CN112324876B - Nine-gear automatic transmission with large speed ratio range - Google Patents

Nine-gear automatic transmission with large speed ratio range Download PDF

Info

Publication number
CN112324876B
CN112324876B CN202011306640.7A CN202011306640A CN112324876B CN 112324876 B CN112324876 B CN 112324876B CN 202011306640 A CN202011306640 A CN 202011306640A CN 112324876 B CN112324876 B CN 112324876B
Authority
CN
China
Prior art keywords
gear
clutch
brake
transmission
planetary 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.)
Active
Application number
CN202011306640.7A
Other languages
Chinese (zh)
Other versions
CN112324876A (en
Inventor
丁华锋
柯涛
龚宸
杨林丛
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
China University of Geosciences
Original Assignee
China University of Geosciences
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by China University of Geosciences filed Critical China University of Geosciences
Priority to CN202011306640.7A priority Critical patent/CN112324876B/en
Publication of CN112324876A publication Critical patent/CN112324876A/en
Application granted granted Critical
Publication of CN112324876B publication Critical patent/CN112324876B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
    • 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

Landscapes

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

Abstract

The invention relates to the technical field of automobile transmission, in particular to a nine-gear automatic transmission with a large speed ratio range, which comprises a transmission shell, an input shaft, an output shaft, a planetary gear row group, a connecting component group and a torque transmission device, wherein the input shaft, the output shaft, the planetary gear row group, the connecting component group and the torque transmission device are arranged in the transmission shell, the planetary gear row group comprises a first planetary gear row, a second planetary gear row, a third planetary gear row and a fourth planetary gear row, and the fourth planetary gear row is a double planetary gear row. The torque transmitting devices include a first clutch, a second clutch, a third clutch, a first brake, a second brake, and a third brake, the first brake, the second brake, and the third brake being fixedly coupled with the transmission housing. Wherein the torque transmitting devices are selectively engageable in combinations of three to establish nine forward speed ratios and a reverse speed ratio between the input shaft and the output shaft. The nine-gear automatic transmission provided by the invention has a large speed ratio range, and the speed ratio step between the transmission ratios of all gears meets the requirements of the transmission.

Description

Nine-gear automatic transmission with large speed ratio range
Technical Field
The invention relates to the technical field of automobile transmission, in particular to a nine-gear automatic transmission with a large speed ratio range.
Background
Automatic transmissions have gradually replaced manual transmissions to occupy the main automobile market, and are widely applied to modern automobiles, and as one of the most complex assemblies on automobiles, the design of the speed changing structure of the automatic transmissions is always a hot spot pursued by the international science and technology world. At present, the number of gears of the automatic transmission on the market is mostly between 4 and 8, and only a 9-gear automatic transmission is used by a single high-grade vehicle, however, generally, the more the number of gears of the automatic transmission is, the smoother the gear shifting is, the gear shifting impact is reduced, and the oil consumption is relatively reduced. Multi-gear automatic transmissions will be a future development trend of automatic transmissions.
The automatic transmission with the largest number of gears which can be contacted in a large number in the market at present is a 9-gear automatic transmission. However, the number of 9-speed gearboxes available on the market is limited and the number of alternatives is small.
Patent CN 205383227U discloses a nine-gear automatic transmission mechanism, specifically, a four-row planetary gear train formed by combining a ravigneaux mechanism and a simpson mechanism is adopted, and nine forward gears and three reverse gears are obtained by matching with four brakes and three clutches. However, the number of control elements of the scheme is relatively large, and the gear shifting control aspect of the gearbox is slightly complicated. Patent CN 205064722U discloses a nine-gear automatic transmission, specifically, a four-row planetary gear train formed by combining two simpson mechanisms is adopted, and nine forward gears and one reverse gear are obtained by matching with three brakes and three clutches. The automatic transmissions in the above technology are all composed of four rows of planetary gear trains, clutches and brake devices, and realize a plurality of transmission ratios, and the gear shift control is complex.
As the popularity of automobiles in society increases, the demand for automatic transmission with high gear numbers increases, and therefore, it is necessary to develop a novel transmission structure of automatic transmission with high gear numbers, which has a larger transmission ratio range and a more stable step ratio.
Disclosure of Invention
In view of the above, the present invention provides a nine speed automatic transmission having a wide speed ratio range, which can reduce the size of a reduction gear and reduce the difficulty of control.
The invention provides a nine-gear automatic transmission with a large speed ratio range, which comprises a transmission shell, an input shaft, an output shaft, a planetary gear row group, a connecting member group and a torque transmission device, wherein the input shaft, the output shaft, the planetary gear row group, the connecting member group and the torque transmission device are arranged in the transmission shell, the planetary gear row group comprises a first planetary gear row, a second planetary gear row, a third planetary gear row and a fourth planetary gear row which are sequentially arranged from front to back, the torque transmission device comprises a first clutch, a second clutch, a third clutch, a first brake, a second brake and a third brake, and the first brake, the second brake and the third brake are fixedly connected with the transmission shell, wherein:
the first planetary gear row consists of a first sun gear, a first planet carrier, a first planet gear and a first gear ring, wherein the first sun gear and the first planet gear are in external engagement transmission, the first planet gear and the first gear ring are in internal engagement transmission, and the first planet gear is rotatably supported on the first planet carrier;
the second planetary gear row consists of a second sun gear, a second planet carrier, a second planet gear and a second gear ring, wherein the second sun gear and the second planet gear are in external engagement transmission, the second planet gear and the second gear ring are in internal engagement transmission, and the second planet gear is rotatably supported on the second planet carrier;
the third planetary gear row consists of a third sun gear, a third planet carrier, a third planet gear and a third gear ring, wherein the third sun gear and the third planet gear are in external meshed transmission, the third planet gear and the third gear ring are in internal meshed transmission, and the third planet gear is rotatably supported on the third planet carrier;
the fourth planetary gear row is a double planetary gear row and consists of a fourth sun gear, a fourth planet carrier, a long planetary gear, a short planetary gear and a fourth gear ring, wherein the fourth sun gear and the short planetary gear are in external engagement transmission, the long planetary gear and the fourth gear ring are in internal engagement transmission, the long planetary gear and the short planetary gear are in external engagement transmission, and the long planetary gear and the short planetary gear are respectively rotatably supported on the fourth planet carrier; the fourth gear ring is connected with the output shaft;
the coupling member set includes a first coupling member, a second coupling member, a third coupling member, a fourth coupling member, a fifth coupling member, and a sixth coupling member;
the first coupling member interconnecting the first sun gear and the second sun gear, the second coupling member interconnecting the first planet carrier and the second ring gear, the third coupling member interconnecting the second planet carrier and the third sun gear, the fourth coupling member interconnecting the third planet carrier and the fourth planet carrier, the fifth coupling member interconnecting the third ring gear and the fourth ring gear, the sixth coupling member interconnecting the third planet gears and the long planet gears;
the first brake interconnecting the second ring gear with the transmission housing, the second brake interconnecting the first ring gear with the transmission housing, and the third brake interconnecting the fourth sun gear with the transmission housing;
the first clutch interconnecting the input shaft with the first sun gear, the second clutch interconnecting the input shaft with the first ring gear, and the third clutch interconnecting the input shaft with the fourth carrier;
the first clutch, the second clutch, the third clutch, the first brake, the second brake, and the third brake are selectively engaged to establish nine forward speed ratios and one reverse speed ratio between the input shaft and the output shaft, including four downshift gears, one direct gear, and four overdrive gears.
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.
Further, a second gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the second brake, and the third brake.
Further, a third gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the second clutch and the third brake.
Further, a fourth gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the third clutch and the third brake.
Further, a five-speed gear ratio is established between the input shaft and the output shaft by engaging the first, second and third clutches.
Further, a six-speed transmission 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 seven speed ratio is established between the input shaft and the output shaft by engaging the first clutch, the first brake and the third clutch.
Further, an eight speed ratio is established between the input shaft and the output shaft by engaging the second brake, the first brake and the third clutch.
Further, a nine speed gear ratio is established between the input shaft and the output shaft by engaging the second clutch, the first 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 first brake and the second clutch.
The technical scheme provided by the invention has the beneficial effects that:
1. the nine-gear automatic transmission provided by the invention adopts a planetary gear train for transmission, and four planetary gear rows are simple and compact in structure, small in size and light in weight, and adopts a Ravigneaux mechanism to be combined with other planetary gear rows, so that the manufacturing process is mature;
2. the nine-gear automatic transmission provided by the invention has the advantages that the number of torque transmission components is small, six torque transmission components are adopted, and the control difficulty and the corresponding volume of the transmission are reduced to a certain extent;
3. the nine-gear automatic transmission provided by the invention has the advantages that the control of each gear of the nine-gear automatic transmission only needs to combine three control elements (clutches or brakes), and only needs to replace a pair of torque transmission members to combine and disconnect when the adjacent gears are changed, so that the control is simple;
4. the speed ratio range of the nine-gear automatic transmission provided by the invention reaches 13.18, the overdrive step ratio is small, and gear shifting is more stable during high-speed running.
Drawings
FIG. 1 is a schematic illustration of a nine speed automatic transmission of large speed ratio range of the present invention.
Detailed Description
For the purpose of making 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.
Referring to fig. 1, an embodiment of the present invention provides a nine-speed automatic transmission with a large speed ratio range, which includes a transmission housing 3, and an input shaft 1, an output shaft 2, a planetary gear row group, a coupling member group, and a torque transmitting device mounted inside the transmission housing 3, wherein the planetary gear row group includes a first planetary gear row, a second planetary gear row, a third planetary gear row, and a fourth planetary gear row mounted in order from front to back. The coupling member group comprises a first coupling member 4, a second coupling member 5, a third coupling member 6, a fourth coupling member 7, a fifth coupling member 8 and a sixth coupling member 9.
The first planetary gear row is composed of a first gear ring 11, a first planetary gear 12, a first planet carrier 13 and a first sun gear 14, the first sun gear 14 and the first planetary gear 12 are in external engagement transmission, the first planetary gear 12 and the first gear ring 11 are in internal engagement transmission, and the first planetary gear 12 is rotatably supported on the first planet carrier 13 through a rolling or sliding bearing.
The second planetary gear row is composed of a second gear ring 21, a second planetary gear 22, a second planet carrier 23 and a second sun gear 24, the second sun gear 24 and the second planetary gear 22 are in external engagement transmission, the second planetary gear 22 and the second gear ring 21 are in internal engagement transmission, and the second planetary gear 22 is rotatably supported on the second planet carrier 23 through a rolling or sliding bearing.
The third planetary gear row is composed of a third gear ring 31, a third planetary gear 32, a third planet carrier 33 and a third sun gear 34, the third sun gear 34 and the third planetary gear 32 are in external engagement transmission, the third planetary gear 32 and the third gear ring 31 are in internal engagement transmission, and the third planetary gear 32 is rotatably supported on the third planet carrier 33 through a rolling or sliding bearing.
The fourth planetary gear row is a double planetary gear row and consists of a fourth gear ring 41, a long planetary gear 42, a fourth planetary carrier 43, a short planetary gear 44 and a fourth sun gear 45, wherein the fourth sun gear 45 and the short planetary gear 44 are in external engagement transmission, the long planetary gear 42 and the fourth gear ring 41 are in internal engagement transmission, the long planetary gear 42 and the short planetary gear 44 are in external engagement transmission, the long planetary gear 42 and the short planetary gear 44 are respectively supported on the fourth planetary carrier 43 in a rotating manner through rolling or sliding bearings, and the fourth gear ring 41 is connected with the output shaft 2.
In this embodiment, the first coupling member 4 interconnects the first sun gear 14 and the second sun gear 24, the second coupling member 5 interconnects the first planet carrier 13 and the second ring gear 21, the third coupling member 6 interconnects the second planet carrier 23 and the third sun gear 34, the fourth coupling member 7 interconnects the third planet carrier 33 and the fourth planet carrier 43, the fifth coupling member 8 interconnects the third ring gear 31 and the fourth ring gear 41, and the sixth coupling member 9 interconnects the third planet gears 32 and the long planet gears 42.
The torque transmitting devices include a first clutch C1, a second clutch C2, a third clutch C3, a first brake B1, a second brake B2, and a third brake B3. The first clutch C1 interconnects the input shaft 1 with the first sun gear 14; the second clutch C2 interconnects the input shaft 1 with the first ring gear 11; the third clutch C3 interconnects the input shaft 1 with the fourth carrier 43. The first brake B1, the second brake B2 and the third brake B3 are fixedly connected with the transmission housing 3, respectively.
The first brake B1 is connected with the second ring gear 21, the first brake B1 interconnects the second ring gear 21 with the transmission housing 3, the second brake B2 is connected with the first ring gear 11, the second brake B2 interconnects the first ring gear 11 with the transmission housing 3, the third brake B3 is connected with the fourth sun gear 45, and the third brake B3 interconnects the fourth sun gear 45 with the transmission housing 3.
The first clutch C1, the second clutch C2, the third clutch C3, the first brake B1, the second brake B2 and the third brake B3 are selectively engaged to establish nine forward speed ratios and one reverse speed ratio between the input shaft 1 and the output shaft 2, which is implemented as follows:
by engaging the third brake B3, the first brake B1 and the first clutch C1 to establish a first gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 and the third brake B3 are engaged to connect the first carrier 13 and the fourth sun gear 45, respectively, with the transmission housing 3, rotation of the second coupling member 5 and the fourth sun gear 45 relative to the transmission housing 3 is prevented. The first clutch C1 is engaged to connect the input shaft 1 and the first sun gear 14 for rotation together. Thereby, a first gear transmission ratio is established between the input shaft 1 and the output shaft 2, the first gear transmission ratio being 5.93;
by engaging the third brake B3, the second brake B2 and the first clutch C1 to establish a second gear ratio between the input shaft 1 and the output shaft 2, specifically, the second brake B2 and the third brake B3 are engaged to connect the first ring gear 11 and the fourth sun gear 45 with the transmission case 3, respectively, rotation of the first ring gear 11 and the fourth sun gear 45 relative to the transmission case 3 is prevented. The first clutch C1 is engaged to connect the input shaft 1 and the first sun gear 14 for rotation together. Thereby, a second gear transmission ratio is established between the input shaft 1 and the output shaft 2, the second gear transmission ratio is 3.73, and the speed ratio step is 1.59;
by engaging the third brake B3, the first clutch C1 and the second clutch C2 to establish a three-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the third brake B3 is engaged to connect the fourth sun gear 45 with the transmission case 3, rotation of the fourth sun gear 45 relative to the transmission case 3 is prevented. The first clutch C1 and the second clutch C2 are engaged to connect the input shaft 1 with the first sun gear 14 and the first gear ring 11 for rotation respectively, thereby establishing a three-gear transmission ratio between the input shaft 1 and the output shaft 2, wherein the three-gear transmission ratio is 2.37, and the speed ratio is 1.57;
by engaging the third brake B3, the first clutch C1 and the third clutch C3 to establish a four-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the third brake B3 is engaged to connect the fourth sun gear 45 with the transmission case 3, rotation of the fourth sun gear 45 relative to the transmission case 3 is prevented. The first clutch C1 and the third clutch C3 are engaged to connect the input shaft 1 with the first sun gear 14 and the fourth planet carrier 43 for rotation, respectively, thereby establishing a four-gear transmission ratio between the input shaft 1 and the output shaft 2, the four-gear transmission ratio being 1.59, and the ratio step being 1.49;
by engaging the first clutch C1, the second clutch C2 and the third clutch C3 to establish a five-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first clutch C1, the second clutch C2 and the third clutch C3 are engaged to connect the input shaft 1 with the first sun gear 14, the first ring gear 11 and the fourth carrier 43, respectively, for rotation, thereby establishing a five-speed gear ratio, i.e., a direct gear, between the input shaft 1 and the output shaft 2, the five-speed gear ratio being 1, and the speed ratio step being 1.59;
by engaging the first clutch C1, the second brake B2 and the third clutch C3 to establish a six-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the second brake B2 is engaged to connect the first ring gear 11 with the transmission case 3, rotation of the first ring gear 11 relative to the transmission case 3 is prevented. The first clutch C1 and the third clutch C3 are engaged to connect the input shaft 1 with the first sun gear 14 and the fourth planet carrier 43 for rotation, respectively, thereby establishing a six-gear transmission ratio between the input shaft 1 and the output shaft 2, the six-gear transmission ratio being 0.79 and the ratio step being 1.27;
by engaging the first clutch C1, the first brake B1 and the third clutch C3 to establish a seven-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 is engaged to connect the first carrier 13 and the transmission housing 3, rotation of the first carrier 13 relative to the transmission housing 3 is prevented. The first clutch C1 and the third clutch C3 are engaged to connect the input shaft 1 with the first sun gear 14 and the fourth planet carrier 43 for rotation, respectively, thereby establishing a seven-gear transmission ratio between the input shaft 1 and the output shaft 2, the seven-gear transmission ratio being 0.69 and the ratio step being 1.14;
by engaging the first brake B1, the second brake B2 and the third clutch C3 to establish an eight speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 and the second brake B2 are engaged to connect the first carrier 13 and the first ring gear 11 with the transmission case 3, rotation of the first carrier 13 and the first ring gear 11 relative to the transmission case 3 is prevented. The third clutch C3 is engaged to connect the input shaft 1 and the fourth carrier 43 for rotation together, thereby establishing an eight speed gear ratio between the input shaft 1 and the output shaft 2, the eight speed gear ratio being 0.57, the ratio step being 1.21;
by engaging the first brake B1, the second clutch C2 and the third clutch C3 to establish a nine speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 is engaged to connect the first carrier 13 and the transmission housing 3, rotation of the first carrier 13 relative to the transmission housing 3 is prevented. The second clutch C2 and the third clutch C3 are engaged to connect the input shaft 1 with the first ring gear 11 and the fourth carrier 43 for rotation, respectively, thereby establishing a nine speed gear ratio between the input shaft 1 and the output shaft 2, the nine speed gear ratio being 0.45, the ratio step being 1.27;
by engaging the first brake B1, the third brake B3 and the second clutch C2 to establish a reverse gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 and the third brake B3 are engaged to connect the first carrier 13 and the fourth sun gear 45 with the transmission case 3, respectively, rotation of the first carrier 13 and the fourth sun gear 45 relative to the transmission case 3 is prevented. The second clutch C2 is engaged to connect the input shaft 1 and the first ring gear 11 for rotation together, thereby establishing a reverse gear ratio between the input shaft 1 and the output shaft 2, the reverse gear ratio being 3.89;
the operation logic table of the first clutch C1, the second clutch C2, the third clutch C3, the first brake B1, the second brake B2, and the third brake B3 is shown in table 1:
table 1: operating logic table
Figure BDA0002788507030000091
Figure BDA0002788507030000101
/>
In the present embodiment, the first clutch C1, the second clutch C2, and the third clutch C3 are multi-plate wet clutches or dog clutches, and the first brake B1, the second brake B2, and the third brake B3 are drum brakes or multi-plate wet brakes.
In this document, terms such as front, rear, upper, lower, etc. are defined with respect to the positions of the components in the drawings and with respect to each other, for clarity and convenience in expressing the technical solution. It should be understood that the use of such orientation terms should not limit the scope of the protection sought herein.
The embodiments described above and features of the embodiments herein may be combined with each other without conflict.
The foregoing description of the preferred embodiments of the invention is not intended to limit the invention to the precise form disclosed, and any such modifications, equivalents, and alternatives falling within the spirit and scope of the invention are intended to be included within the scope of the invention.

Claims (3)

1. The utility model provides a nine keep off automatic gearbox that speed ratio scope is big, includes the derailleur shell and installs in inside input shaft, output shaft, planetary gear row group, coupling member group and the torque transmission device of derailleur shell, planetary gear row group is including first planetary gear row, second planetary gear row, third planetary gear row and the fourth planetary gear row of installing in proper order from front to back, torque transmission device includes first clutch, second clutch, third clutch, first stopper, second stopper, third stopper, first stopper, second stopper, third stopper and third shell all links firmly, its characterized in that:
the first planetary gear row consists of a first sun gear, a first planet carrier, a first planet gear and a first gear ring, wherein the first sun gear and the first planet gear are in external engagement transmission, the first planet gear and the first gear ring are in internal engagement transmission, and the first planet gear is rotatably supported on the first planet carrier;
the second planetary gear row consists of a second sun gear, a second planet carrier, a second planet gear and a second gear ring, wherein the second sun gear and the second planet gear are in external engagement transmission, the second planet gear and the second gear ring are in internal engagement transmission, and the second planet gear is rotatably supported on the second planet carrier;
the third planetary gear row consists of a third sun gear, a third planet carrier, a third planet gear and a third gear ring, wherein the third sun gear and the third planet gear are in external meshed transmission, the third planet gear and the third gear ring are in internal meshed transmission, and the third planet gear is rotatably supported on the third planet carrier;
the fourth planetary gear row is a double planetary gear row and consists of a fourth sun gear, a fourth planet carrier, a long planetary gear, a short planetary gear and a fourth gear ring, wherein the fourth sun gear and the short planetary gear are in external engagement transmission, the long planetary gear and the fourth gear ring are in internal engagement transmission, the long planetary gear and the short planetary gear are in external engagement transmission, and the long planetary gear and the short planetary gear are respectively rotatably supported on the fourth planet carrier; the fourth gear ring is connected with the output shaft;
the coupling member set includes a first coupling member, a second coupling member, a third coupling member, a fourth coupling member, a fifth coupling member, and a sixth coupling member;
the first coupling member interconnecting the first sun gear and the second sun gear, the second coupling member interconnecting the first planet carrier and the second ring gear, the third coupling member interconnecting the second planet carrier and the third sun gear, the fourth coupling member interconnecting the third planet carrier and the fourth planet carrier, the fifth coupling member interconnecting the third ring gear and the fourth ring gear, the sixth coupling member interconnecting the third planet gears and the long planet gears;
the first brake interconnecting the second ring gear with the transmission housing, the second brake interconnecting the first ring gear with the transmission housing, and the third brake interconnecting the fourth sun gear with the transmission housing;
the first clutch interconnecting the input shaft with the first sun gear, the second clutch interconnecting the input shaft with the first ring gear, and the third clutch interconnecting the input shaft with the fourth carrier;
the three combinations of the first clutch, the second clutch, the third clutch, the first brake, the second brake, and the third brake are selectively engaged to establish nine forward speed ratios and a reverse speed ratio between the input shaft and the output shaft.
2. The nine speed automatic transmission having a large speed ratio range according to claim 1, characterized in that:
a reverse gear ratio is established between the input shaft and the output shaft by engaging the third brake, the first brake and the second clutch.
3. The nine speed automatic transmission having a large speed ratio range according to claim 1, characterized in that:
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 first clutch, the second brake and the third brake;
establishing a three-speed 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 five-speed gear ratio between the input shaft and the output shaft by engaging the first, second and third clutches;
establishing a six-speed transmission ratio between the input shaft and the output shaft by engaging the first clutch, the second brake, and the third clutch;
establishing a seven speed 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 ratio between the input shaft and the output shaft by engaging the second brake, the first brake and the third clutch;
nine gear ratios are established between the input shaft and the output shaft by engaging the second clutch, the first brake and the third clutch.
CN202011306640.7A 2020-11-19 2020-11-19 Nine-gear automatic transmission with large speed ratio range Active CN112324876B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202011306640.7A CN112324876B (en) 2020-11-19 2020-11-19 Nine-gear automatic transmission with large speed ratio range

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202011306640.7A CN112324876B (en) 2020-11-19 2020-11-19 Nine-gear automatic transmission with large speed ratio range

Publications (2)

Publication Number Publication Date
CN112324876A CN112324876A (en) 2021-02-05
CN112324876B true CN112324876B (en) 2023-05-26

Family

ID=74321778

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202011306640.7A Active CN112324876B (en) 2020-11-19 2020-11-19 Nine-gear automatic transmission with large speed ratio range

Country Status (1)

Country Link
CN (1) CN112324876B (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114001133B (en) * 2021-10-26 2023-04-18 中国地质大学（武汉） Nine-forward-gear automatic transmission
CN114001132A (en) * 2021-10-26 2022-02-01 中国地质大学（武汉） Nine-gear automatic transmission with small step ratio
CN115853978B (en) * 2023-02-06 2023-05-16 盛瑞传动股份有限公司 Gear box

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008000429A1 (en) * 2008-02-28 2009-09-03 Zf Friedrichshafen Ag Multi-speed transmission
DE102008041213B4 (en) * 2008-08-13 2018-10-18 Zf Friedrichshafen Ag Multi-speed transmission
KR20120132021A (en) * 2011-05-27 2012-12-05 현대자동차주식회사 Planetary gear train of automatic transmission for vehicles
DE102012206817B4 (en) * 2012-04-25 2021-03-11 Zf Friedrichshafen Ag Multi-speed transmission
CN107076273B (en) * 2014-10-23 2019-08-13 马自达汽车株式会社 Automatic transmission
CN105090394B (en) * 2015-07-17 2018-04-10 中国地质大学（武汉） A kind of nine speed transmission
CN105179615B (en) * 2015-07-17 2018-02-27 中国地质大学（武汉） A kind of nine speed transmission
KR101846884B1 (en) * 2016-02-03 2018-04-09 현대자동차 주식회사 Planetary gear train of automatic transmission for vehicles
CN106949201B (en) * 2017-04-11 2019-03-22 广州汽车集团股份有限公司 Nine speed automatic transmissions
KR102375167B1 (en) * 2017-06-19 2022-03-17 현대자동차주식회사 Transmission for vehicles
CN109798334A (en) * 2019-02-25 2019-05-24 燕山大学 A kind of nine speed transmission
CN109764095B (en) * 2019-02-25 2022-02-18 燕山大学 Nine-gear transmission

Also Published As

Publication number Publication date
CN112324876A (en) 2021-02-05

Similar Documents

Publication Publication Date Title
CN112324876B (en) Nine-gear automatic transmission with large speed ratio range
US8801566B2 (en) Quad-clutch multi-speed transmission
KR101427977B1 (en) Planetary gear train of automatic transmission for vehicles
KR101509726B1 (en) Planetary gear train of automatic transmission for vehicles
CN111043260B (en) Six-gear transmission
US9022891B2 (en) Triple clutch multi-speed transmission
CN109764095B (en) Nine-gear transmission
US8747274B2 (en) Triple clutch multi-speed transmission
CN107269779B (en) Three-planet-row six-speed automatic transmission
CN106884936B (en) Three-planet-row six-speed automatic transmission and automobile
CN112324874B (en) Nine-gear automatic transmission with stable step ratio
US9145960B2 (en) Triple clutch multi-speed transmission
CN112324875B (en) Nine-gear automatic transmission with small step ratio
CN112324877B (en) Nine-gear automatic transmission
CN111550531B (en) 12-speed automatic transmission
GB2465997A (en) A dual clutch transmission with Ravigneaux type planetary gearsets
CN114001133B (en) Nine-forward-gear automatic transmission
CN111750047B (en) Multi-gear planetary row type automatic transmission, control method thereof and vehicle
KR100482582B1 (en) Power train in an automatic transmission for vehicles
CN109973595B (en) Double-stage planetary gear type automatic transmission based on lever analysis method
CN115750699A (en) Nine-gear automatic transmission structure
CN217177299U (en) Multi-gear automatic transmission
CN114001132A (en) Nine-gear automatic transmission with small step ratio
CN112253701B (en) Nine-gear automatic transmission with double-shaft structure
CN216951504U (en) Multi-gear hydraulic automatic transmission

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant