CN116877646A - Eleven-gear planetary gear transmission and automobile - Google Patents
Eleven-gear planetary gear transmission and automobile Download PDFInfo
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- CN116877646A CN116877646A CN202310800839.2A CN202310800839A CN116877646A CN 116877646 A CN116877646 A CN 116877646A CN 202310800839 A CN202310800839 A CN 202310800839A CN 116877646 A CN116877646 A CN 116877646A
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
- 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
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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
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
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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
- 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
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/10—Braking arrangements
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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
- 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
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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
- 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
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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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/087—Arrangement and support of friction devices in planetary gearings, e.g. support of clutch drums, stacked arrangements of friction devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0073—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eleven forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The application provides an eleven-gear planetary gear transmission and an automobile, which comprise a transmission shell, an input shaft, an output shaft, a planetary gear row group and a torque transmission group, wherein the input shaft and the planetary gear row group are arranged in the transmission shell, the planetary gear row group consists of a plurality of planetary gear rows, the torque transmission group consists of a plurality of brakes and a plurality of clutch groups, and the input shaft is connected to the output shaft after being sequentially matched with the planetary gear row group and the torque transmission group. The eleven-gear planetary gear transmission and the automobile provided by the application are simple and compact, eleven-gear speed change can be realized, a plurality of elements are not required to be connected to each gear, gear shifting control is relatively simple, the speed ratio change between each gear is small, the speed regulation change is smooth, the feeling of pause and frustration is small, riding comfort can be improved, and the impact force between gears is small, abrasion is less, so that the service life is longer, and the practicability is strong.
Description
Technical Field
The application relates to the technical field of automobile transmission, in particular to an eleven-gear planetary gear transmission and an automobile.
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. The number of gears of the automatic transmission on the market at present is mostly between 4 and 9, and only 10 gears and more of the automatic transmission are used by individual high-grade vehicles, so that no related research data exists for an eleven-gear speed reducer. Generally, the more gears of an automatic transmission, the denser the gear ratio, the less the feel of a jerk during shifting, the smoother the acceleration, and the relatively reduced fuel consumption. An automatic transmission that can achieve more gears with fewer planetary rows and engagement elements will be a future development of the automatic transmission.
The highest energy-yielding automatic transmission in the market at present is a 10-gear automatic transmission. There are mainly the Toyota AWR10L65 series and the GM/Ford co-developed 10R80 series.
In the existing automatic transmission mechanism using a planetary gear mechanism for a high gear, four rows of planetary gear trains formed by combining a Simpson mechanism and other two planetary rows are mainly adopted, and are matched with four brakes, two clutches and a sliding sleeve clutch to obtain eleven forward gears and two reverse gears. However, the transmission requires three coupling elements to be engaged in each gear, which is relatively complex in terms of transmission shift control.
With the increasing popularity of automobiles in society, people demand for automatic transmissions with high gear numbers is also increasing, and research and development of novel transmission structures of automatic transmissions with high gear numbers are necessary.
Disclosure of Invention
According to the defects of the prior art, the application aims to provide an eleven-gear planetary gear transmission and an automobile, which are simple and compact, can realize eleven-gear speed change, do not need to be connected with a plurality of elements in each gear, and are relatively simple in gear shifting control.
In order to solve the technical problems, the application adopts the following technical scheme:
an eleven-gear planetary gear transmission comprises a transmission shell, an input shaft, an output shaft, a planetary gear row group and a torque transmission group, wherein the input shaft and the output shaft are arranged in the transmission shell;
the input shaft is connected to the output shaft after being sequentially assembled with the planetary gear row group and the torque transmission group.
Further, 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;
the first planetary gear row comprises 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 is a double planetary gear row and comprises a second sun gear, a second long planetary carrier, a second short planetary carrier, a long planetary gear, a short planetary gear and a second gear ring, wherein the second sun gear and the short planetary gear are in external engagement transmission, the short planetary gear and the long planetary gear are in external engagement transmission, the long planetary gear and the second gear ring are in internal engagement transmission, the short planetary gear is rotatably supported on the second short planetary carrier, and the long planetary gear is rotatably supported on the second long planetary carrier;
the third planetary gear row comprises 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 comprises a fourth sun gear, a fourth planet carrier, a fourth planet gear and a fourth gear ring, the fourth sun gear and the fourth planet gear are in external engagement transmission, the fourth planet gear and the fourth gear ring are in internal engagement transmission, and the fourth planet gear is rotatably supported on the fourth planet carrier.
Further, the torque transfer set includes a first clutch, a second clutch, a third clutch, a fourth clutch, a fifth clutch, a first brake, and a second brake;
the first gear ring is fixedly connected with the transmission shell, the first sun gear is fixedly connected with the input shaft, the second long planet carrier is fixedly connected with the third planet carrier, the second gear ring is fixedly connected with the third gear ring, the long planet wheel is fixedly connected with the third planet wheel, the third sun gear is fixedly connected with the fourth gear ring, and the third gear ring is fixedly connected with the fourth sun gear;
the transmission shell is connected with the third gear ring through a first brake, and the transmission shell is connected with the fourth gear ring through a second brake;
the input shaft is fixedly connected with the first sun gear, the output shaft is connected with the fourth planet carrier,
the first planet carrier is connected with the second gear ring through a first clutch, the first planet carrier is connected with the second long planet carrier and the second short planet carrier through a second clutch, the first planet carrier is connected with the second sun gear through a third clutch, the input shaft is connected with the second short planet carrier through a fourth clutch, and the input shaft is connected with the third sun gear through a fifth clutch.
Further, a first gear ratio is established between the input shaft and the output shaft by engaging the second clutch and the second brake;
establishing a second gear ratio between the input shaft and the output shaft by engaging the first clutch and the second clutch;
establishing a three-speed gear ratio between the input shaft and the output shaft by engaging the first brake and the second clutch;
establishing a fourth gear ratio between the input shaft and the output shaft by engaging the second clutch and the fifth clutch;
establishing a five-speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the first brake;
establishing a six-speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the first clutch;
establishing a seven speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the third clutch;
establishing an eight speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the fourth clutch;
establishing a nine speed gear ratio between the input shaft and the output shaft by engaging the third clutch and the fourth clutch;
establishing a ten speed ratio between the input shaft and the output shaft by engaging the first clutch and the fourth clutch;
establishing an eleven-speed gear ratio between the input shaft and the output shaft by engaging the first brake and the fourth clutch;
a reverse gear ratio is established between the input shaft and the output shaft by engaging the first brake and the third clutch.
Further, the first clutch, the second clutch, the third clutch, the fourth clutch and the fifth clutch are multi-plate wet clutches or jaw clutches.
Further, the first brake and the second brake are drum brakes or multi-disc wet brakes.
Further, the first planetary gear row, the second planetary gear row, the third planetary gear row, and the fourth planetary gear row are provided in this order between the input shaft and the output shaft.
Further, the distance between the first planetary gear row and the second planetary gear row, the distance between the second planetary gear row and the third planetary gear row, and the distance between the third planetary gear row and the fourth planetary gear row are kept uniform.
Further, the K value of the first planetary gear row is K1, the K value of the second planetary gear row is K2, the K value of the third planetary gear row is K3, the K value of the fourth planetary gear row is K4, and the transmission ratios from first gear to eleven gear and reverse gear are respectively:
first gear ratio: (k3-1)/(k1·k3·k4-k1·k3-k3·k4+k3);
second gear ratio: -1/(k 1-1);
three gear ratio: (k3.k4-k4)/(k1.k4-k1-k4+1);
four gear ratio: (k1.k3.k4-k1-k3.k4+k3)/(k1.k3.k4-k1.k3-k3.k4+k3);
five gear ratio: k 4/(k 4-1);
six gear ratio: (k1.k4-k4+1)/(k1.k4-k1-k4+1);
seven gear ratio:
eight gear ratio: 1, a step of;
nine gear ratio:
ten gear ratio: (-k1.k3.k4+k1.k4-k4+1)/(k1.k4-k1-k4+1);
eleven gear ratios: (-k3·k4+k4)/(k 4-1);
reverse gear:
an automobile using the eleven-speed planetary transmission of any one of the claims.
Compared with the prior art, the application has the following advantages and beneficial effects:
1. the eleven-gear planetary gear transmission and the automobile provided by the application comprise four planetary gear row structures which are sequentially arranged along the direction from an input shaft to an output shaft; the clutch in the torque transmission device is connected with the input shaft and the planetary gear train, the brake in the torque transmission device is connected with the transmission shell and the planetary gear train, two combinations of the clutches and the brakes are selectively jointed, eleven forward gear speed ratios and one reverse gear speed ratio are established between the input shaft and the output shaft, the step ratio between gears is small, and gear shifting is stable during high-speed running.
2. The eleven-gear planetary gear transmission provided by the application is driven by the planetary gear rows, and the four planetary gear rows are simple and compact in structure and small in size, and are combined by other planetary gear rows of a common Ravigneaux type structure, so that the manufacturing process is mature.
3. The eleven-gear transmission adopts seven torque transmission members, so that the transmission control difficulty and the corresponding volume are reduced to a certain extent.
4. The control of each gear only needs to combine two torque transmission members (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
The accompanying drawings are included to provide a further understanding of the application, and are incorporated in and constitute a part of this specification. The exemplary embodiments of the present application and the descriptions thereof are for explaining the present application and do not constitute an undue limitation of the present application. In the drawings:
fig. 1 is a schematic diagram of an eleven-speed planetary transmission of the present application.
Wherein, 1, an input shaft; 2. an output shaft; 3. a first row of planet gears; 31. a first ring gear; 32. a first planet; 33. a first planet carrier; 34. a first sun gear; 4. a second planetary gear row; 41. a second ring gear; 42. a long planet wheel; 43. a second long planet carrier; 44. a second short planet carrier; 45. a short planet wheel; 46. a second sun gear; 5. a third planetary gear row; 51. a third ring gear; 52. a third planet wheel; 53. a third carrier; 54. a third sun gear; 6. a fourth planetary gear row; 61. a fourth ring gear; 62. a fourth planetary gear; 63. a fourth carrier; 64. a fourth sun gear; 7. a transmission housing; c1, a first clutch; c2, a second clutch; c3, a third clutch; c4, a fourth clutch; c5, a fifth clutch; b1, a first brake; b2, a second brake.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present application.
In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present application. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first", "a second", etc. may explicitly or implicitly include one or more such feature. In the description of the present application, unless otherwise indicated, the meaning of "a plurality" is two or more.
The application provides an eleven-gear planetary gear transmission, which is shown in a figure 1 and comprises a transmission shell 7, an input shaft 1, an output shaft 2, a planetary gear row group consisting of a plurality of planetary gear rows and a torque transmission group consisting of a plurality of brakes and a plurality of clutch groups, wherein the input shaft 1 and the output shaft 2 are arranged in the transmission shell 7;
the input shaft 1 is connected to the output shaft 2 after being sequentially coupled with the planetary gear row set and the torque transmission set.
The application realizes gear transmission ratio by transmitting through a planetary gear row group formed by a plurality of planetary gear rows, a torque transmission group formed by a plurality of brakes and a plurality of clutch groups.
In the present application, as shown in fig. 1, the planetary gear row group includes a first planetary gear row 3, a second planetary gear row 4, a third planetary gear row 5, and a fourth planetary gear row 6.
The first planetary gear set includes a first sun gear 34, a first planet carrier 33, a first planet gear 32 and a first gear ring 31, the first sun gear 34 and the first planet gear 32 are in external engagement transmission, the first planet gear 32 and the first gear ring 31 are in internal engagement transmission, and the first planet gear 32 is rotatably supported on the first planet carrier 33.
The second planetary gear row is a double planetary gear planetary row and comprises a second sun gear 46, a second long planetary carrier 43, a second short planetary carrier 44, long planetary gears 42, short planetary gears 45 and a second gear ring 41, wherein the second sun gear 46 and the short planetary gears 45 are in external engagement transmission, the short planetary gears 45 and the long planetary gears 42 are in external engagement transmission, the long planetary gears 42 and the second gear ring 41 are in internal engagement transmission, the short planetary gears 45 are rotatably supported on the second short planetary carrier 44, and the long planetary gears 42 are rotatably supported on the second long planetary carrier 43.
The third planetary gear row comprises a third sun gear 54, a third planet carrier 53, a third planet gear 52 and a third gear ring 51, the third sun gear 54 and the third planet gear 52 are in external engagement transmission, the third planet gear 52 and the third gear ring 51 are in internal engagement transmission, and the third planet gear 52 is rotatably supported on the third planet carrier 53.
The fourth planetary gear row comprises a fourth sun gear 64, a fourth planet carrier 63, fourth planet gears 62 and a fourth gear ring 61, the fourth sun gear 64 and the fourth planet gears 62 are in external engagement transmission, the fourth planet gears 62 and the fourth gear ring 61 are in internal engagement transmission, and the fourth planet gears 62 are rotatably supported on the fourth planet carrier 63.
The first gear ring 31 is fixedly connected with the transmission housing 7, the first sun gear 34 is fixedly connected with the input shaft 1, the second long planet carrier 43 is fixedly connected with the third planet carrier 53, the second gear ring 41 is fixedly connected with the third gear ring 51, the long planet gear 42 is fixedly connected with the third planet gear 54, the third sun gear 54 is fixedly connected with the fourth gear ring 61, and the third gear ring 51 is fixedly connected with the fourth sun gear 64.
The torque transmitting set includes a first clutch C1, a second clutch C2, a third clutch C3, a fourth clutch C4, a fifth clutch C5, a first brake B1, and a second brake B2.
The transmission case 7 is connected to the third ring gear 51 through the first brake B1, and the transmission case 7 is connected to the fourth ring gear 61 through the second brake B2.
The input shaft 1 is fixedly connected with the first sun gear 34, the output shaft 2 is connected with the fourth planet carrier 63,
the first carrier 33 is connected to the second ring gear 41 via a first clutch C1, the first carrier 33 is connected to the second long carrier 43 and the second short carrier 44 via a second clutch C2, the first carrier 33 is connected to the second sun gear 46 via a third clutch C3, the input shaft 1 is connected to the second short carrier 44 via a fourth clutch C4, and the input shaft 1 is connected to the third sun gear 54 via a fifth clutch C5.
The eleven-gear planetary gear transmission provided by the application adopts the common Ravigneaux type structure that other planetary rows are combined, has a compact structure and more gears, can realize eleven gears compared with the traditional nine-gear or eight-gear transmission, has small speed ratio change between each gear, smooth speed regulation change and small pause and frustration, can improve riding comfort, has small impact force and less abrasion between gears, and has longer service life and strong practicability.
In the present application, the torque transmitting devices are selectively engageable in combinations of two to establish eleven forward speed ratios and one reverse speed ratio between the input shaft and the output shaft, with the forward speeds including seven downshift gears (first gear to seventh gear), one direct gear (eighth gear) and three overdrive gears (ninth gear to eleventh gear).
By engaging the second clutch C2 and the second brake B2 to establish a first gear ratio between the input shaft 1 and the output shaft 2, specifically, the second brake B2 is engaged to connect the fourth ring gear 61 with the transmission case 7, rotation of the fourth ring gear 61 relative to the transmission case 7 is prevented. The second clutch C2 is engaged to connect the first carrier 33, the second long carrier 43, and the second short carrier 44 for rotation together. Thereby, a gear ratio of first gear is established between the input shaft 1 and the output shaft 2.
By engaging the second clutch C2 and the first clutch C1 to establish a second gear ratio between the input shaft 1 and the output shaft 2, specifically, the first clutch C1 is engaged to connect the first carrier 33 and the second ring gear 41 for rotation together. The second clutch C2 is engaged to connect the first carrier 33, the second long carrier 43, and the second short carrier 44 for rotation together. Thereby, a gear ratio of the second gear is established between the input shaft 1 and the output shaft 2.
By engaging the second clutch C2 and the first brake B1 to establish a three-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 is engaged to connect the third ring gear 51 with the transmission case 7, rotation of the third ring gear 51 relative to the transmission case 7 is prevented. The second clutch C2 is engaged to connect the first carrier 33, the second long carrier 43, and the second short carrier 44 for rotation together. Thereby, a three-gear transmission ratio is established between the input shaft 1 and the output shaft 2.
By engaging the second clutch C2 and the fifth clutch C5 to establish a four-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 54 for rotation together. The second clutch C2 is engaged to connect the first carrier 33, the second long carrier 43, and the second short carrier 44 for rotation together. Thereby, a four-speed gear ratio is established between the input shaft 1 and the output shaft 2.
By engaging the fifth clutch C5 and the first brake B1 to establish a five-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 is engaged to connect the third ring gear 51 with the transmission case 7, rotation of the third ring gear 51 relative to the transmission case 7 is prevented. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 54 for rotation together. Thus, a five-speed transmission ratio is established between the input shaft 1 and the output shaft 2.
By engaging the first clutch C1 and the fifth clutch C5 to establish a six-speed transmission ratio between the input shaft 1 and the output shaft 2, specifically, the fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 54 for rotation together. The first clutch C1 is engaged to connect the first carrier 33 and the second ring gear 41 for rotation together. Thereby, a six-speed transmission ratio is established between the input shaft 1 and the output shaft 2.
By engaging the third clutch C3 and the fifth clutch C5 to establish a seven-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 54 for rotation together. The third clutch C3 is engaged to connect the first carrier 33 and the second sun gear 46 for rotation together. Thereby, a seven-speed transmission ratio is established between the input shaft 1 and the output shaft 2.
By engaging the fourth clutch C4 and the fifth clutch C5 to establish an eight speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 54 for rotation together. The fourth clutch C4 is engaged to connect the input shaft 1 and the second stub carrier 44 for rotation together. Thus, an eight-speed transmission ratio is established between the input shaft 1 and the output shaft 2.
By engaging the fourth clutch C4 and the third clutch C3 to establish a nine speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the third clutch C3 is engaged to connect the first carrier 33 and the second sun gear 46 for rotation together. The fourth clutch C4 is engaged to connect the input shaft 1 and the second stub carrier 44 for rotation together. Thereby, a nine speed transmission ratio is established between the input shaft 1 and the output shaft 2.
By engaging the fourth clutch C4 and the first clutch C1 to establish a ten-speed transmission ratio between the input shaft 1 and the output shaft 2, specifically, the first clutch C1 is engaged to connect the first carrier 33 and the second ring gear 41 for rotation together. The fourth clutch C4 is engaged to connect the input shaft 1 and the second stub carrier 44 for rotation together. Thereby, a ten-speed transmission ratio is established between the input shaft 1 and the output shaft 2.
By engaging the fourth clutch C4 and the first brake B1 to establish an eleven-gear transmission ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 is engaged to connect the third ring gear 51 with the transmission case 7, rotation of the third ring gear 51 relative to the transmission case 7 is prevented. The fourth clutch C4 is engaged to connect the input shaft 1 and the second stub carrier 44 for rotation together. Thereby, a gear ratio of eleven gears is established between the input shaft 1 and the output shaft 2.
By engaging the third clutch C3 and the first brake B1 to establish an eleven-gear transmission ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 is engaged to connect the third ring gear 51 with the transmission case 7, rotation of the third ring gear 51 relative to the transmission case 7 is prevented. The third clutch C3 is engaged to connect the first carrier 33 and the second sun gear 46 for rotation together. Thereby, a reverse gear ratio is established between the input shaft 1 and the output shaft 2.
The eleven-gear transmission adopts seven torque transmission members, so that the transmission control difficulty and the corresponding volume are reduced to a certain extent.
The control of each gear only needs to combine two torque transmission members (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.
The operating logic tables of the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4, the fifth clutch C5, the first brake B1 and the second brake B2 are shown in the table, and ∈ in table 1 represents that the torque transmitting device is engaged. The speed ratios of the various gears and the speed ratio spacing between two adjacent gears are also shown in Table 1. It should be noted that these numbers are exemplary only and that these numbers may be adjusted within a range. The speed ratio refers to the ratio of the input speed to the output speed, and the planet row K value refers to the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear of the planet row. By setting the K value of the first planetary gear row 3 to K1, the K value of the second planetary gear row 4 to K2, the K value of the third planetary gear row 5 to K3, and the K value of the fourth planetary gear row 6 to K4, the gear ratio can be adjusted.
The transmission ratios from first gear to eleven gears and the reverse gear are respectively as follows:
first gear ratio: (k3-1)/(k1·k3·k4-k1·k3-k3·k4+k3);
second gear ratio: -1/(k 1-1);
three gear ratio: (k3.k4-k4)/(k1.k4-k1-k4+1);
four gear ratio: (k1.k3.k4-k1-k3.k4+k3)/(k1.k3.k4-k1.k3-k3.k4+k3);
five gear ratio: k 4/(k 4-1);
six gear ratio: (k1.k4-k4+1)/(k1.k4-k1-k4+1);
seven gear ratio:
eight gear ratio: 1, a step of;
nine gear ratio:
ten gear ratio: (-k1.k3.k4+k1.k4-k4+1)/(k1.k4-k1-k4+1);
eleven gear ratios: (-k3·k4+k4)/(k 4-1);
reverse gear:
in one embodiment of the present application, k1= -2.5, k2=3.8, k3= -1.6, k4= -1.9 are the speed ratios of the various gears in this embodiment as shown in table 1 below.
TABLE 1 eleven speed planetary transmission speed ratios, step ratio and coupling element engagement state table
According to the embodiment provided by the application, the eleven-gear planetary gear transmission provided by the application has the advantages of wide speed regulation range, smooth speed regulation, small step ratio, suitability for richer driving environments, small impact between gears and relatively long service life, and is suitable for a transmission with fewer gears.
In the present application, the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4, and the fifth clutch C5 are multi-plate wet clutches or dog clutches, and the first brake B1 and the second brake B2 are drum brakes or multi-plate wet brakes.
In the present application, the power of the input shaft 1 is supplied by an engine.
The application also provides an automobile, and the eleven-gear planetary gear transmission is used.
In summary, the eleven-gear planetary gear transmission and the automobile provided by the application comprise four planetary gear row structures which are sequentially arranged along the direction from an input shaft to an output shaft; the clutch in the torque transmission device is connected with the input shaft and the planetary gear train, the brake in the torque transmission device is connected with the transmission shell and the planetary gear train, two combinations of the clutches and the brakes are selectively jointed, eleven forward gear speed ratios and one reverse gear speed ratio are established between the input shaft and the output shaft, the step ratio between gears is small, and gear shifting is stable during high-speed running.
The eleven-gear planetary gear transmission provided by the application is driven by the planetary gear rows, and the four planetary gear rows are simple and compact in structure and small in size, and are combined by other planetary gear rows of a common Ravigneaux type structure, so that the manufacturing process is mature.
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 claimed application.
It will be apparent to those skilled in the art that various modifications and variations can be made to the present application without departing from the spirit or scope of the application. Thus, it is intended that the present application also include such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.
Claims (10)
1. An eleven-gear planetary gear transmission, characterized in that: the planetary gear set comprises a transmission shell, an input shaft, an output shaft, a planetary gear set group consisting of a plurality of planetary gear sets and a torque transmission set consisting of a plurality of brakes and a plurality of clutches, wherein the input shaft and the output shaft are arranged in the transmission shell;
the input shaft is connected to the output shaft after being sequentially assembled with the planetary gear row group and the torque transmission group.
2. An eleven-speed planetary transmission according to claim 1, wherein:
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; the first planetary gear row comprises 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 is a double planetary gear row and comprises a second sun gear, a second long planetary carrier, a second short planetary carrier, a long planetary gear, a short planetary gear and a second gear ring, wherein the second sun gear and the short planetary gear are in external engagement transmission, the short planetary gear and the long planetary gear are in external engagement transmission, the long planetary gear and the second gear ring are in internal engagement transmission, the short planetary gear is rotatably supported on the second short planetary carrier, and the long planetary gear is rotatably supported on the second long planetary carrier;
the third planetary gear row comprises 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 comprises a fourth sun gear, a fourth planet carrier, a fourth planet gear and a fourth gear ring, the fourth sun gear and the fourth planet gear are in external engagement transmission, the fourth planet gear and the fourth gear ring are in internal engagement transmission, and the fourth planet gear is rotatably supported on the fourth planet carrier.
3. An eleven-speed planetary transmission according to claim 2, wherein:
the torque transfer set includes a first clutch, a second clutch, a third clutch, a fourth clutch, a fifth clutch, a first brake, and a second brake;
the first gear ring is fixedly connected with the transmission shell, the first sun gear is fixedly connected with the input shaft, the second long planet carrier is fixedly connected with the third planet carrier, the second gear ring is fixedly connected with the third gear ring, the long planet wheel is fixedly connected with the third planet wheel, the third sun gear is fixedly connected with the fourth gear ring, and the third gear ring is fixedly connected with the fourth sun gear;
the transmission shell is connected with the third gear ring through a first brake, and the transmission shell is connected with the fourth gear ring through a second brake;
the input shaft is fixedly connected with the first sun gear, the output shaft is connected with the fourth planet carrier,
the first planet carrier is connected with the second gear ring through a first clutch, the first planet carrier is connected with the second long planet carrier and the second short planet carrier through a second clutch, the first planet carrier is connected with the second sun gear through a third clutch, the input shaft is connected with the second short planet carrier through a fourth clutch, and the input shaft is connected with the third sun gear through a fifth clutch.
4. An eleven-speed planetary transmission according to claim 3, wherein:
establishing a first gear ratio between the input shaft and the output shaft by engaging the second clutch and the second brake;
establishing a second gear ratio between the input shaft and the output shaft by engaging the first clutch and the second clutch;
establishing a three-speed gear ratio between the input shaft and the output shaft by engaging the first brake and the second clutch;
establishing a fourth gear ratio between the input shaft and the output shaft by engaging the second clutch and the fifth clutch;
establishing a five-speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the first brake;
establishing a six-speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the first clutch;
establishing a seven speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the third clutch;
establishing an eight speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the fourth clutch;
establishing a nine speed gear ratio between the input shaft and the output shaft by engaging the third clutch and the fourth clutch;
establishing a ten speed ratio between the input shaft and the output shaft by engaging the first clutch and the fourth clutch;
establishing an eleven-speed gear ratio between the input shaft and the output shaft by engaging the first brake and the fourth clutch;
a reverse gear ratio is established between the input shaft and the output shaft by engaging the first brake and the third clutch.
5. An eleven-speed planetary transmission according to claim 3, wherein:
the first clutch, the second clutch, the third clutch, the fourth clutch and the fifth clutch are multi-plate wet clutches or jaw clutches.
6. An eleven-speed planetary transmission according to claim 3, wherein:
the first brake and the second brake are drum brakes or multi-disc wet brakes.
7. An eleven-speed planetary transmission according to claim 2, wherein:
the first planetary gear row, the second planetary gear row, the third planetary gear row and the fourth planetary gear row are sequentially arranged between the input shaft and the output shaft.
8. An eleven-speed planetary transmission according to claim 2, wherein:
the distance between the first planetary gear row and the second planetary gear row, the distance between the second planetary gear row and the third planetary gear row, and the distance between the third planetary gear row and the fourth planetary gear row remain the same.
9. An eleven-speed planetary transmission according to claim 3, wherein:
the K value of the first planetary gear row is K1, the K value of the second planetary gear row is K2, the K value of the third planetary gear row is K3, the K value of the fourth planetary gear row is K4, and the transmission ratios from first gear to eleven gear and reverse gear are respectively:
first gear ratio: (k3-1)/(k1·k3·k4-k1·k3-k3·k4+k3);
second gear ratio: -1/(k 1-1);
three gear ratio: (k3.k4-k4)/(k1.k4-k1-k4+1);
four gear ratio: (k1.k3.k4-k1-k3.k4+k3)/(k1.k3.k4-k1.k3-k3.k4+k3);
five gear ratio: k 4/(k 4-1);
six gear ratio: (k1.k4-k4+1)/(k1.k4-k1-k4+1);
seven gear ratio:
eight gear ratio: 1, a step of;
nine gear ratio:
ten gear ratio: (-k1.k3.k4+k1.k4-k4+1)/(k1.k4-k1-k4+1);
eleven gear ratios: (-k3·k4+k4)/(k 4-1);
reverse gear:
10. an automobile, characterized in that the eleven-gear planetary transmission according to any one of claims 1 to 9 is used.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310800839.2A CN116877646A (en) | 2023-06-30 | 2023-06-30 | Eleven-gear planetary gear transmission and automobile |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310800839.2A CN116877646A (en) | 2023-06-30 | 2023-06-30 | Eleven-gear planetary gear transmission and automobile |
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| Publication Number | Publication Date |
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| CN116877646A true CN116877646A (en) | 2023-10-13 |
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ID=88265475
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|---|---|---|---|
| CN202310800839.2A Pending CN116877646A (en) | 2023-06-30 | 2023-06-30 | Eleven-gear planetary gear transmission and automobile |
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| Country | Link |
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| CN (1) | CN116877646A (en) |
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2023
- 2023-06-30 CN CN202310800839.2A patent/CN116877646A/en active Pending
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