CN206571918U - automatic transmission and vehicle - Google Patents
automatic transmission and vehicle Download PDFInfo
- Publication number
- CN206571918U CN206571918U CN201720107581.8U CN201720107581U CN206571918U CN 206571918 U CN206571918 U CN 206571918U CN 201720107581 U CN201720107581 U CN 201720107581U CN 206571918 U CN206571918 U CN 206571918U
- Authority
- CN
- China
- Prior art keywords
- clutch
- gear
- automatic transmission
- planet
- sun gear
- 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.)
- Withdrawn - After Issue
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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
- 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
-
- 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
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten forward speeds
-
- 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
-
- 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
-
- 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
Abstract
The utility model is related to a kind of automatic transmission and vehicle, pass through four planetary gearsets, the Reasonable Arrangement of six clutches, the automatic transmission that the utility model is provided is set to be reversed gear with ten forward gears and one, and pass through the control of three clutches, the transmission of power under the gear can be ensured, on the premise of its transmission efficiency and planet wheel speed is ensured, by making the first gear ring be directly fixed on casing and without using brake, on the one hand make the structure of automatic transmission compacter, on the other hand impact of the brake to casing in shift process is reduced, improve the loading conditions of casing.Comparatively, increase the quantity of clutch without using brake, on the one hand by nested arrangement automatic transmission can be caused compacter, on the other hand the utilization rate of clutch can also be increased, and disconnect shortening idle running transmission route, so as to reduce idle running planetary gearsets towing moment of torsion, reduce band row and stir oily loss, improve transmission efficiency.
Description
Technical field
The utility model is related to automatic transmission field, especially a kind of automatic transmission and with the automatic transmission
Vehicle.
Background technology
Automatic transmission (Automatic Transmission, AT) generally comprise multiple planetary gearsets, brake and
Clutch, multiple planetary gearsets, brake and clutch are linked together by certain mode, the torsion produced when engine
When square enters automatic transmission, automatic transmission can according to different working methods it is multistage change moment of torsion into it, and
Moment of torsion after change is outwards exported.From theory of mechanics, mechanism has the number that the condition for determining to move is mechanism power source
Amount is equal to mechanism rotating speed number of degrees of freedom,.Because AT is to be implemented in combination with different gears by the combination of different clutch/brakes, i.e.,
The free degree of automatic transmission is constrained by brake/clutch, so that reduction degree of freedom in system purpose is reached, it is final to ensure certainly
Dynamic speed changer has the motion determined.That is, for the single power source automatic transmission that a degree of freedom in system number is N,
It is that automatic transmission (N-1) the individual rotating speed is limited by operating elements such as brake/clutch with the condition for determining to move
The free degree.
In general, the gear that automatic transmission has is more, the power performance and fuel-economy performance of automobile are better, but
It is, the quantity of planetary gearsets number, clutch and brake, and driving member connection determines transmission to a certain extent
The complexity of scenario-frame arrangement.Number of degrees of freedom, increases the operating element increasing number for conversion of being shifted gears between adjacent gear,
Control difficulty increase will all be caused, and volume, efficiency and the bearing capacity of automatic transmission produce direct influence.Each
The power transmission route of gear depends on transmission scheme, should avoid the occurrence of internal power circulation, will influence each gear transmission efficiency.
With the automobile emission regulation increasingly requirement of harshness and the raising to fuel economy requirement, gear-change of automatic transmissions
Position demand increases.For planetary gearsets automatic transmission, typically increase gear by two kinds of approach：One is increase planetary gear
The quantity of group；Two be increase free degree quantity, but the quantity of increase planetary gearsets can significantly increase the body of automatic transmission
Product and weight, increase free degree quantity are easily caused increasing for actuation member, manipulation difficulty during increase gearshift.Therefore, seeking
A kind of planetary gearsets and operating element quantity best of breed, compact conformation, the efficient planetary automatic speed-changing mechanism of transmission turn into
Major vehicle enterprises or the key of research and development institution's product development.
Ten gear transmissions that passenger car in the market is used at this stage mainly have two kinds：
First, the 10R80 automatic transmission schemes of general and Ford cooperative development；The program is another using four clutches
Brake, with 5 frees degree, each gear is needed in combination with 4 each shifting elements.
2nd, the direct shift-10AT schemes of Toyota, the preceding two minings La Weina structures of the program, with four
Clutch and two brakes, are 4DOF system, and each gear is needed in combination with 3 shifting elements.
Either 10R80 schemes or the scheme of Toyota, are realized using four clutches and two brakes,
That is having two brakes, brake is eventually by connector, and such as friction steel disc tooth is connected on casing, brake
Presence add the processing and manufacturing difficulty of casing；Simultaneously because the material of casing is usually aluminium alloy, brake is in closure
Casing can be impacted, the intensity requirement to casing is higher, and this can cause difficulty to the light-weight design of casing again, eventually
Increase the weight of automatic transmission.
Utility model content
The purpose of this utility model is to provide a kind of automatic transmission and the vehicle with the automatic transmission, and this is automatic
Speed changer is without using brake, and all gears are realized by the control of clutch, is conducive to improving the loading conditions of casing,
Make that the structure of automatic transmission is compacter, transmission efficiency is higher.
The utility model, which is provided, includes input shaft, casing, the first planetary gearsets, the second planetary gearsets, third planet
Gear train, fourth planet gear train, first clutch, second clutch, the 3rd clutch, the 4th clutch, the 5th clutch,
6th clutch and output shaft；
First planetary gearsets include the first sun gear, the first planetary gear, the first gear ring and the first planet carrier, described
First planetary gear is rotatably supported on first planet carrier, and first planetary gear be located at first sun gear with
Between first gear ring, and engaged with first sun gear and first gear ring；
Second planetary gearsets include the second sun gear, the second planetary gear, the second gear ring and the second planet carrier, described
Second planetary gear is rotatably supported on second planet carrier, and second planetary gear be located at second sun gear with
Between second gear ring, and engaged with second sun gear and second gear ring；
The third planet gear train includes the 3rd sun gear, the third line star-wheel, the 3rd gear ring and the third line carrier, described
The third line star-wheel is rotatably supported in the third line carrier, and the third line star-wheel be located at the 3rd sun gear with
Between 3rd gear ring, and engaged with the 3rd sun gear and the 3rd gear ring；
The fourth planet gear train includes the 4th sun gear, fourth line star-wheel, the 4th gear ring and fourth line carrier, described
Fourth line star-wheel is rotatably supported in the fourth line carrier, and the fourth line star-wheel be located at the 4th sun gear with
Between 4th gear ring, and engaged with the 4th sun gear and the 4th gear ring；
The input shaft is connected with second planet carrier, and the output shaft is connected with the fourth line carrier, and described
One gear ring is fixed on the casing, and first sun gear is connected with second sun gear, second gear ring with it is described
3rd sun gear is connected, and the 3rd gear ring is connected with the 4th sun gear；
One end of the first clutch is connected with one end of first planet carrier and the second clutch, and described
The other end of one clutch is connected with one end, one end of the 6th clutch and the 4th gear ring of the 4th clutch；
One end of the second clutch is connected with one end of the first clutch and first planet carrier, and described
The other end of two clutches is connected with first sun gear and second sun gear；
One end of 4th clutch and one end, one end of the 6th clutch and the 4th gear ring of the first clutch
It is connected, the other end of the 4th clutch is connected with second gear ring and the 3rd sun gear；
One end of 5th clutch is connected with the input shaft and second planet carrier, the 5th clutch
The other end is connected with the 3rd gear ring and the 4th sun gear；
One end of 6th clutch and one end of the first clutch, one end of the 4th clutch and described
4th gear ring is connected, and the other end of the 6th clutch is connected with the third line carrier；
3rd clutch is selectively integral the third planet gear train to be rotated.
Further, the output end of the input of the input shaft and the output shaft is respectively arranged at first planet
Gear train, second planetary gearsets, the both sides of the third planet gear train and the fourth planet gear train, it is described defeated
Enter the power transmission direction of axle to be parallel to each other with the power transmission direction of the output shaft.
Further, the input shaft may be contained within first planetary gearsets, second row with the output shaft
The same side of star gear train, the third planet gear train and the fourth planet gear train, the power transmission of the input shaft
Direction and the power transmission direction of the output shaft are mutually perpendicular to.
Further, the 3rd clutch is arranged between the 3rd sun gear and the third line carrier, or institute
State between the 3rd sun gear and the 3rd gear ring, or between the 3rd gear ring and the third line carrier.
Further, first planetary gearsets, second planetary gearsets, the third planet gear train and institute
Fourth planet gear train is stated to lay successively.
Further, the first clutch and the second clutch be arranged at first planetary gearsets with it is described
Between second planetary gearsets, the 3rd clutch, the 4th clutch, the 5th clutch and the 6th clutch
Device is arranged between second planetary gearsets and the third planet gear train.
Further, when the automatic transmission is located at a gear, the first clutch, the second clutch and described
5th clutch is in closure state；When the automatic transmission is located at two gears, the first clutch, the second clutch
And the 3rd clutch is in closure state；When the automatic transmission is located at three gears, the first clutch, the described 3rd
Clutch and the 5th clutch are in closure state；When the automatic transmission is located at four gears, the first clutch, institute
State the 3rd clutch and the 4th clutch is in closure state；The automatic transmission be in five gear when, described first from
Clutch, the 4th clutch and the 5th clutch are in closure state；It is described when the automatic transmission is located at six gears
First clutch, the 5th clutch and the 6th clutch are in closure state；The automatic transmission is located at seven gears
When, the 4th clutch, the 5th clutch and the 6th clutch are in closure state；The automatic transmission position
When eight keep off, the second clutch, the 5th clutch and the 6th clutch are in closure state；It is described from
When dynamic speed changer is located at nine gears, the second clutch, the 4th clutch and the 5th clutch are in closure state；
When the automatic transmission is located at ten gears, the second clutch, the 4th clutch and the 6th clutch are in and closed
Conjunction state；The automatic transmission is located at when reversing gear, the first clutch, the second clutch and the 6th clutch
In closure state.
The utility model additionally provides a kind of vehicle, and the vehicle includes automatic transmission provided by the utility model.
In summary, the utility model makes this practicality new by four planetary gearsets, the Reasonable Arrangement of six clutches
The automatic transmission that type is provided is reversed gear with ten forward gears and one, and passes through the control of three clutches, you can ensureing should
The transmission of power under gear, on the premise of its transmission efficiency and planet wheel speed is ensured, by making the first gear ring directly fix
In on casing and without using brake, on the one hand make the structure of automatic transmission compacter, on the other hand reduce and shifted gears
Impact of the brake to casing in journey, improves the loading conditions of casing.Comparatively, clutch is increased without using brake
Quantity, on the one hand by nested arrangement automatic transmission can be caused compacter, on the other hand can also increase clutch
Utilization rate, and disconnect shortening idle running transmission route so that reduce idle running planetary gearsets towing moment of torsion, reduce band row stirs oily damage
Consumption, improves transmission efficiency.Further, the setting of more multi-clutch can also be conducive to the later stage by increasing planetary gearsets
Or increase more operating elements so that automatic transmission has more gears, the development for being conducive to automatic transmission following.
Described above is only the general introduction of technical solutions of the utility model, in order to better understand skill of the present utility model
Art means, and being practiced according to the content of specification, and in order to allow above and other purpose of the present utility model, feature
It can be become apparent with advantage, below especially exemplified by preferred embodiment, and coordinate accompanying drawing, describe in detail as follows.
Brief description of the drawings
The structural representation for the automatic transmission that Fig. 1 provides for the utility model first embodiment.
Fig. 2 is drive path schematic diagram of the automatic transmission when one keeps off shown in Fig. 1.
Fig. 3 is drive path schematic diagram of the automatic transmission when two keep off shown in Fig. 1.
Fig. 4 is drive path schematic diagram of the automatic transmission when three keep off shown in Fig. 1.
Fig. 5 is drive path schematic diagram of the automatic transmission when four keep off shown in Fig. 1.
Fig. 6 is drive path schematic diagram of the automatic transmission when five keep off shown in Fig. 1.
Fig. 7 is drive path schematic diagram of the automatic transmission when six keep off shown in Fig. 1.
Fig. 8 is drive path schematic diagram of the automatic transmission when seven keep off shown in Fig. 1.
Fig. 9 is drive path schematic diagram of the automatic transmission when eight keep off shown in Fig. 1.
Figure 10 is drive path schematic diagram of the automatic transmission when nine keep off shown in Fig. 1.
Figure 11 is drive path schematic diagram of the automatic transmission when ten keep off shown in Fig. 1.
Figure 12 is drive path schematic diagram of the automatic transmission when reversing gear shown in Fig. 1.
The structural representation for the automatic transmission that Figure 13 provides for the utility model second embodiment.
Embodiment
Further to illustrate that the utility model is to reach technological means and effect that predetermined utility model purpose is taken,
Below in conjunction with accompanying drawing and preferred embodiment, the utility model is described in detail as follows.
The utility model provides a kind of automatic transmission and the vehicle with the automatic transmission, the automatic transmission
There are four groups of planetary gearsets, 10 forward gear gears can be achieved.The automatic transmission has 4 frees degree, without using brake,
So that casing avoids the processing of heteromorphic teeth, the manufacture difficulty of processing of casing is reduced, the bearing capacity of casing is improved, and then can be with
Make light-weight design, cause automatic transmission structure compact by the nested designs of clutch.
The structural representation for the automatic transmission that Fig. 1 provides for the utility model first embodiment, as illustrated, this practicality
The automatic transmission that new first embodiment is provided includes input shaft 11, casing 21, the first planetary gearsets 30, the second planet tooth
Wheel group 40, third planet gear train 50, fourth planet gear train 60, first clutch 71, second clutch 72, the 3rd clutch
73rd, the 4th clutch 74, the 5th clutch 75, the 6th clutch 76 and output shaft 12.
First planetary gearsets 30 include the first sun gear 31, the first planetary gear 32, the first gear ring 33 and the first planet carrier
34, the first planetary gear 32 can be rotatably supported on the first planet carrier 34 by rolling or sliding bearing, and the first planet
Wheel 32 is located between the first sun gear 31 and the first gear ring 33, and is engaged with the first sun gear 31 and the first gear ring 33.
Second planetary gearsets 40 include the second sun gear 41, the second planetary gear 42, the second gear ring 43 and the second planet carrier
44, the second planetary gear 42 can be rotatably supported on the second planet carrier 44 by rolling or sliding bearing, and the second planet
Wheel 42 is located between the second sun gear 41 and the second gear ring 43, and is engaged with the second sun gear 41 and the second gear ring 43.
Third planet gear train 50 includes the 3rd sun gear 51, the third line star-wheel 52, the 3rd gear ring 53 and the third line carrier
54, the third line star-wheel 52 can be rotatably supported in the third line carrier 54 by rolling or sliding bearing, and third planet
Wheel 52 is located between the 3rd sun gear 51 and the 3rd gear ring 53, and is engaged with the 3rd sun gear 51 and the 3rd gear ring 53.
Fourth planet gear train 60 includes the 4th sun gear 61, fourth line star-wheel 62, the 4th gear ring 63 and fourth line carrier
64, fourth line star-wheel 62 can be rotatably supported in fourth line carrier 64 by rolling or sliding bearing, and fourth planet
Wheel 62 is located between the 4th sun gear 61 and the 4th gear ring 63, and is engaged with the 4th sun gear 61 and the 4th gear ring 63.
Input shaft 11 can by spline, weld or the mode such as be integrally formed and be directly connected with the second planet carrier 44, the 4th
Planet carrier 64 can by spline, weld or the mode such as be integrally formed and be directly connected with output shaft 12, input shaft 11 is by power member
The incoming power of part, such as hydraulic moment variator is transmitted into the automatic transmission, i.e., participating in power in the second planetary gearsets 40 passes
When defeated, the second planet carrier 44 is all the time as power input element, and output shaft 12 is connected with fourth line carrier 64, inputs fluid drive
The power of device is transmitted to fourth line carrier 64 by each shift transformation, and is transmitted by fourth line carrier 64 to output shaft 12, i.e.,
Four planet carriers 64 are in automatic transmission all the time as output block.
In the present embodiment, the first planetary gearsets 30, the second planetary gearsets 40, third planet gear train 50 and the 4th
Planetary gearsets 60 are laid successively in sequence.It should be noted that above-mentioned arrangement mode is the preferred feelings of the present embodiment
Condition, in other embodiments, the first planetary gearsets 30, the second planetary gearsets 40, third planet gear train 50 and fourth line
The order of star gear train 60 can also change according to specific laying situation, but the element in each planetary gearsets is mutual
Between annexation, and the annexation between each clutch and each planetary gearsets is constant.
In the present embodiment, the output end of the input of input shaft 11 and output shaft 12 is located at four planetary gearsets respectively
Both sides, the power transmission direction of input shaft 11 is parallel to each other with the power transmission direction of output shaft 12, i.e. the automatic transmission
Can be Longitudinal, but the automatic transmission can also be (see the Figure 13) of transverse type as needed.
First gear ring 33 can by spline, weld or the mode such as be integrally formed and be directly fixed on casing 21, i.e., first
Gear ring 33 is always stationary parts, the first sun gear 31 can by spline, weld or the mode such as be integrally formed directly with second
Sun gear 41 is connected, the second gear ring 43 can by spline, weld or be integrally formed etc. mode directly with the phase of the 3rd sun gear 51
Even, the 3rd gear ring 53 can by spline, weld or the mode such as be integrally formed and be directly connected with the 4th sun gear 61.
One end of first clutch 71 is connected with one end of the first planet carrier 34 and second clutch 72, first clutch 71
The other end be connected with one end, one end of the 6th clutch 76 and the 4th gear ring 63 of the 4th clutch 74；
One end of second clutch 72 is connected with one end of first clutch 71 and the first planet carrier 34, the other end and first
The sun gear 41 of sun gear 31 and second is connected；
One end of 4th clutch 74 and one end of first clutch 71, one end of the 6th clutch 76 and the 4th gear ring 63
It is connected, the other end is connected with the second gear ring 43 and the 3rd sun gear 51；
One end of 6th clutch 76 and one end of first clutch 71, one end of the 4th clutch 74 and the 4th gear ring 63
It is connected, the other end of the 6th clutch 76 is connected with the third line carrier 54；
In the present embodiment, the 3rd clutch 73 is arranged between the sun gear 51 of the third line carrier 54 and the 3rd, may be selected
Ground makes third planet gear train 50 be rotated into being integral.
When first clutch 71 is in closure state, the first planet carrier 34 rotates together with the 4th gear ring 63；When second
When clutch 72 is in closure state, the first planetary gearsets 30 are fixed；When the 3rd clutch 73 is in closure state,
Third planet gear train 50, which is integral, to be rotated；When the 4th clutch 74 be in closure state when, the second gear ring 43 and
3rd sun gear 51 is connected with the 4th gear ring 63；When the 3rd clutch 73 and the 4th clutch 74 are in closure state, the 3rd
Planetary gearsets 50 and fourth planet gear train 60 are rotated collectively as an entirety.
One end of 5th clutch 75 is connected with the planet carrier 44 of input shaft 11 and second, the other end and the 4th sun gear 61 and
3rd gear ring 53 is connected, and the power that input shaft 11 is transmitted by the 5th clutch 75 can respectively enter the 3rd gear ring 53 and the 4th
In sun gear 61, when the 5th clutch 75 is in closure state, the second planet carrier 44, the 3rd gear ring 53 and the 4th sun gear 61
Rotate together, when third planet gear train 50 and/or fourth planet gear train 60 participate in power transmission, what input shaft 11 was inputted
Power can be as needed, by the 5th clutch 75 incoming 3rd gear ring 53 and/or the 4th sun gear 61.
In the present embodiment, first clutch 71, second clutch 72, the 3rd clutch 73, the 4th clutch the 74, the 5th
The clutch 76 of clutch 75 and the 6th can be multiple-piece wet clutch or dog clutch.
In the present embodiment, first clutch 71 and second clutch 72 are arranged at the first planetary gearsets 30 and the second row
Between star gear train 40, the 3rd clutch 73, the 4th clutch 74, the 5th clutch 75 and the 6th clutch 76 may be contained within
Between two planetary gearsets 40 and third planet gear train 50, the laying mode is conducive to the nested designs of clutch, makes automatic
The structure of speed changer is more compact.
The utility model is by the control to six clutches, and can make four planetary gearsets of interconnection has ten
Individual forward gear and one are reversed gear, and the realization of each gear is both needed to manipulate three control elements, the i.e. automatic transmission with four
The individual free degree.Table one is that, in each gear, each clutch state in which is, it is necessary to explain, when occurring black in form
During solid rim, represent that the clutch is in closure state, when form is blank, the clutch is in patent conjunction state.
Table one：The corresponding relation of each gear of automatic transmission and each operation element
(wherein：C1 represents that first clutch 71, C2 represent that second clutch 72, C3 represent that the 3rd clutch 73, C4 are represented
4th clutch 74, C5 represent that the 5th clutch 75, C6 represent that the 6th clutch 76, k1, k2, k3 and k4 are respectively four planets
Gear train characteristic parameter, its numerical value is equal to the ratio between number of teeth of corresponding gear ring and sun gear in the planetary gearsets)
Fig. 2 is drive path schematic diagram of the automatic transmission when one keeps off shown in Fig. 1, as shown in figure 1, when this practicality is new
When the automatic transmission that type is provided is in a gear, first clutch 71, the clutch 75 of second clutch 72 and the 5th are in closure
State, because second clutch 72 is in closure state, and the first gear ring 33 is connected with casing 21, therefore, the first planetary gear
Group 30 is stationary parts, because first clutch 71 is in closure state, therefore, and the 4th gear ring 63 is stationary parts, due to the
Five clutches 75 are in closure state, and the power that input shaft 11 is inputted can be transmitted to the 4th sun gear by the 5th clutch 75
61, the power transmission route of the gear is as shown in black lines thicker in Fig. 2, and its gearratio is：
I1=K4+1.
The power transmission route of the gear is：Input shaft 11 → 61 → the fourth planet of sun gear of the 5th clutch the 75 → the 4th
Take turns 62 → fourth line carrier, 64 → output shaft 12.
Fig. 3 is drive path schematic diagram of the automatic transmission when two keep off shown in Fig. 1, as shown in Fig. 2 when this practicality is new
When the automatic transmission that type is provided is in two gears, first clutch 71, the clutch 73 of second clutch 72 and the 3rd are in closure
State, because first clutch 71 and second clutch 72 are in closure state, therefore the first planetary gearsets 30, second sun
The gear ring 63 of wheel 41 and the 4th is stationary parts, because the 3rd clutch 73 is in closure state, therefore the 3rd sun gear 51 and the
Three planet carriers 54 are connected, therefore third planet gear train 50 is rotated as an entirety, and the power transmission route of the gear is such as
In Fig. 3 shown in thicker black lines, and the gearratio of the automatic transmission is：
I2=(K4+1) * K2/ (1+K2).
The power transmission route of the gear is：The gear ring of 11 → the second planet carrier of input shaft, 44 → the second planetary gear 42 → the second
43 → third planet gear train 50 → the 4th, 64 → output shaft of sun gear 61 → fourth line star-wheel 62 → fourth line carrier 12.
Fig. 4 be Fig. 1 shown in automatic transmission three keep off when drive path schematic diagram, when the utility model provide from
When dynamic speed changer is in three gears, first clutch 71, the 3rd clutch 73 and the 5th clutch 75 are in closure state, due to the
Three clutches 73 and the 5th clutch 75 are in closure state, therefore the second planetary gearsets 40 and third planet gear train 50 are made
It is integral and is rotated.Because first clutch 71 is in closure state, therefore, the 4th gear ring 63 is with the first planet carrier 34 1
With rotation, therefore in this gear, power transmission route has thicker black line in two, the power transmission route such as Fig. 4 of the gear
Shown in bar, the gearratio of the gear is：
I3=(K1+1) * (K4+1)/(1+K1+K4).
The power transmission route of the gear is：1. the planetary gearsets 40 of input shaft 11 → the second and third planet gear train 50
→ the four 64 → output shaft of sun gear 61 → fourth line star-wheel 62 → fourth line carrier 12.
2. the planetary gearsets 40 of input shaft 11 → the second and the 31 → the first row of sun gear of third planet gear train 50 → the first
Gear ring 63 → fourth line, 62 → fourth line of the star-wheel carrier 64 of 32 → the first 34 → first clutch of planet carrier of star-wheel the 71 → the 4th →
Output shaft 12.
Fig. 5 be Fig. 1 shown in automatic transmission four keep off when drive path schematic diagram, when the utility model provide from
When dynamic speed changer is in four gears, first clutch 71, the 3rd clutch 73 and the 4th clutch 74 are in closure state, due to the
Three clutches 73 and the 4th clutch 74 are in closure state, therefore, third planet gear train 50 and fourth planet gear train 60
It is integral and is rotated, because the clutch 74 of first clutch 71 and the 4th is in closure state, therefore the first planet carrier 34
As third planet gear train 50 and fourth planet gear train 60 rotate together, because the first gear ring 33 is stationary parts, therefore
Power enters the first planetary gearsets 30 by the first planet carrier 34, and when reaching the second sun gear 41 by the first sun gear 31, the
One sun gear 31 and the second sun gear 41 can produce reverse push action to third planet gear train 50 and fourth planet gear train 60
With.The power transmission route of the gear is as shown in black lines thicker in Fig. 5, and the gearratio of the gear is：
I4=(K1+K2+1)/(1+K2).
The power transmission route of the gear is：The gear ring of 11 → the second planet carrier of input shaft, 44 → the second planetary gear 42 → the second
43 → third planet gear train 50 and 64 → output shaft of fourth planet gear train 60 → fourth line carrier 12.
Wherein, power by 44 → the second planetary gear of the second planet carrier 42 → the second, 43 → third planet of gear ring gear train 50 and
The sun gear 31 → the of 34 → the first planetary gear of fourth planet gear train 60 → first clutch, 71 → the first planet carrier 32 → the first
The planetary gear 42 of two sun gear 41 → the second reaches the second gear ring 43, is that third planet gear train 50 and fourth planet gear train 60 are carried
For reverse impetus.
Fig. 6 be Fig. 1 shown in automatic transmission five keep off when drive path schematic diagram, when the utility model provide from
When dynamic speed changer is in five gears, first clutch 71, the 4th clutch 74 and the 5th clutch 75 are in closure state, such as Fig. 6
In shown in thicker black lines, the power transmission route of the gear has three, and the gearratio of automatic transmission is during the gear：
I5=(K1+K2+1) * (K4+1)/((K2+1) * (K4+1)+K1).
The power transmission route of the gear is：1. input shaft 11 → 61 → fourth line of sun gear of the 5th clutch the 75 → the 4th
64 → output shaft of star-wheel 62 → fourth line carrier 12.
2. the 43 → the four clutch 74 → the of gear ring of 11 → the second planet carrier of input shaft, 44 → the second planetary gear 42 → the second
Four 64 → output shafts of gear ring 63 → fourth line star-wheel 62 → fourth line carrier 12.
3. the sun gear 31 of 11 → the second planet carrier of input shaft, 44 → the second planetary gear, 42 → the second sun gear 41 → the first →
Gear ring 63 → fourth line, the 62 → fourth planet of star-wheel of first planetary gear, 32 → the first 34 → first clutch of planet carrier the 71 → the 4th
64 → output shaft of frame 12.
Fig. 7 be Fig. 1 shown in automatic transmission six keep off when drive path schematic diagram, when the utility model provide from
When dynamic speed changer is in six gears, first clutch 71, the 5th clutch 75 and the 6th clutch 76 are in closure state, the gear
With three power transmission routes, the power transmission route of the gear is as shown in black lines thicker in Fig. 6, the fluid drive
The gearratio of device is：
I6=(K2* (K3+1)+K1+1) * (K4+1))/((K4+1) * (K2* (K3+1)+1)+1).
Its power transmission route is：1. input shaft 11 → 61 → fourth line of sun gear star-wheel 62 of the 5th clutch the 75 → the 4th
64 → output shaft of → fourth line carrier 12.
2. clutch the 75 → the three gear ring 53 → the third line, 52 → the third line of the star-wheel carrier 54 → the of input shaft 11 → the 5th
Six clutch the 76 → the 4th, 64 → output shaft of gear ring 63 → fourth line star-wheel 62 → fourth line carrier 12.
3. the sun gear 31 of 11 → the second planet carrier of input shaft, 44 → the second planetary gear, 42 → the second sun gear 41 → the first →
Gear ring 63 → fourth line, the 62 → fourth planet of star-wheel of first planetary gear, 32 → the first 34 → first clutch of planet carrier the 71 → the 4th
64 → output shaft of frame 12.
It is to be appreciated that in this gear, there is opposite movement tendency between the second gear ring 43 and the 3rd sun gear 51,
Therefore, it can have positive impetus to Article 2 power transmission route and Article 3 power transmission route.
Fig. 8 be Fig. 1 shown in automatic transmission seven keep off when drive path schematic diagram, when the utility model provide from
When dynamic speed changer is located at seven gears, the 4th clutch 74, the 5th clutch 75 and the 6th clutch 76 are in closure state, due to the
Four clutches 74, the 5th clutch 75 and the 6th clutch 76 are in closure state, the second planetary gearsets 40, third planet tooth
Wheel group 50 and fourth planet gear train 60 are rotated as an entirety, therefore, and the gear is direct gear, the transmission of the gear
Than for 1, the power transmission route of the gear is as shown in thicker black lines in Fig. 8.
Its power transmission route is：The planetary gearsets 40 of input shaft 11 → the second, third planet gear train 50 and fourth line
60 → output shaft of star gear train 12.
Fig. 9 be Fig. 1 shown in automatic transmission eight keep off when drive path schematic diagram, when the utility model provide from
When dynamic speed changer is in eight gears, second clutch 72, the 5th clutch 75 and the 6th clutch 76 are in closure state.Due to
Two clutches 72 are in closure state, therefore the second sun gear 41 and the first planetary gearsets 30 are stationary parts, the gear
Power transmission route has three, and the power transmission route of the gear becomes automatically as shown in thicker black lines in Fig. 9 under the gear
The gearratio of fast device is：
I8=(K2* (1+K3) * (1+K4))/(K2* (1+K3) * (1+K4)+K4).
The power transmission route of the gear is：1. input shaft 11 → 61 → fourth line of sun gear of the 5th clutch the 75 → the 4th
64 → output shaft of star-wheel 62 → fourth line carrier 12.
2. clutch the 75 → the three gear ring 53 → the third line, 52 → the third line of the star-wheel carrier 54 → the of input shaft 11 → the 5th
Six clutch the 76 → the 4th, 64 → output shaft of gear ring 63 → fourth line star-wheel 62 → fourth line carrier 12.
3. the 43 → the three sun gear 51 → the of gear ring of 11 → the second planet carrier of input shaft, 44 → the second planetary gear 42 → the second
Gear ring 63 → fourth line star-wheel 62 → fourth line the carrier of three the 54 → the 6th clutch of 52 → the third line of planetary gear carrier the 76 → the 4th
64 → output shaft 12.
Figure 10 is drive path schematic diagram of the automatic transmission when nine keep off shown in Fig. 1, is provided when the utility model
When automatic transmission is in nine gears, second clutch 72, the 4th clutch 74 and the 5th clutch 75 are in closure state, due to
Second clutch 72 is in closure state, and the second sun gear 41 and the first planetary gearsets 30 are to have under stationary parts, the gear
Two power transmission routes, as shown in Figure 10, its gearratio is the power transmission route of the gear：
I9=K2* (1+K4)/(K2* (1+K4)+K4).
The power transmission route of the gear is：1. input shaft 11 → 61 → fourth line of sun gear of the 5th clutch the 75 → the 4th
64 → output shaft of star-wheel 62 → fourth line carrier 12.
2. the 43 → the four clutch 74 → the of gear ring of 11 → the second planet carrier of input shaft, 44 → the second planetary gear 42 → the second
Four 64 → output shafts of gear ring 63 → fourth line star-wheel 62 → fourth line carrier 12.
Figure 11 is drive path schematic diagram of the automatic transmission when ten keep off shown in Fig. 1, is provided when the utility model
When automatic transmission is in ten gears, second clutch 72, the 4th clutch 74 and the 6th clutch 76 are in closure state, second
Clutch 72 is in closure state, and it is stationary parts, the 4th clutch 74 to make the second sun gear 41 and the first planetary gearsets 30
And the 6th clutch 76 be in closure state, make third planet gear train 50 and fourth planet gear train 60 into being integral progress
Revolution.The power transmission route of the gear is as shown in thicker black lines in Figure 11, and the gearratio of the gear is：
I10=K2/ (1+K2).
Its power transmission route is：The gear ring 43 → the of 11 → the second planet carrier of input shaft, 44 → the second planetary gear 42 → the second
Three planetary gearsets 50 and 60 → output shaft of fourth planet gear train 12.
Figure 12 is drive path schematic diagram of the automatic transmission when reversing gear shown in Fig. 1, is provided when the utility model
Automatic transmission is in when reversing gear, and first clutch 71, the clutch 76 of second clutch 72 and the 6th are in closure state, first
Planetary gearsets 30, the second sun gear 41, the gear ring 63 of the third line carrier 54 and the 4th are stationary parts, and the power of the gear is passed
Defeated route is as shown in thicker black lines in Figure 12, and the gearratio of the gear is：
IR=-K2*K3* (1+K4)/(1+K2).
The power transmission route of the gear is：The gear ring of 11 → the second planet carrier of input shaft, 44 → the second planetary gear 42 → the second
43 → the 3rd the 52 → the 3rd gear ring of 51 → the third line of sun gear star-wheel the 53 → the 4th, 61 → fourth line of sun gear star-wheel the 62 → the 4th
64 → output shaft of planet carrier 12.
It is to be appreciated that from the power transmission route of above-mentioned each gear, the acting as of the 3rd clutch 73 may be selected
Ground makes third planet gear train 50 be rotated as an entirety, therefore the position of the 3rd clutch 73 is not limited to first in fact
The situation shown in example is applied, the 3rd clutch 73 can also be arranged between the 3rd gear ring 53 and the third line carrier 54, or the 3rd
51 between the sun gear of gear ring 53 and the 3rd.
The utility model makes what the utility model was provided by four planetary gearsets, the Reasonable Arrangement of six clutches
Automatic transmission is reversed gear with ten forward gears and one, and passes through the control of three clutches, you can ensure to move under the gear
The transmission of power, on the premise of its transmission efficiency and planet wheel speed is ensured, by making the first gear ring 33 be directly fixed on casing
On 21 and without using brake, on the one hand make the structure of automatic transmission compacter, on the other hand reduce in shift process
Impact of the brake to casing 21, improves the loading conditions of casing 21.Comparatively, clutch is increased without using brake
Quantity, on the one hand by nested arrangement automatic transmission can be caused compacter, on the other hand can also increase clutch
Utilization rate, and disconnect shortening idle running transmission route so that reduce idle running planetary gearsets towing moment of torsion, reduce band row stirs oily damage
Consumption, improves transmission efficiency.Further, the setting of more multi-clutch can also be conducive to the later stage by increasing planetary gearsets
Or increasing more operating elements so that automatic transmission has more gears, the multi-speed for being conducive to automatic transmission following is opened up
Exhibition.
The structural representation for the automatic transmission that Figure 13 provides for the utility model 3rd embodiment, as shown in figure 13, this
The automatic transmission that is there is provided of 3rd embodiment that utility model is provided with it is essentially identical in embodiment one, its difference exists
In input shaft 11 is laid in the first row star gear train 30, the second planetary gearsets 40, third planet gear train with output shaft 12
50 and the same side of fourth planet gear train 60, the power transmission direction of input shaft 11 and the power transmission direction phase of output shaft 12
Mutually vertical, i.e., in the present embodiment, automatic transmission can be transverse type.
In summary, the utility model makes this practicality new by four planetary gearsets, the Reasonable Arrangement of six clutches
The automatic transmission that type is provided is reversed gear with ten forward gears and one, and passes through the control of three clutches, you can ensureing should
The transmission of power under gear, on the premise of its transmission efficiency and planet wheel speed is ensured, by making the first gear ring directly fix
In on casing and without using brake, on the one hand make the structure of automatic transmission compacter, on the other hand reduce and shifted gears
Impact of the brake to casing in journey, improves the loading conditions of casing.Comparatively, clutch is increased without using brake
Quantity, on the one hand by nested arrangement automatic transmission can be caused compacter, on the other hand can also increase clutch
Utilization rate, and disconnect shortening idle running transmission route so that reduce idle running planetary gearsets towing moment of torsion, reduce band row stirs oily damage
Consumption, improves transmission efficiency.Further, the setting of more multi-clutch can also be conducive to the later stage by increasing planetary gearsets
Or increase more operating elements so that automatic transmission has more gears, the development for being conducive to automatic transmission following.
The utility model additionally provides a kind of vehicle, and the vehicle includes above-mentioned automatic transmission, on its of the vehicle
He may refer to prior art at structure, will not be repeated here.
It is described above, only it is preferred embodiment of the present utility model, not makees any formal to the utility model
Limitation, although the utility model is disclosed above with preferred embodiment, but is not limited to the utility model, any ripe
Professional and technical personnel is known, is not being departed from the range of technical solutions of the utility model, when in the technology using the disclosure above
Hold the equivalent embodiment made a little change or be modified to equivalent variations, as long as being without departing from technical solutions of the utility model
Hold, any simple modification, equivalent variations and the modification made according to technical spirit of the present utility model to above example, still
Belong in the range of technical solutions of the utility model.
Claims (8)
1. a kind of automatic transmission, it is characterised in that：Including input shaft, casing, the first planetary gearsets, the second planetary gear
Group, third planet gear train, fourth planet gear train, first clutch, second clutch, the 3rd clutch, the 4th clutch,
5th clutch, the 6th clutch and output shaft；
First planetary gearsets include the first sun gear, the first planetary gear, the first gear ring and the first planet carrier, described first
Planetary gear is rotatably supported on first planet carrier, and first planetary gear is located at first sun gear and first
Between gear ring, and engaged with first sun gear and first gear ring；
Second planetary gearsets include the second sun gear, the second planetary gear, the second gear ring and the second planet carrier, described second
Planetary gear is rotatably supported on second planet carrier, and second planetary gear is located at second sun gear and second
Between gear ring, and engaged with second sun gear and second gear ring；
The third planet gear train includes the 3rd sun gear, the third line star-wheel, the 3rd gear ring and the third line carrier, the described 3rd
Planetary gear is rotatably supported in the third line carrier, and the third line star-wheel is located at the 3rd sun gear and the 3rd
Between gear ring, and engaged with the 3rd sun gear and the 3rd gear ring；
The fourth planet gear train includes the 4th sun gear, fourth line star-wheel, the 4th gear ring and fourth line carrier, the described 4th
Planetary gear is rotatably supported in the fourth line carrier, and the fourth line star-wheel is located at the 4th sun gear and the 4th
Between gear ring, and engaged with the 4th sun gear and the 4th gear ring；
The input shaft is connected with second planet carrier, and the output shaft is connected with the fourth line carrier, first tooth
Circle is fixed on the casing, and first sun gear is connected with second sun gear, second gear ring and the described 3rd
Sun gear is connected, and the 3rd gear ring is connected with the 4th sun gear；
One end of the first clutch is connected with one end of first planet carrier and the second clutch, described first from
The other end of clutch is connected with one end, one end of the 6th clutch and the 4th gear ring of the 4th clutch；
One end of the second clutch is connected with one end of the first clutch and first planet carrier, described second from
The other end of clutch is connected with first sun gear and second sun gear；
One end of 4th clutch and one end, one end of the 6th clutch and the 4th gear ring phase of the first clutch
Even, the other end of the 4th clutch is connected with second gear ring and the 3rd sun gear；
One end of 5th clutch is connected with the input shaft and second planet carrier, the 5th clutch it is another
End is connected with the 3rd gear ring and the 4th sun gear；
One end of 6th clutch and one end of the first clutch, one end and the described 4th of the 4th clutch
Gear ring is connected, and the other end of the 6th clutch is connected with the third line carrier；
3rd clutch is selectively integral the third planet gear train to be rotated.
2. automatic transmission according to claim 1, it is characterised in that：The input of the input shaft and the output shaft
Output end be respectively arranged at first planetary gearsets, second planetary gearsets, the third planet gear train and
The both sides of the fourth planet gear train, the power transmission direction of the input shaft and the power transmission direction phase of the output shaft
It is mutually parallel.
3. automatic transmission according to claim 1, it is characterised in that：The input shaft may be contained within the output shaft
First planetary gearsets, second planetary gearsets, the third planet gear train and the fourth planet gear train
The same side, the power transmission direction of the input shaft is mutually perpendicular to the power transmission direction of the output shaft.
4. automatic transmission according to claim 1, it is characterised in that：3rd clutch is arranged at the described 3rd too
Between sun wheel and the third line carrier, or between the 3rd sun gear and the 3rd gear ring, or the 3rd gear ring with
Between the third line carrier.
5. automatic transmission according to claim 1, it is characterised in that：First planetary gearsets, second row
Star gear train, the third planet gear train and the fourth planet gear train are laid successively.
6. automatic transmission according to claim 4, it is characterised in that：The first clutch and the second clutch
It is arranged between first planetary gearsets and second planetary gearsets, the 3rd clutch, the 4th clutch
Device, the 5th clutch and the 6th clutch are arranged at second planetary gearsets and the third planet gear train
Between.
7. automatic transmission according to claim 1, it is characterised in that：It is described when the automatic transmission is located at a gear
First clutch, the second clutch and the 5th clutch are in closure state；The automatic transmission is located at two gears
When, the first clutch, the second clutch and the 3rd clutch are in closure state；The automatic transmission position
When three keep off, the first clutch, the 3rd clutch and the 5th clutch are in closure state；The automatic change
When fast device is located at four gears, the first clutch, the 3rd clutch and the 4th clutch are in closure state；It is described
When automatic transmission is in five gears, the first clutch, the 4th clutch and the 5th clutch are in closed form
State；When the automatic transmission is located at six gears, the first clutch, the 5th clutch and the 6th clutch are in
Closure state；When the automatic transmission is located at seven gears, the 4th clutch, the 5th clutch and the 6th clutch
Device is in closure state；When the automatic transmission is located at eight gears, the second clutch, the 5th clutch and described the
Six clutches are in closure state；The automatic transmission be located at nine gear when, the second clutch, the 4th clutch and
5th clutch is in closure state；The automatic transmission be located at ten gear when, the second clutch, the described 4th from
Clutch and the 6th clutch are in closure state；The automatic transmission is located at when reversing gear, the first clutch, described
Second clutch and the 6th clutch are in closure state.
8. a kind of vehicle, it is characterised in that：Including automatic transmission as claimed in any of claims 1 to 7 in one of claims.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720107581.8U CN206571918U (en) | 2017-01-27 | 2017-01-27 | automatic transmission and vehicle |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201720107581.8U CN206571918U (en) | 2017-01-27 | 2017-01-27 | automatic transmission and vehicle |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN206571918U true CN206571918U (en) | 2017-10-20 |
Family
ID=60061687
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201720107581.8U Withdrawn - After Issue CN206571918U (en) | 2017-01-27 | 2017-01-27 | automatic transmission and vehicle |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN206571918U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106594201A (en) * | 2017-01-27 | 2017-04-26 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
-
2017
- 2017-01-27 CN CN201720107581.8U patent/CN206571918U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| 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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