CN109538718A - Six speed automatic transmissions and automobile - Google Patents
Six speed automatic transmissions and automobile Download PDFInfo
- Publication number
- CN109538718A CN109538718A CN201710857311.3A CN201710857311A CN109538718A CN 109538718 A CN109538718 A CN 109538718A CN 201710857311 A CN201710857311 A CN 201710857311A CN 109538718 A CN109538718 A CN 109538718A
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- clutch
- gear
- braking member
- planetary gear
- planet carrier
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 115
- 238000003466 welding Methods 0.000 claims description 6
- 239000007787 solid Substances 0.000 claims 1
- 238000004519 manufacturing process Methods 0.000 abstract description 10
- 238000012545 processing Methods 0.000 abstract description 7
- 238000006467 substitution reaction Methods 0.000 abstract description 3
- 238000010586 diagram Methods 0.000 description 8
- 230000008859 change Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 238000005096 rolling process Methods 0.000 description 3
- 230000005526 G1 to G0 transition Effects 0.000 description 2
- 230000009977 dual effect Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
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
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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
- F16H2200/0052—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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- 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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention provides a kind of six speed automatic transmissions and automobiles, six speed automatic transmission includes input link, output link, case of transmission, first planetary gear set, the second planetary gear set, third planet gear set, first clutch, second clutch, third clutch, the first braking member and the second braking member, first clutch, second clutch, third clutch, the first braking member and the second braking member are selectively engaged or separate, to generate six forward gear transmissions when back gear ratio between input link and output link.Six speed automatic transmissions of the embodiment of the present invention, achieve the purpose that increase clutch quantity by using clutch substitution braking member, reduce braking member quantity, reduce the processing and manufacture of internal tooth on case of transmission, reduce case of transmission difficulty of processing and manufacturing cost, be conducive to the lightweight of case of transmission, and entire speed changer can be made more compact.
Description
Technical field
The invention belongs to technical field of automobile transmission, more particularly to a kind of six speed automatic transmissions and automobile.
Background technique
Electric control hydraulic variator system realizes that the mechanism of speed change is usually the planetary gear speed-changing for including multiple planet rows
Mechanism.The power of engine is passed to after epicyclic transmission carries out speed change after fluid torque-converter and exports.Automatic transmission
Volume, weight, efficiency and bearing capacity it is directly related with epicyclic transmission.The gear of automatic transmission drive train
Number is more, and the fuel consumption of automobile is lower, and economy is better.But with the increase of gear number, the quantity of planet row and behaviour
The quantity of vertical element (clutch and brake) is also increasing, and the design for meeting theoretical stage ratio is even more to be difficult to realize.Industry is always
Seeking to go out to meet the knot of automotive performance demand with less planet row and operating element (clutch and brake) number combinations
The stronger more efficient planetary gear automatic transmission of the compact intensity of structure.
There are mainly four types of schemes by the 6AT (six speed automatic transmissions) of carrying passenger car at present, first is that, love letter, ZF and Ji
The Lai Peilaijie scheme that benefit uses；Second is that the scheme that modern A6MF and A6LF series uses；Third is that general 6T series used
Scheme；Fourth is that six fast scheme used in the blue sky Chuan Chi of Mazda.
Lai Peilaijie scheme is to increase a rows of planetary row on the basis of four gear transmission of Ravigneaux to realize, without straight
Connect gear.With the realization of three planet rows, the position of clutch is also with Lai Peilaijie scheme difference for general and modern scheme
Difference, and there is a planet row to use dual planetary gear structure in modern volume production series A 6MF and A6LF, relative to uniline star
For wheel, it is unfavorable for the compactedness of structure and increases weight and cost.Six fast schemes used in the blue sky Chuan Chi of Mazda are originated from
The lateral arrangement for the scheme that ALLISON company, the U.S. uses on cart, direct gear appear in four gears.
Modern and general scheme is realized with two clutches and three brakes, and the quantity of brake is more than
The number of clutch.Brake is finally that friction steel disc tooth is connected on shell, and more brakes undoubtedly increase adding for shell
Work manufacture difficulty；And since case material is usually aluminium alloy, more brakes undoubtedly can to can proof strength while
Light-weight design cause difficulty.Lai Peilaijie scheme uses Ravigneaux structure, dual planetary gear structure occurs, how multiple structure piece uploading is
It is miscellaneous, it is unfavorable for lightweight.Six fast schemes used in the blue sky Chuan Chi of Mazda are originated from the side used on matching diesel engine heavy type cart
The lateral arrangement of case is matched with gasoline engine, has inadequate natural endowment in the transmission ratio configuration that can be realized.
Summary of the invention
The technical problems to be solved by the present invention are: being directed to existing six speed automatic transmission, more brake is used
The problem of increasing the processing and manufacturing difficulty of case of transmission provides six speed automatic transmissions of one kind and automobile.
In order to solve the above technical problems, on the one hand, a kind of six speed automatic transmissions of the embodiment of the present invention, comprising:
Input link；
Output link；
Case of transmission；
First planetary gear set, the second planetary gear set and third planet gear set；The first planetary gear set includes
First sun gear, the first planetary gear, the first gear ring and first planet carrier；First sun gear and the first planetary gear external toothing pass
Dynamic, first planetary gear and the first gear ring Inside gear drive, first planetary gear are rotatably supported on the first planet carrier
On；Second planetary gear set includes the second sun gear, the second planetary gear, the second gear ring and the second planet carrier；Described second
Sun gear and the second planetary gear external toothing are driven, second planetary gear and the second gear ring Inside gear drive, second planet
Wheel is rotatably supported on second planet carrier；The third planet gear set includes third sun gear, the third line star-wheel, third
Gear ring and third planet carrier；The third sun gear and the external toothing of the third line star-wheel are driven, the third line star-wheel and third tooth
Inside gear drive is enclosed, the third line star-wheel is rotatably supported in the third planet carrier；First gear ring and third planet
Frame is fixedly linked, and second planet carrier is fixedly linked with third gear ring, the output link and first gear ring or third
Planet carrier is fixedly linked, and the third sun gear is fixedly linked with case of transmission；
First clutch, second clutch, third clutch, the first braking member and the second braking member, described first
Sun gear connect by the first clutch with the input link, the first planet carrier pass through the second clutch and
The input link connection, second gear ring are connect by the third clutch with the first planet carrier, and described first
Sun gear is connect by first braking member with the case of transmission, and the first planet carrier is braked by described second
Element is connect with the case of transmission；
The first clutch, second clutch, third clutch, the first braking member and the second braking member selectivity
Ground engagement or separation, to generate six forward gear transmissions when reverse gear between the input link and output link
Than.
Optionally, by engaging the third clutch and the second braking member, separate the first clutch, second from
Clutch and the first braking member, to generate 1 gear transmission ratio between the input link and output link；
By engaging the third clutch and the first braking member, the first clutch, two clutches and the are separated
Two braking members, to generate 2 gear transmission ratios between the input link and output link；
By engaging the first clutch and third clutch, separate the second clutch, the first braking member and
Second braking member, to generate 3 gear transmission ratios between the input link and output link；
By engaging the second clutch and third clutch, separate the first clutch, the first braking member and
Second braking member, to generate 4 gear transmission ratios between the input link and output link；
By engaging the first clutch and second clutch, separate the third clutch, the first braking member and
Second braking member, to generate 5 gear transmission ratios between the input link and output link；
By engaging the second clutch and the first braking member, separate the first clutch, third clutch and
Second braking member, to generate 6 gear transmission ratios between the input link and output link.
Optionally, by engaging the first clutch and the second braking member, separate the second clutch, third from
Clutch and the first braking member, to generate back gear ratio between the input link and output link.
Optionally, the first clutch, second clutch and third clutch are multi-plate wet clutch or dental inlay
Formula clutch.
Optionally, first braking member and the second braking member are drum brake, multi-disk wet type brake, list
To clutch or multimode clutch.
Optionally, the first planetary gear set, the second planetary gear set and the coaxial arrangement of third planet gear set.
Optionally, the first planetary gear set, the second planetary gear set and third planet gear set successively sequential lateral
Or it is longitudinally disposed.
Optionally, the input link welds with second sun gear, is integrally manufactured or connect by spline；It is described
Second planet carrier and third gear ring weld, integrally manufactured or connect by spline；The third sun gear and case of transmission
Welding, it is integrally manufactured or by spline connection；The output link and first gear ring or third planet carrier welding, one
Manufacture is connected by spline.
Six speed automatic transmissions of the embodiment of the present invention pass through three planetary gear sets, three clutches and two brakings
The Reasonable Arrangement of element, realizes six forward gears and one reverses gear.By using clutch substitution braking member reach increase from
Clutch quantity, the purpose for reducing braking member quantity, reduce the processing and manufacture of internal tooth on case of transmission, reduce speed changer
Shell difficulty of processing and manufacturing cost are conducive to the lightweight of case of transmission, and entire speed changer can be made more compact.
In addition, the embodiment of the present invention also provides a kind of automobile comprising six above-mentioned speed automatic transmissions.
Detailed description of the invention
Fig. 1 is the structure diagram for six speed automatic transmissions that one embodiment of the invention provides；
Fig. 2 is the six speed automatic transmissions 1 gear power transmitting schematic diagram that one embodiment of the invention provides；
Fig. 3 is the six speed automatic transmissions 2 gear power transmitting schematic diagram that one embodiment of the invention provides；
Fig. 4 is the six speed automatic transmissions 3 gear power transmitting schematic diagram that one embodiment of the invention provides；
Fig. 5 is the six speed automatic transmissions 4 gear power transmitting schematic diagram that one embodiment of the invention provides；
Fig. 6 is the six speed automatic transmissions 5 gear power transmitting schematic diagram that one embodiment of the invention provides；
Fig. 7 is the six speed automatic transmissions 6 gear power transmitting schematic diagram that one embodiment of the invention provides；
Fig. 8 be first embodiment of the invention provide six speed automatic transmissions reverse gear power transmitting schematic diagram.
Appended drawing reference in specification is as follows:
11, input link；12, output link；
21, case of transmission；
30, first planetary gear set；31, the first sun gear；32, the first planetary gear；33, the first gear ring；34, the first planet
Frame；
40, the second planetary gear set；41, the second sun gear；42, the second planetary gear；43, the second gear ring；44, the second planet
Frame；
50, third planet gear set；51, third sun gear；52, the third line star-wheel；53, third gear ring；54, third planet
Frame；
61, first clutch；62, second clutch；63, third clutch；
71, the first braking member；72, the second braking member.
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, six speed automatic transmissions that first embodiment of the invention provides, including input link 11, output structure
Part 12, case of transmission 21, first planetary gear set 30, the second planetary gear set 40, third planet gear set 50, the first clutch
Device 61, second clutch 62, third clutch 63, the first braking member 71 and the second braking member 72.
In the present embodiment, each planetary gear set is single star row of interior external toothing.Specifically:
First planetary gear set 30 includes the first sun gear 31, the first planetary gear 32, the first gear ring 33, first planet carrier
34.First sun gear 31 and 32 external toothing of the first planetary gear are driven, and are nibbled in first planetary gear 32 and the first gear ring 33
Transmission is closed, first planetary gear 32 is rotatably supported on the pin shaft of the first planet carrier 34 by rolling or sliding bearing.
Second planetary gear set 40 includes the second sun gear 41, the second planetary gear 42, the second gear ring 43, the second planet carrier
44.Second sun gear 41 and 42 external toothing of the second planetary gear are driven, and are nibbled in second planetary gear 42 and the second gear ring 43
Transmission is closed, second planetary gear 42 is rotatably supported on the pin shaft of second planet carrier 44 by rolling or sliding bearing.
Third planet gear set 50 includes third sun gear 51, the third line star-wheel 52, third gear ring 53, third planet carrier
54.The third sun gear 51 is driven with 52 external toothing of the third line star-wheel, is nibbled in the third line star-wheel 52 and third gear ring 53
Transmission is closed, the third line star-wheel 52 is rotatably supported on the pin shaft of the third planet carrier 54 by rolling or sliding bearing.
As shown in Figure 1, first gear ring 33 is fixedly linked with third planet carrier 54, second planet carrier 44 and third
Gear ring 53 is fixedly linked, and the output link 12 is fixedly linked with the third planet carrier 54, the third sun gear 51 and change
Fast device shell 21 is fixedly linked.
As shown in Figure 1, first sun gear 31 is connect by the first clutch 61 with the input link 11, institute
It states first planet carrier 34 to connect by the second clutch 62 with the input link 11, second gear ring 43 passes through described
Third clutch 63 is connect with the first planet carrier 34, and first sun gear 31 passes through first braking member 71 and institute
The connection of case of transmission 21 is stated, the first planet carrier 34 is connected by second braking member 72 with the case of transmission 21
It connects.
The input link 11 welds with second sun gear 41, integrally manufactured or connect by spline；Described
Two planet carriers 42 and third gear ring 53 weld, integrally manufactured or connect by spline；The third sun gear 51 and speed changer
Shell 21 welding, it is integrally manufactured or by spline connection；The output link 12 and first gear ring 33 or third planet
Frame 52 welding, it is integrally manufactured or by spline connection.
In one embodiment, the first planetary gear set 30, the second planetary gear set 40 and third planet gear set 50
Coaxial arrangement.It is further preferable that the first planetary gear set 30, the second planetary gear set 40 and third planet gear set 50 according to
Secondary sequential lateral is longitudinally disposed.With this, so that six speed automatic transmission is more compact.
In the present embodiment, the first clutch 61, second clutch 62, third clutch 63, the first braking member 71
And second braking member 72 be selectively engaged or separate, between the input link 11 and output link 12 generate six
Forward gear is driven a when back gear ratio.
In the present embodiment, the first clutch 61, second clutch 62,63 first braking member 71 of third clutch and
The manipulation logic of second braking member 72 is referring to following table 1:
Table 1
In table 1, mark ● indicate that the operating element engages, blank space indicates that the operating element separates.K1, k2 and k3 are respectively
First planetary gear set 30, the second planetary gear set 40, third planet gear set 50 planet row characteristic parameter, the planet row is special
It levies parameter and is equal to the ratio between gear ring and the number of teeth of sun gear.That is k1 is the ratio between the number of teeth of the first gear ring 33 and the first sun gear 31, k2
For the ratio between the number of teeth of the second gear ring 43 and the second sun gear 41, k3 is the ratio between the number of teeth of third gear ring 53 and third sun gear 51.
Referring to Fig. 1-8, under the manipulation logic of table 1, the power transmission line of six 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 third clutch 63 and the second braking member 72,1 gear is realized, 1 gear transmission ratio is i1=
(1+K2)*(1+1/K3).Due to the engagement of the second braking member 72 and third clutch 63, so that the second gear ring 43 realizes system
It is dynamic, it is exported so that the second planetary gear set 40 realizes that single-degree-of-freedom is slowed down, reduction ratio K2+1；Then third planet tooth is sealed in
Wheel group 50；Since third sun gear 51 is often braked, therefore third planet gear set 50 realizes the output of single-degree-of-freedom speedup, speed increasing ratio
For (1+K3)/K3；Therefore 1 gear transmission ratio is (1+K2) * (1+1/K3).The power transmission line of 1 gear are as follows: input link 11 → the second
41 → first planetary gear set of sun gear, 30 decelerations → 50 speedups of third planet gear set → 54 → output link of third planet carrier
12。
(2) 2 gear power transmission lines
As shown in figure 3, only engaging third clutch 63 and the first braking member 71,2 gears, 2 gear transmission ratios are as follows: i2=are realized
((1+K1)(1+K2)+K3(1+K1+K2))/(K3(1+K1)).2 gear power transmission lines divide two-way to transmit, route one: input structure
11 → the second sun gear of part, 41 → the second planetary gear, 42 → the second planet carrier 44 → third, 53 → the third line of gear ring star-wheel, 52 (third
Sun gear 51 and case of transmission 21, which are fixedly linked, limits the one degree of freedom of third planet gear set 50) → third planet carrier 54
→ output link 12.Route two: 11 → the second sun gear of input link, 41 → the second planetary gear, 42 → the second 43 → third of gear ring
(engagement of the first braking member 71 is so that first for 63 → first planet carrier of clutch, 34 → the first planetary gear, 32 → the first gear ring 33
Planetary gear set 30 realizes single-degree-of-freedom output) → 54 → output link of third planet carrier 12.
(3) 3 gear power transmission lines
As shown in figure 4, only engaging first clutch 61 and third clutch 63,3 gears, 3 gear transmission ratios are as follows: i3=are realized
((1+K1)(1+K2)+K3(1+K1+K2))/(K3(1+K1+K2)).The transmitting of two or three tunnel of its power transmission line point, route one: defeated
Enter 11 → the second sun gear of component, 41 → the second planetary gear, 42 → the second planet carrier 44 → third, 53 → the third line of gear ring star-wheel 52
→ third planet carrier 54 (third sun gear 51 and case of transmission 21 be fixedly linked limit one of third planet gear set 50 from
By spending) → output link 12；Route two: 11 → the second sun gear of input link, 41 → the second planetary gear, 42 → the second gear ring 43 →
63 → first planet carrier of third clutch, 34 → the first planetary gear, 32 → the first gear ring 33 → third planet carrier, 54 → output link
12；Route 3: 11 → first clutch of input link, 61 → the first sun gear, 31 → the first planetary gear, 32 → the first gear ring 33 → the
Three 54 → output links of planet carrier 12.
(4) 4 gear power transmission lines
As shown in figure 5, only engaging second clutch 62 and third clutch 63,4 gears, 4 gear transmission ratios are as follows: I4=(1 are realized
+K3)/K3.Under the gear, due to the engagement of second clutch 62 and third clutch 63, so that the second planetary gear set 40
Third planet gear set 50 is integrally sealed in as a revolution participates in transmission；Since third sun gear 51 is often braked, so that third
Planetary gear set 50 realizes that single-degree-of-freedom is slowed down and exports that reduction ratio is (1+K3)/K3；Therefore the reduction ratio under the gear is (1+
K3)/K3.Its power transmission line are as follows: 11 → the second planetary gear set 40 of input link turns round entirety → third planet gear set
50 are slowed down, and (third sun gear 51 and case of transmission 21 are fixedly linked and limit a freedom of third planet gear set 50
Degree) → output link 12.
(5) 5 gear power transmission lines
As shown in fig. 6, only engaging first clutch 61 and second clutch 62, realize that 5 gears, 5 gears are direct gear, transmission ratio
For i5=1.Due to being engaged while first clutch 61 and second clutch 62, so that first planetary gear set 30 is as a whole
Input, is directly exported by third planet carrier 54, to realize direct gear.Its power transmission line: 11 → the first row of input link
Star gear set 30 turns round entirety → 54 → output link of third planet carrier 12.
(6) 6 gear power transmission lines
As shown in fig. 7, only engaging second clutch 62 and the first braking member 71,6 gears are directly realized by, realize 6 gears, 6 gears
For overgear, transmission ratio is i6=K1/ (1+K1).Under the gear, since the engagement of the first braking member 71 is so that first too
Sun wheel 31 is locked up, so that the one degree of freedom of first planetary gear set 30 is limited, so that first planetary gear set 30 is real
Existing single-degree-of-freedom speedup output, speed increasing ratio are K1/ (1+K1)；Therefore the transmission ratio under the gear is K1/ (1+K1).Its power passes
Pass route are as follows: 11 → first planetary gear set of input link 30 carries out speedup → output link 12.
(7) reverse gear power transmission line
As shown in figure 8, only engaging first clutch 61 and the second braking member 72, realization is reversed gear, back gear ratio iR
=-K1.Under the gear, since the engagement of first second braking member 72 is so that first planet carrier 34 is locked up, thus limitation the
The one degree of freedom of one planetary gear set 30, so that first planetary gear set 30 realizes the output of single-degree-of-freedom negative deceleration,
Speed increasing ratio is-K1；Therefore the speed ratio under the gear is-K1.Its power transmission line: 11 → first planetary gear set of input link 30
Carry out negative deceleration → output link 12.
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 61, second clutch 62, third
Clutch 63 can be multi-plate wet clutch or jaw clutch.
Braking member effect is to realize being connected or separating for component and case of transmission by engaging or separating, to component
Braking or separation, the type of braking member have drum brake, multi-disk wet type brake, one-way clutch letter multimode clutch
Device.That is, first braking member 71 and the second braking member 72 can be drum brake, multi-disk wet type brake, unidirectional
Clutch or multimode clutch.
Six speed automatic transmissions of the above embodiment of the present invention pass through three planetary gear sets, three clutches and two
The Reasonable Arrangement of brake, realizes six forward gears and one reverses gear.By using clutch substitution brake reach increase from
Clutch quantity, the purpose for reducing braking member quantity, reduce the processing and manufacture of internal tooth on case of transmission, reduce speed changer
Shell difficulty of processing and manufacturing cost are conducive to the lightweight of case of transmission, and entire speed changer can be made more compact.
In addition, using greater number of clutch for braking member, be conducive to the nested designs of clutch,
Meeting is so that entire planetary gear mechanism is more compact.And more clutch quantity are conducive in specific gear incision line-break star tooth
Connection relationship between wheel group makes the planetary gear set of redundancy be not involved in rotation, reduces band row's towing loss, improves system effectiveness.
In addition, more clutches are more by increasing planetary gear set or the more operating elements progress of increase after being more advantageous to
Speed is expanded.
In addition, third sun gear is often fixed with case of transmission, avoid in shift process braking member to case of transmission
Direct impact, so as to improve the loading conditions of case of transmission.
Six speed automatic transmission provided by the above embodiment, the output link 12 and 54 stationary phase of third planet carrier
Even, to be suitable for longitudinal speed changer.
In another embodiment not shown in the figure, it is also possible to the output link and the first gear ring stationary phase
Even, to be suitable for horizontal speed changer.
In addition, the present invention also provides a kind of automobiles comprising six speed automatic transmissions of above-described embodiment.
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 (9)
1. a kind of six speed automatic transmissions characterized by comprising
Input link；
Output link；
Case of transmission；
First planetary gear set, the second planetary gear set and third planet gear set；The first planetary gear set includes first
Sun gear, the first planetary gear, the first gear ring and first planet carrier；First sun gear and the first planetary gear external toothing are driven,
First planetary gear and the first gear ring Inside gear drive, first planetary gear are rotatably supported in the first planet carrier；
Second planetary gear set includes the second sun gear, the second planetary gear, the second gear ring and the second planet carrier；Second sun
Wheel is driven with the second planetary gear external toothing, second planetary gear and the second gear ring Inside gear drive, the second planetary gear rotation
Turn to be supported on second planet carrier；The third planet gear set includes third sun gear, the third line star-wheel, third gear ring
And third planet carrier；The third sun gear and the external toothing of the third line star-wheel are driven, in the third line star-wheel and third gear ring
Engaged transmission, the third line star-wheel are rotatably supported in the third planet carrier；First gear ring and third planet carrier are solid
Fixed to be connected, second planet carrier is fixedly linked with third gear ring, the output link and first gear ring or third planet
Frame is fixedly linked, and the third sun gear is fixedly linked with case of transmission；
First clutch, second clutch, third clutch, the first braking member and the second braking member, first sun
Wheel is connect by the first clutch with the input link, the first planet carrier pass through the second clutch with it is described
Input link connection, second gear ring are connect by the third clutch with the first planet carrier, first sun
Wheel is connect by first braking member with the case of transmission, and the first planet carrier passes through second braking member
It is connect with the case of transmission；
The first clutch, second clutch, third clutch, the first braking member and the second braking member selectively connect
It closes or separates, to generate six forward gears transmissions when back gear ratio between the input link and output link.
2. six speed automatic transmission according to claim 1, which is characterized in that by engaging the third clutch and the
Two braking members separate the first clutch, second clutch and the first braking member, in the input link and output
1 gear transmission ratio is generated between component；
By engaging the third clutch and the first braking member, the first clutch, two clutches and the second system are separated
Dynamic element, to generate 2 gear transmission ratios between the input link and output link；
By engaging the first clutch and third clutch, the second clutch, the first braking member and second are separated
Braking member, to generate 3 gear transmission ratios between the input link and output link；
By engaging the second clutch and third clutch, the first clutch, the first braking member and second are separated
Braking member, to generate 4 gear transmission ratios between the input link and output link；
By engaging the first clutch and second clutch, the third clutch, the first braking member and second are separated
Braking member, to generate 5 gear transmission ratios between the input link and output link；
By engaging the second clutch and the first braking member, the first clutch, third clutch and second are separated
Braking member, to generate 6 gear transmission ratios between the input link and output link.
3. six speed automatic transmission according to claim 1 or 2, which is characterized in that by engaging the first clutch
And second braking member, separate the second clutch, third clutch and the first braking member, with the input link with
Back gear ratio is generated between output link.
4. six speed automatic transmission according to claim 1, which is characterized in that the first clutch, second clutch
And third clutch is multi-plate wet clutch or jaw clutch.
5. six speed automatic transmission according to claim 1, which is characterized in that first braking member and the second braking
Element is drum brake, multi-disk wet type brake, one-way clutch or multimode clutch.
6. six speed automatic transmission according to claim 1, which is characterized in that the first planetary gear set, the second row
Star gear set and the coaxial arrangement of third planet gear set.
7. six speed automatic transmission according to claim 1, which is characterized in that the first planetary gear set, the second row
Star gear set and third planet gear set successively sequential lateral or longitudinally disposed.
8. six speed automatic transmission according to claim 1, which is characterized in that the input link and second sun
Wheel welding, it is integrally manufactured or by spline connection；Second planet carrier and third gear ring weld, integrally manufactured or pass through
Spline connection；The third sun gear and case of transmission weld, integrally manufactured or connect by spline；The output link
With first gear ring or third planet carrier welding, integrally manufactured or connect by spline.
9. a kind of automobile, which is characterized in that including described in any item six speed automatic transmissions of such as claim 1-8.
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| CN201710857311.3A CN109538718B (en) | 2017-09-21 | 2017-09-21 | Six-gear automatic transmission and automobile |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201710857311.3A CN109538718B (en) | 2017-09-21 | 2017-09-21 | Six-gear automatic transmission and automobile |
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| CN109538718A true CN109538718A (en) | 2019-03-29 |
| CN109538718B CN109538718B (en) | 2024-05-24 |
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Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010039996A1 (en) * | 2010-08-31 | 2012-03-01 | Zf Friedrichshafen Ag | Multi-step planetary reduction gearbox for motor vehicle, has planetary gear trains selectively engaged with shafts so that various transmission ratios are produced between drive and driven shafts to realize forward and reverse gears |
| CN104033545A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Six-gear speed changer |
| CN105114558A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear automatic transmission |
| CN207278803U (en) * | 2017-09-21 | 2018-04-27 | 广州汽车集团股份有限公司 | Six speed automatic transmissions and automobile |
-
2017
- 2017-09-21 CN CN201710857311.3A patent/CN109538718B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102010039996A1 (en) * | 2010-08-31 | 2012-03-01 | Zf Friedrichshafen Ag | Multi-step planetary reduction gearbox for motor vehicle, has planetary gear trains selectively engaged with shafts so that various transmission ratios are produced between drive and driven shafts to realize forward and reverse gears |
| CN104033545A (en) * | 2014-06-11 | 2014-09-10 | 同济大学 | Six-gear speed changer |
| CN105114558A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear automatic transmission |
| CN207278803U (en) * | 2017-09-21 | 2018-04-27 | 广州汽车集团股份有限公司 | Six speed automatic transmissions and automobile |
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| Publication number | Publication date |
|---|---|
| CN109538718B (en) | 2024-05-24 |
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