ring is described
First planetary gear 2 is rotatably supported in the first planet carrier 3 by rolling or sliding bearing.
Second planetary gear set includes the second sun gear 5, the second planetary gear 6, the second planet carrier 7 and the second gear ring 8.It is described
Second sun gear 5 and 6 external toothing of the second planetary gear are driven, and 8 Inside gear drive of second planetary gear 6 and the second gear ring is described
Second planetary gear 6 is rotatably supported on second planet carrier 7 by rolling or sliding bearing.
Third planet gear set includes third sun gear 9, the third line star-wheel 10, third planet carrier 11 and third gear ring 12.
The third sun gear 9 is driven with 10 external toothing of the third line star-wheel, and the third line star-wheel 10 is passed with 12 internal messing of third gear ring
Dynamic, the third line star-wheel 10 is rotatably supported in the third planet carrier 11 by rolling or sliding bearing.
Fourth planet gear set includes the 4th sun gear 13, fourth line star-wheel 14, fourth line carrier 15 and the 4th gear ring 16.
4th sun gear 13 is driven with 14 external toothing of fourth line star-wheel, and the fourth line star-wheel 14 and 16 internal messing of the 4th gear ring pass
Dynamic, the fourth line star-wheel 14 is rotatably supported in the fourth line carrier 15 by rolling or sliding bearing.
As shown in Figure 1, second planet carrier 7 is fixedly linked with input link 23, first sun gear 1 and second is too
Sun wheel 5 is fixedly linked, and second gear ring 8 is fixedly linked with third sun gear 9, the third gear ring 12 and the 4th sun gear 13
It is fixedly linked, the fourth line carrier 15 is fixedly linked with output link 24, and first gear ring 4 and case of transmission 22 are fixed
It is connected.Being fixedly linked herein, can be spline connection, welding or integrally formed.
In this implementation, as shown in Figure 1, the first planet carrier 3 and the 4th gear ring 16 are connected by the first clutch 17
It connects, first sun gear 1 and first planet carrier 3 are connect by the second clutch 18, the third planet carrier 11 and the
Three sun gears 9 are connected by the third clutch 19, second planet carrier 7 and the 4th sun gear 13 by the described 4th from
Clutch 20 connects, and the third planet carrier 11 is connect with the 4th gear ring 16 by the 5th clutch 21.
In the present embodiment, the first clutch 17, second clutch 18, third clutch 19, the 4th clutch 20 and
5th clutch 21 is selectively engaged or separates, to generate eight advances between the input link 23 and output link 24
Gear is driven a when back gear ratio.
In the present embodiment, the first clutch 17, second clutch 18, third clutch 19, the 4th clutch 20 and
The manipulation logic (shift logic) of 5th clutch 21 is referring to following table 1:
Table 1
In table 1, mark ● indicate that the clutch engages, blank space indicates the clutch separation.K1, k2, k3 and k4 are respectively
First planetary gear set, the second planetary gear set, third planet gear set and fourth planet gear set planet row characteristic parameter,
The planet row characteristic parameter is equal to the ratio between gear ring and the number of teeth of sun gear.That is k1 is the number of teeth of the first gear ring 4 and the first sun gear 1
The ratio between, k2 is the ratio between the number of teeth of the second gear ring 8 and the second sun gear 5, k3 be third gear ring 12 and third sun gear 9 the number of teeth it
Than k4 is the ratio between the number of teeth of the 4th gear ring 16 and the 4th sun gear 13.
Referring to Fig. 1-10, under the manipulation logic of table 1, the power transmission line of eight speed automatic transmission is specific as follows
(lines overstriking is handled on transfer route).
(1) 1 gear power transmission line
As shown in Fig. 2, only engaging first clutch 17, second clutch 18 and the 4th clutch 20,1 gear, transmission are realized
Than for (1+k4).First planetary gear set integrally bears reaction force.Because the first gear ring 4 and the constant fixation of case of transmission 22 connect
It connects, therefore the first planetary gear set integral stop when first clutch 17 engages.At this point, being realized when second clutch 18 engages
Braking to the 4th gear ring 16.1 gear power transmission line: 23 → the second the 7 → the four clutch 20 → the of planet carrier of input link
Four 15 → output links of sun gear 13 → fourth line star-wheel 14 → fourth line carrier 24.
(2) 2 gear power transmission lines
As shown in figure 3, only engaging first clutch 17, second clutch 18 and third clutch 19,2 gears, transmission are realized
Than for (k2* (1+k4)/(1+k2)).At this point, the engagement of first clutch 17, second clutch 18 is so that 5 and of the second sun gear
4th gear ring 16 realizes braking, and the engagement of third clutch 19 is so that third planet gear set integrally participates in passing as a revolution
It is dynamic.2 gear power transmission lines: 23 → the second planet carrier of input link, 7 → the second planetary gear, 6 → the second gear ring, 8 (the second sun gear
5 brake so that first planetary gear set realizes single-degree-of-freedom output) → third planet gear set revolution entirety → the 4th sun gear
(the 4th gear ring 16 is braked so that fourth planet gear set realizes that single-degree-of-freedom is defeated for 13 → fourth line, 14 → fourth line of star-wheel carrier 15
Out) → output link 24.
(3) 3 gear power transmission lines
As shown in figure 4, only engaging first clutch 17, third clutch 19 and the 4th clutch 20,3 gears, transmission are realized
Than for ((1+k1+k4+k4*k1)/(1+k1+k4)).At this point, the engagement of third clutch 19 and the 4th clutch 20 is so that second
Planetary gear set and third planet gear set integrally participate in being driven as a revolution.3 gear power transmitting include two lines, road
Line one: 23 → the second planet carrier of input link, 7 → the second planetary gear set and third planet gear set revolution entirety → 4th are too
Sun wheel 13 → fourth line star-wheel, 14 → fourth line carrier, 15 → output link 24.
(4) 4 gear power transmission lines
As shown in figure 5, only engaging first clutch 17, third clutch 19 and the 5th clutch 21,4 gears, transmission are realized
Than for ((1+k1+k2)/(1+k2)).At this point, due to the engagement of third clutch 19 and the 5th clutch 21, so that third planet
Gear set and fourth planet gear set integrally participate in being driven as a revolution.4 gear power transmitting include two lines, route
One: 23 → the second planetary gear of input link, 6 → the second 8 → third planet of gear ring gear set and the revolution of fourth planet gear set are whole
15 → output link of → fourth line carrier 24；Route two: 23 → the second planet carrier of input link, 7 → the second planetary gear 6 → the second
5 → the first sun gear of sun gear, 1 → the first planetary gear 2 → first planet carrier, 3 → first clutch, 17 → third planet gear set
15 → output link of entirety → fourth line carrier 24 is turned round with fourth planet gear set.
(5) 5 gear power transmission lines
As shown in fig. 6, first clutch 17, the 4th clutch 20 and the 5th clutch 21 are only engaged, at this point, the first planet
Gear set, the second planetary gear set, third planet gear set and fourth planet gear set both participate in power transmitting, realize 5 with this
Gear, at this point, transmission ratio is (1+k4+k1+k4*k1+k2*k4+k2*k3*k4)/(1+k1+k2*k3*k4+k4+k2*k4).5 gears are altogether
There are 4 power transmission lines.Route one: the 20 → the 4th sun gear 13 of 23 → the second the 7 → the 4th clutch of planet carrier of input link
15 → output link of → fourth line star-wheel 14 → fourth line carrier 24；Route 2: 23 → the second planet carrier the 7 → the 4th of input link
The 21 → the 4th gear ring 16 of the 11 → the 5th clutch of clutch 20 → third gear ring 12 → the third line star-wheel, 10 → third planet carrier →
15 → output link of fourth line star-wheel 14 → fourth line carrier 24；Route 3: 23 → the second planet carrier of input link, 7 → the second row
The 11 → the 5th clutch the 21 → the 4th of 6 → the second 10 → third planet carrier of gear ring 8 → third sun gear 9 → the third line star-wheel of star-wheel
15 → output link of gear ring 16 → fourth line star-wheel 14 → fourth line carrier 24；Route four: 23 → the second planet carrier 7 of input link
6 → the second sun gear of → the second planetary gear, 5 → the first sun gear, 1 → the first planetary gear 2 → first planet carrier, 3 → first clutch
17 → the 4th 15 → output link of gear ring 16 → fourth line star-wheel 14 → fourth line carrier 24.Reaction force transfer route: first
4 → case of transmission of gear ring 22.
(6) 6 gear power transmission lines
As shown in fig. 7, only engaging third clutch 19, the 4th clutch 20 and the 5th clutch 21,6 gears, transmission are realized
Than being 1.At this point, the engagement of third clutch 19, the 4th clutch 20 and the 5th clutch 21 is so that the second planetary gear set,
Three planetary gear sets and fourth planet gear set become single-mode system, so that the second planetary gear set, third planet
Gear set and fourth planet gear set integrally participate in being driven as a revolution, to realize direct gear.Power transmission line: defeated
It is whole to enter 23 → the second planet carrier of component, 7 → the second planetary gear set, third planet gear set and the revolution of fourth planet gear set
15 → output link of → fourth line carrier 24.
(7) 7 gear power transmission lines
As shown in figure 8, only engaging second clutch 18, the 4th clutch 20 and the 5th clutch 21,7 gears, transmission are realized
Than for k2* (1+k3)/(k2*k3+1+k2).The engagement of second clutch 18 is so that the second sun gear 5 realizes system under the gear
It is dynamic, 3 power transmission lines are shared under the gear.Route one: the 7 → the 4th clutch 20 of 23 → the second planet carrier of input link
→ the four 15 → output link of sun gear 13 → fourth line star-wheel 14 → fourth line carrier 24；Route two: input link 23 → the
The 11 → the 5th clutch 21 of the 7 → the 4th 10 → third planet carrier of clutch 20 → third gear ring 12 → the third line star-wheel of two planet carriers
→ the four 15 → output link of gear ring 16 → fourth line star-wheel 14 → fourth line carrier 24；Route three: input link 23 → the second
7 → the second planetary gear of planet carrier, 6 → the second 10 → third planet carrier of gear ring 8 → third sun gear 9 → the third line star-wheel 11 → the
The 21 → the 4th 15 → output link of gear ring 16 → fourth line star-wheel 14 → fourth line carrier 24 of five clutches.
(8) 8 gear power transmission lines
As shown in figure 9, only engaging second clutch 18, third clutch 19 and the 5th clutch 21,8 gears, transmission are realized
Than for k2/ (1+k2).The engagement of second clutch 18 is so that the second sun gear 5 realizes braking under the gear；Third clutch 19
Engagement with the 5th clutch 21 so that third planet gear set and fourth planet gear set are configured to single-mode system, thus
So that third planet gear set and fourth planet gear set integrally participate in transmission as a revolution.Power transmission line: input
23 → the second planet carrier of component, 7 → the second planetary gear, 6 → the second 8 → third planet of gear ring gear set and fourth planet gear set return
Turn 15 → output link of entirety → fourth line carrier 24.
(9) reverse gear power transmission line
As shown in Figure 10, first clutch 17, second clutch 18 and third clutch 19 are only engaged, realization is reversed gear, and is passed
Dynamic ratio is-k2* (k3*k4-1)/(1+k2).Under the gear, first clutch 17, second clutch 18 and third clutch 19
Engagement so that the second sun gear 5, third planet carrier 11 and the 4th gear ring 16 realize braking.Power transmission line are as follows: input structure
23 → the second planet carrier of part, 7 → the second planetary gear, 6 → the second gear ring 8 → third sun gear 9 → the third line star-wheel 10 → third tooth
The 12 → the 4th 15 → output link of sun gear 13 → fourth line star-wheel 14 → fourth line carrier 24 of circle (the 4th gear ring 16 brake so that
Fourth planet gear set realizes single-degree-of-freedom output).
Clutch effect is by engaging or separating being fixedly connected and separating between realizing two components, and common type has multi-disc
Rotating vane type clutch and jaw clutch (Dog Clutch).That is, the first clutch 17, second clutch 18, third
Clutch 19, the 4th clutch 20 and the 5th clutch 21 are multi-plate wet clutch or jaw clutch.
Brake effect is to realize being connected or separating for component and case of transmission by engaging or separating, to component system
Dynamic or separation.In the present embodiment, brake is free of.
In addition, being eight speed automatic transmissions of second embodiment of the invention referring to Figure 11.Exist with the first implementation difference
In the third planet carrier 11 is connect with third gear ring 12 by the third clutch 19, i.e., third clutch 19 is connected to
(in first embodiment, third clutch 19 is connected to the third planet between the third planet carrier 11 and third gear ring 12
Between frame 11 and third sun gear 9).
The shift control logic of second embodiment is identical with the first embodiment, i.e. the above-mentioned position change of third clutch 19
Shift control logic is not influenced.
In addition, being eight speed automatic transmissions of third embodiment of the invention referring to Figure 12.Exist with the first implementation difference
In the third sun gear 9 is connect with third gear ring 12 by the third clutch 19, i.e., third clutch 19 is connected to institute
State between third sun gear 9 and third gear ring 12 that (in first embodiment, third clutch 19 is connected to the third planet carrier 11
Between third sun gear 9).
The shift control logic of 3rd embodiment is identical with the first embodiment, i.e. the above-mentioned position change of third clutch 19
Shift control logic is not influenced.
In above three embodiments, since third clutch 19 is connected to three component (thirds of third planet gear set
Sun gear 9, third planet carrier 11 and third gear ring 12) between two of them, thus, in three embodiments, the third from
When clutch 19 engages, the third planet gear set is whole revolution.
In addition, in above-described embodiment, the first planetary gear set, the second planetary gear set, third planet gear set and
The coaxial arrangement of second planetary gear set.
However, in other embodiments, it is also possible that third planet gear set and fourth planet gear set are radially superposed
Setting, and the overall structure and first planetary gear set and the second planet of third planet gear set and fourth planet gear set composition
Gear set coaxial arrangement.With this, the axial dimension for shortening eight shift transmission is small, reduces the volume of eight shift transmission,
The horizontal of eight shift transmission can be achieved.
Eight speed automatic transmissions of the embodiment of the present invention include four planetary gear sets and five clutches, pass through five
Clutch is selectively engaged or separates, to generate eight forward gear transmissions when one between input link and output link
Back gear ratio, that is, realize eight forward gears and one reverses gear.Eight speed automatic transmission does not use brake, to keep away
The processing and manufacture for having exempted from internal tooth on case of transmission reduce the processing and manufacture difficulty of case of transmission, are conducive to speed change
The lightweight of device shell, to keep entire speed changer more compact.Also, the first gear ring is directly connected to case of transmission, is kept away
Exempt from direct impact of the brake to cabinet in existing 8AT scheme shift process, so as to improve the loading conditions of case of transmission.
Increase clutch quantity in addition, reaching by using clutch substitution brake, reduce brake quantity (without system
Dynamic device) purpose.The quantity of more clutches is conducive to the nested designs of clutch for more brakes, from
And make entire speed changer more compact.Also, more clutch quantity are conducive to for more brakes
The connection between each planetary gear set is cut off under specific gear, so that the planetary gear set of redundancy is not involved in rotation, is reduced towing and is turned round
Square reduces band row's fuel oil loss, improves system effectiveness.
The foregoing is merely illustrative of the preferred embodiments of the present invention, is not intended to limit the invention, all in essence of the invention
Made any modifications, equivalent replacements, and improvements etc., should all be included in the protection scope of the present invention within mind and principle.
Claims (7)
1. a kind of eight speed automatic transmissions, comprising:
Input link；
Output link；
Case of transmission；
First planetary gear set, the second planetary gear set, third planet gear set and fourth planet gear set；First planet
Gear set includes the first sun gear, the first planetary gear, first planet carrier and the first gear ring；First sun gear and the first planet
External toothing transmission, first planetary gear and the first gear ring Inside gear drive are taken turns, first planetary gear is rotatably supported on described
In first planet carrier；Second planetary gear set includes the second sun gear, the second planetary gear, the second planet carrier and the second tooth
Circle；Second sun gear and the second planetary gear external toothing are driven, second planetary gear and the second gear ring Inside gear drive, institute
The second planetary gear is stated to be rotatably supported on second planet carrier；The third planet gear set includes third sun gear, third
Planetary gear, third planet carrier and third gear ring；The third sun gear and the external toothing of the third line star-wheel are driven, the third planet
Wheel and third gear ring Inside gear drive, the third line star-wheel are rotatably supported in the third planet carrier；The fourth planet
Gear set includes the 4th sun gear, fourth line star-wheel, fourth line carrier and the 4th gear ring；4th sun gear and fourth planet
External toothing transmission, the fourth line star-wheel and the 4th gear ring Inside gear drive are taken turns, the fourth line star-wheel is rotatably supported on described
In fourth line carrier；
It is characterized in that, second planet carrier is fixedly linked with input link, first sun gear and the second sun gear are solid
Fixed to be connected, second gear ring is fixedly linked with third sun gear, and the third gear ring is fixedly linked with the 4th sun gear, described
Fourth line carrier is fixedly linked with output link, and first gear ring is fixedly linked with case of transmission；
Eight speed automatic transmission further includes first clutch, second clutch, third clutch, the 4th clutch and the 5th
Clutch；
The first clutch, second clutch, third clutch, the 4th clutch and the 5th clutch be selectively engaged or
Separation, to generate eight forward gear transmissions when back gear ratio between the input link and output link.
2. eight speed automatic transmission according to claim 1, which is characterized in that described when the third clutch engages
Third planet gear set integrally turns round.
3. eight speed automatic transmission according to claim 1, which is characterized in that the first planet carrier and the 4th gear ring are logical
First clutch connection is crossed, first sun gear is connect with first planet carrier by the second clutch, and described the
Three planet carriers are connect with third sun gear by the third clutch, and second planet carrier and the 4th sun gear are described in
The connection of 4th clutch, the third planet carrier are connect with the 4th gear ring by the 5th clutch.
4. eight speed automatic transmission according to claim 1, which is characterized in that the first planet carrier and the 4th gear ring are logical
First clutch connection is crossed, first sun gear is connect with first planet carrier by the second clutch, and described the
Three planet carriers are connect with third gear ring by the third clutch, and second planet carrier and the 4th sun gear pass through described the
The connection of four clutches, the third planet carrier are connect with the 4th gear ring by the 5th clutch.
5. eight speed automatic transmission according to claim 1, which is characterized in that the first planet carrier and the 4th gear ring are logical
First clutch connection is crossed, first sun gear is connect with first planet carrier by the second clutch, and described the
Three sun gears are connect with third gear ring by the third clutch, and second planet carrier and the 4th sun gear pass through described the
The connection of four clutches, the third planet carrier are connect with the 4th gear ring by the 5th clutch.
6. eight speed automatic transmission according to claim 1, which is characterized in that the first planetary gear set, the second row
Star gear set, third planet gear set and the coaxial arrangement of the second planetary gear set.
7. eight speed automatic transmissions described in -6 any one according to claim 1, which is characterized in that pass through engagement described first
Clutch, second clutch and the 4th clutch separate the third clutch and the 5th clutch, in the input link
1 gear transmission ratio is generated between output link；
By engaging the first clutch, second clutch and third clutch, separate the 4th clutch and the 5th from
Clutch, to generate 2 gear transmission ratios between the input link and output link；
By engaging the first clutch, third clutch and the 4th clutch, separate the second clutch and the 5th from
Clutch, to generate 3 gear transmission ratios between the input link and output link；
By engaging the first clutch, third clutch and the 5th clutch, separate the second clutch and the 4th from
Clutch, to generate 4 gear transmission ratios between the input link and output link；
By engaging the first clutch, the 4th clutch and the 5th clutch, separate the second clutch and third from
Clutch, to generate 5 gear transmission ratios between the input link and output link；
By engaging the third clutch, the 4th clutch and the 5th clutch, separate the first clutch and second from
Clutch, to generate 6 gear transmission ratios between the input link and output link；
By engaging the second clutch, the 4th clutch and the 5th clutch, separate the first clutch and third from
Clutch, to generate 7 gear transmission ratios between the input link and output link；
By engaging the second clutch, third clutch and the 5th clutch, separate the first clutch and the 4th from
Clutch, to generate 8 gear transmission ratios between the input link and output link；
By engaging the first clutch, second clutch and the 5th clutch, separate the third clutch and the 4th from
Clutch, to generate back gear ratio between the input link and output link.
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| CN201710285778.5A CN106917850B (en) | 2017-04-27 | 2017-04-27 | Eight speed automatic transmissions |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710285778.5A CN106917850B (en) | 2017-04-27 | 2017-04-27 | Eight speed automatic transmissions |
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| CN106917850A CN106917850A (en) | 2017-07-04 |
| CN106917850B true CN106917850B (en) | 2018-12-14 |
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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108180265B (en) * | 2017-12-29 | 2021-12-24 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN108223718B (en) * | 2017-12-29 | 2020-01-03 | 广州汽车集团股份有限公司 | Four-planet-row automatic transmission and vehicle |
| CN109812550B (en) * | 2019-02-28 | 2022-03-04 | 东华大学 | Eight-gear gearbox for bulldozer |
| CN110608270B (en) * | 2019-09-24 | 2024-05-14 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN115325116B (en) * | 2022-10-17 | 2023-01-06 | 北京航空航天大学 | Multi-gear planetary gear transmission device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104033549A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Eight-gear transmission |
| CN106523628A (en) * | 2016-12-16 | 2017-03-22 | 贵州凯星液力传动机械有限公司 | Eight-gear planetary automatic transmission |
| CN106594201A (en) * | 2017-01-27 | 2017-04-26 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006006622A1 (en) * | 2006-02-14 | 2007-09-13 | Zf Friedrichshafen Ag | Multi-speed transmission |
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2017
- 2017-04-27 CN CN201710285778.5A patent/CN106917850B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104033549A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Eight-gear transmission |
| CN106523628A (en) * | 2016-12-16 | 2017-03-22 | 贵州凯星液力传动机械有限公司 | Eight-gear planetary automatic transmission |
| CN106594201A (en) * | 2017-01-27 | 2017-04-26 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
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