CN114001132A - Nine-gear automatic transmission with small step ratio - Google Patents

Nine-gear automatic transmission with small step ratio Download PDF

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Publication number
CN114001132A
CN114001132A CN202111245919.3A CN202111245919A CN114001132A CN 114001132 A CN114001132 A CN 114001132A CN 202111245919 A CN202111245919 A CN 202111245919A CN 114001132 A CN114001132 A CN 114001132A
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CN
China
Prior art keywords
planetary gear
clutch
brake
gear
input shaft
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Pending
Application number
CN202111245919.3A
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Chinese (zh)
Inventor
丁华锋
何林
张铭进
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China University of Geosciences
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China University of Geosciences
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Publication date
Application filed by China University of Geosciences filed Critical China University of Geosciences
Priority to CN202111245919.3A priority Critical patent/CN114001132A/en
Publication of CN114001132A publication Critical patent/CN114001132A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine 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

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention provides a nine-gear automatic transmission with a small step ratio, which comprises a transmission shell, an input shaft, an output shaft, a planetary gear row set and a torque transmission device, wherein the input shaft, the output shaft, the planetary gear row set and the torque transmission device are arranged in the transmission shell; the torque transmitting devices connect an input shaft and one of the planetary gear sets, and three combinations of the clutches and brakes of the torque transmitting devices are selectively engageable to establish nine forward speed ratios and one reverse speed ratio between the input shaft and the output shaft. The invention has the beneficial effects that: the four planet rows have compact structure, small volume and light weight. The step ratio among all gears of the transmission is small, and the speed ratio range also meets the requirements of the transmission.

Description

Nine-gear automatic transmission with small step ratio
Technical Field
The invention relates to the technical field of vehicle transmission, in particular to a nine-gear automatic transmission with a small step ratio.
Background
Automatic transmissions occupy the major automobile market today, and are applied to the current automobiles to a great extent, and as one of the most important systems in automobiles, the design of the transmission structure of the automatic transmission is a hot spot in automobile research at home and abroad. At present, the number of gears of an automatic transmission on the market is mostly between four and eight, only a few vehicles use the automatic transmission with nine gears, generally, the more the gears of the automatic transmission are, the more smooth the gear shifting is, the impact caused by gear shifting is greatly reduced, and certain oil consumption can be reduced. Multi-speed automatic transmissions will be a future development trend for transmissions.
At present, the automatic transmission with the largest number of gears in the market is a nine-gear automatic transmission, but the automatic transmission has the problems that the number of control elements is relatively large, and the aspect of gear shifting control of the transmission is slightly complex.
Disclosure of Invention
In view of the above, in order to meet the requirement that the optimization requirement degree of automobile design and manufacture gradually increases, the embodiment of the invention provides a nine-gear automatic transmission with a small step ratio.
An embodiment of the present invention provides a nine speed automatic transmission having a small step ratio, including:
a transmission housing;
and an input shaft, an output shaft, a planetary gear set and a torque transmission device which are arranged in the transmission shell,
the planetary gear row set comprises four planetary gear rows which are sequentially arranged along the direction from the input shaft to the output shaft, the four planetary gear rows are respectively a first planetary gear row, a second planetary gear row, a third planetary gear row and a fourth planetary gear row, each planetary gear row comprises a sun gear, a planet carrier, a planet gear and a gear ring, wherein the planet carrier of the first planetary gear row is connected with the ring gear of the second planetary gear row, the sun gear of the first planetary gear row is connected with the planet carrier of the second planetary gear row, the planet carrier of the second planetary gear row is connected with the ring gear of the third planetary gear row, the planet carrier of the third planetary gear row is connected with the ring gear of the fourth planetary gear row, the sun gear of the third planetary gear row is connected with the sun gear of the fourth planetary gear row, and the planet carrier of the fourth planetary gear row is connected with the output shaft;
the torque transmitting device includes:
a first clutch connecting the input shaft and the ring gear of the first planetary gear row;
a second clutch connecting the input shaft and the carrier of the first planetary gear row;
a third clutch connecting the input shaft and the carrier of the third planetary gear row;
a first brake connected to the sun gear of the second planetary gear row;
a second brake connected to the ring gear of the second planetary gear row;
and a third brake connecting the sun gear of the third planetary gear row and the sun gear of the fourth planetary gear row;
wherein three combinations of each said clutch and each said brake are selectively engageable to establish nine forward speed ratios and one reverse speed ratio between said input shaft and said output shaft.
Further, the nine forward gear ratios are four reduction gears, one direct gear and four overdrive gears respectively.
Further, a first gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the first brake, and the third brake;
establishing a second gear ratio between the input shaft and the output shaft by engaging the second clutch, the first brake, and the third brake;
establishing a third gear ratio between the input shaft and the output shaft by engaging the first clutch, the second clutch, and the third brake;
establishing a fourth gear ratio between the input shaft and the output shaft by engaging the first clutch, the third clutch, and the third brake;
establishing a fifth gear ratio between the input shaft and the output shaft by engaging the first clutch, the second clutch, and the third clutch;
establishing a sixth gear ratio between the input shaft and the output shaft by engaging the second clutch, the first brake, and the third clutch;
establishing a seven speed gear ratio between the input shaft and the output shaft by engaging the first clutch, the first brake, and the third clutch;
establishing an eight speed gear ratio between the input shaft and the output shaft by engaging the second brake, the first brake, and the third clutch;
a nine speed gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the second brake, and the third clutch.
Further, a reverse gear ratio is established between the input shaft and the output shaft by engaging the third brake, the second brake, and the first clutch.
Further, the first clutch, the second clutch, and the third clutch are multi-plate wet clutches or dog clutches.
Further, the first brake, the second brake, and the third brake are drum brakes or multi-plate wet brakes.
Further, the first brake, the second brake, and the third brake are all fixed to the transmission housing.
The technical scheme provided by the embodiment of the invention has the following beneficial effects:
1. the novel nine-gear transmission designed by the invention adopts a planetary gear mechanism for transmission, four planetary rows in the structure have the characteristics of small internal structure volume and simple and compact structure, and a mature manufacturing process method is selected by adopting the common Ravigneaux mechanism to be connected with other planetary rows.
2. The number of components for transmitting the torque is small, and the nine-gear transmission adopts six torque transmission components, so that the effects of reducing the control difficulty and the corresponding volume of the transmission can be achieved.
3. The control of each gear only needs to combine three control element clutches or brakes, and only needs to replace the combination and disconnection of a pair of torque transmission members when the adjacent gears are changed, so that the control is simple.
Drawings
FIG. 1 is a schematic illustration of a small step ratio nine speed automatic transmission of the present invention;
FIG. 2 is a logic diagram illustrating the operation of a nine speed automatic transmission having a small step ratio in accordance with the present invention.
In the figure: 1-input shaft, 2-output shaft, 11/21/31/41-gear ring, 12/22/32/42-planetary gear, 13/23/33/43-planetary gear carrier, 14/24/34/44-sun gear, B1-first brake, B2-second brake, B3-third brake, C1-first clutch, C2-second clutch and C3-third clutch.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be further described with reference to the accompanying drawings. The following presents a simplified summary of the invention in order to provide a basic understanding of the invention and to provide a basic understanding of the invention.
In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted" and "connected" are to be interpreted broadly, e.g., as being either fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Referring to FIG. 1, an embodiment of the present invention provides a nine speed automatic transmission with a small step ratio comprising a transmission housing; and an input shaft 1, an output shaft 2, a planetary gear set and a torque transmitting device mounted inside the transmission housing.
The planetary gear row set comprises four planetary gear rows which are sequentially arranged along the direction from the input shaft 1 to the output shaft 2, and the four planetary gear rows are a first planetary gear row, a second planetary gear row, a third planetary gear row and a fourth planetary gear row respectively.
Each planetary gear row comprises a sun gear, a planet carrier, a planet gear and a gear ring. Specifically, the method comprises the following steps:
the sun gear 14 of the first planetary gear set is in external gearing with the planet gears 12 of the first planetary gear set, the planet gears 12 of the first planetary gear set are in internal gearing with the ring gear 11 of the first planetary gear set, and the planet gears 12 of the first planetary gear set are rotatably supported on the planet carrier 13 of the first planetary gear set.
The sun gear 24 of the second planetary gear set is in external gearing with the planet gears 22 of the second planetary gear set, the planet gears 22 of the second planetary gear set are in internal gearing with the ring gear 21 of the second planetary gear set, and the planet gears 22 of the second planetary gear set are rotatably supported on the planet carrier 23 of the second planetary gear set.
The sun gear 34 of the third planetary gear set is in external gearing with the planetary gears 32 of the third planetary gear set, the planetary gears 32 of the third planetary gear set are in internal gearing with the ring gear 31 of the third planetary gear set, and the planetary gears 32 of the third planetary gear set are rotatably supported on the planet carrier 33 of the third planetary gear set.
The sun gear 44 of the fourth planetary gear set is in external gearing with the planetary gears 42 of the fourth planetary gear set, the planetary gears 42 of the fourth planetary gear set are in internal gearing with the ring gear 41 of the fourth planetary gear set, and the planetary gears 42 of the fourth planetary gear set are rotatably supported on the planet carrier 43 of the fourth planetary gear set.
Wherein the planet carrier 13 of the first planetary gear set is connected to the ring gear 21 of the second planetary gear set, the sun gear 14 of the first planetary gear set is connected to the planet carrier 23 of the second planetary gear set, the planet carrier 23 of the second planetary gear set is connected to the ring gear 31 of the third planetary gear set, the planet carrier 33 of the third planetary gear set is connected to the ring gear 41 of the fourth planetary gear set, the sun gear 34 of the third planetary gear set is connected to the sun gear 44 of the fourth planetary gear set, and the planet carrier 43 of the fourth planetary gear set is connected to the output shaft 2.
The torque transmission device comprises three clutches and three brakes, the clutches are multi-plate wet clutches or jaw clutches, and the brakes are drum brakes or multi-plate wet brakes. The three clutches are a first clutch C1, a second clutch C2 and a third clutch C3 respectively, and the three brakes are a first brake B1, a second brake B2 and a third brake B3.
Wherein the first clutch C1 connects the input shaft 1 and the ring gear 11 of the first planetary gear set;
the second clutch C2 connects the input shaft 1 and the carrier 13 of the first planetary gear set;
the third clutch C3 connects the input shaft 1 with the carrier 33 of the third planetary gear set.
The first brake B1, the second brake B2 and the third brake B3 are all fixed to the transmission housing, and,
the first brake B1 is connected to the sun gear 24 of the second planetary gear row;
the second brake B2 is connected to the ring gear 21 of the second planetary gear set;
the third brake B3 connects the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row.
Each of the clutches C1, C2, C3 and each of the brakes B1, B2, B3 are selectively engageable in combinations of three to establish nine forward speed ratios and one reverse speed ratio between the input shaft 1 and the output shaft 2. The nine forward gears respectively comprise four speed reduction gears, a direct gear and four overdrive gears.
Referring to the operating logic table shown in FIG. 2, the transmission is embodied as follows:
a first gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the first clutch C1, the first brake B1 and the third brake B3. Specifically, the first brake B1 and the third brake B3 are engaged to connect the sun gear 24 of the second planetary gear row, the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row, respectively, with the transmission housing, preventing rotation of the sun gear 24 of the second planetary gear row, the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row relative to the transmission housing. The first clutch C1 is engaged to connect the input shaft 1 and the ring gear 11 of the first planetary gear set for rotation together. Thereby, a first gear ratio is established between the input shaft 1 and the output shaft 2.
A two-gear transmission ratio is established between the input shaft 1 and the output shaft 2 by engaging the second clutch C2, the first brake B1, and the third brake B3. Specifically, the first brake B1 and the third brake B3 are engaged to connect the sun gear 24 of the second planetary gear row, the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row, respectively, with the transmission housing, preventing rotation of the sun gear 24 of the second planetary gear row, the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row relative to the transmission housing. The second clutch C2 is engaged to connect the input shaft 1 and the ring gear 21 of the second planetary gear set for rotation together. A transmission ratio of two gears is thereby established between the input shaft 1 and the output shaft 2.
A third gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the first clutch C1, the second clutch C2 and the third brake B3. Specifically, the third brake B3 is engaged to connect the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row with the transmission housing, preventing rotation of the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row relative to the transmission housing. The first clutch C1 and the second clutch C2 are engaged such that the input shaft 1 rotates together with the ring gear 11 of the first planetary gear row and the ring gear 21 of the second planetary gear row, respectively, and the connection, whereby a gear ratio of three gears is established between the input shaft 1 and the output shaft 2.
A fourth gear transmission ratio is established between the input shaft 1 and the output shaft 2 by engaging the first clutch C1, the third clutch C3 and the third brake B3. Specifically, the third brake B3 is engaged to connect the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row with the transmission housing, preventing rotation of the sun gear 34 of the third planetary gear row and the sun gear 44 of the fourth planetary gear row relative to the transmission housing. The first clutch C1 and the third clutch C3 are engaged such that the input shaft 1 is connected for rotation with the ring gear 11 of the first planetary gear row and the ring gear 41 of the fourth planetary gear row, respectively, whereby a gear ratio of four gears is established between the input shaft 1 and the output shaft 2.
A fifth gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the first clutch C1, the second clutch C2, and the third clutch C3. Specifically, the first clutch C1, the second clutch C2 and the third clutch C3 are engaged to connect the input shaft 1 to the ring gear 11 of the first planetary gear row, the ring gear 21 of the second planetary gear row and the ring gear 41 of the fourth planetary gear row, respectively, for rotation together, thereby establishing a gear ratio of five gears, that is, a direct gear, between the input shaft 1 and the output shaft 2.
A sixth gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the second clutch C2, the first brake B1 and the third clutch B3. Specifically, the first brake B1 is engaged to connect the sun gear 24 of the second planetary gear set with the transmission housing, preventing rotation of the sun gear 24 of the second planetary gear set relative to the transmission housing. The second clutch C2 and the third clutch C3 are engaged so that the input shaft 1 is connected for rotation with the ring gear 21 of the second planetary gear row and the ring gear 41 of the fourth planetary gear row, respectively, whereby a gear ratio of six gears is established between the input shaft 1 and the output shaft 2.
A seven speed gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the first clutch C1, the first brake B1 and the third clutch C3. Specifically, the first brake B1 is engaged to connect the sun gear 24 of the second planetary gear set with the transmission housing, preventing rotation of the sun gear 24 of the second planetary gear set relative to the transmission housing. The first clutch C1 and the third clutch C3 are engaged such that the input shaft 1 is connected for rotation with the ring gear 11 of the first planetary gear row and the ring gear 41 of the fourth planetary gear row, respectively, whereby a seven-speed gear ratio is established between the input shaft 1 and the output shaft 2.
An eight speed gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the second brake B2, the first brake B1 and the third clutch C3. Specifically, the first brake B1 and the second brake B2 are engaged to connect the sun gear 24 of the second planetary gear row and the ring gear 21 of the second planetary gear row to the transmission housing, preventing rotation of the sun gear 24 of the second planetary gear row and the ring gear 21 of the second planetary gear row relative to the transmission housing. The third clutch C3 is engaged to connect the input shaft 1 and the ring gear 41 of the fourth planetary gear row for rotation together, thereby establishing a gear ratio of eight gears between the input shaft 1 and the output shaft 2.
A nine speed gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the first clutch C1, the second brake B2 and the third clutch C3. Specifically, the second brake B2 is engaged to connect the ring gear 21 of the second planetary gear set with the transmission housing, preventing rotation of the ring gear 21 of the second planetary gear set relative to the transmission housing. The first clutch C1 and the third clutch C3 are engaged such that the input shaft 1 is connected for rotation with the ring gear 11 of the first planetary gear row and the ring gear 41 of the fourth planetary gear row, respectively, whereby a gear ratio of nine gears is established between the input shaft 1 and the output shaft 2.
Further, a reverse gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the third brake B3, the second brake B2, and the first clutch C1. Specifically, the second brake B2 and the third brake B3 are engaged to connect the ring gear 21 of the second planetary gear row, the sun gear 34 of the third planetary gear row, and the sun gear 44 of the fourth planetary gear row, respectively, with the transmission housing, preventing the ring gear 21 of the second planetary gear row, the sun gear 34 of the third planetary gear row, and the sun gear 44 of the fourth planetary gear row from rotating relative to the transmission housing. The first clutch C1 is engaged to connect the input shaft 1 and the ring gear 11 of the first planetary gear set for rotation together, thereby establishing a gear ratio of reverse gear between the input shaft 1 and the output shaft 2.
In this document, the terms front, back, upper and lower are used to define the components in the drawings and the positions of the components relative to each other, and are used for clarity and convenience of the technical solution. It is to be understood that they are relative concepts that may be modified in various manners of use and placement and that the use of directional terms should not be taken to limit the scope of what is claimed.
The features of the embodiments and embodiments described herein above may be combined with each other without conflict.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.

Claims (7)

1. A small step ratio nine speed automatic transmission comprising:
a transmission housing;
and install input shaft, output shaft, planetary gear row group and the torque transmission device inside the derailleur shell, its characterized in that:
the planetary gear row set comprises four planetary gear rows which are sequentially arranged along the direction from the input shaft to the output shaft, the four planetary gear rows are respectively a first planetary gear row, a second planetary gear row, a third planetary gear row and a fourth planetary gear row, each planetary gear row comprises a sun gear, a planet carrier, a planet gear and a gear ring, wherein the planet carrier of the first planetary gear row is connected with the ring gear of the second planetary gear row, the sun gear of the first planetary gear row is connected with the planet carrier of the second planetary gear row, the planet carrier of the second planetary gear row is connected with the ring gear of the third planetary gear row, the planet carrier of the third planetary gear row is connected with the ring gear of the fourth planetary gear row, the sun gear of the third planetary gear row is connected with the sun gear of the fourth planetary gear row, and the planet carrier of the fourth planetary gear row is connected with the output shaft;
the torque transmitting device includes:
a first clutch connecting the input shaft and the ring gear of the first planetary gear row;
a second clutch connecting the input shaft and the carrier of the first planetary gear row;
a third clutch connecting the input shaft and the carrier of the third planetary gear row;
a first brake connected to the sun gear of the second planetary gear row;
a second brake connected to the ring gear of the second planetary gear row;
and a third brake connecting the sun gear of the third planetary gear row and the sun gear of the fourth planetary gear row;
wherein three combinations of each said clutch and each said brake are selectively engageable to establish nine forward speed ratios and one reverse speed ratio between said input shaft and said output shaft.
2. A small step ratio nine speed automatic transmission as set forth in claim 1 wherein: the nine forward gears respectively comprise four speed reduction gears, a direct gear and four overdrive gears.
3. A small step ratio nine speed automatic transmission as set forth in claim 2 wherein:
establishing a first gear ratio between the input shaft and the output shaft by engaging the first clutch, the first brake, and the third brake;
establishing a second gear ratio between the input shaft and the output shaft by engaging the second clutch, the first brake, and the third brake;
establishing a third gear ratio between the input shaft and the output shaft by engaging the first clutch, the second clutch, and the third brake;
establishing a fourth gear ratio between the input shaft and the output shaft by engaging the first clutch, the third clutch, and the third brake;
establishing a fifth gear ratio between the input shaft and the output shaft by engaging the first clutch, the second clutch, and the third clutch;
establishing a sixth gear ratio between the input shaft and the output shaft by engaging the second clutch, the first brake, and the third clutch;
establishing a seven speed gear ratio between the input shaft and the output shaft by engaging the first clutch, the first brake, and the third clutch;
establishing an eight speed gear ratio between the input shaft and the output shaft by engaging the second brake, the first brake, and the third clutch;
a nine speed gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the second brake, and the third clutch.
4. A small step ratio nine speed automatic transmission as set forth in claim 1 wherein:
establishing a reverse gear ratio between the input shaft and the output shaft by engaging the third brake, the second brake, and the first clutch.
5. A small step ratio nine speed automatic transmission as set forth in claim 1 wherein: the first clutch, the second clutch and the third clutch are multi-plate wet clutches or jaw clutches.
6. A small step ratio nine speed automatic transmission as set forth in claim 1 wherein: the first brake, the second brake, and the third brake are drum brakes or multi-plate wet brakes.
7. A small step ratio nine speed automatic transmission as set forth in claim 1 wherein: the first brake, the second brake and the third brake are all fixed on the transmission housing.
CN202111245919.3A 2021-10-26 2021-10-26 Nine-gear automatic transmission with small step ratio Pending CN114001132A (en)

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Application Number Priority Date Filing Date Title
CN202111245919.3A CN114001132A (en) 2021-10-26 2021-10-26 Nine-gear automatic transmission with small step ratio

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Application Number Priority Date Filing Date Title
CN202111245919.3A CN114001132A (en) 2021-10-26 2021-10-26 Nine-gear automatic transmission with small step ratio

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Publication Number Publication Date
CN114001132A true CN114001132A (en) 2022-02-01

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Citations (21)

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Application publication date: 20220201