CN116608244A - Thirteen-gear planetary gear transmission - Google Patents

Thirteen-gear planetary gear transmission Download PDF

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Publication number
CN116608244A
CN116608244A CN202310608833.5A CN202310608833A CN116608244A CN 116608244 A CN116608244 A CN 116608244A CN 202310608833 A CN202310608833 A CN 202310608833A CN 116608244 A CN116608244 A CN 116608244A
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CN
China
Prior art keywords
gear
clutch
transmission
input shaft
brake
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.)
Pending
Application number
CN202310608833.5A
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Chinese (zh)
Inventor
丁华锋
柯涛
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China University of Geosciences
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China University of Geosciences
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Filing date
Publication date
Application filed by China University of Geosciences filed Critical China University of Geosciences
Priority to CN202310608833.5A priority Critical patent/CN116608244A/en
Publication of CN116608244A publication Critical patent/CN116608244A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • 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
    • F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more 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

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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 thirteen-gear planetary gear transmission. The transmission comprises four planetary gear row structures which are sequentially arranged along the direction from an input shaft to an output shaft; clutches in the torque transfer devices connect the input shaft and the planetary gear sets, brakes in the torque transfer devices connect the transmission housing and the planetary gear sets, two combinations of each clutch and each brake are selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft and the output shaft. The planetary gear rows of the single planet are adopted for transmission, the four planetary gear rows are simple and compact in structure and small in size, and the common simpson is combined with other planetary rows, so that the manufacturing process is mature; seven torque transmitting members (clutches or brakes) are employed to reduce transmission control difficulty and corresponding bulk; the control of each gear of the transmission only needs to combine two torque transmission members, 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.

Description

Thirteen-gear planetary gear transmission
Technical Field
The invention belongs to the technical field of vehicle transmission, and particularly relates to a thirteen-gear planetary gear transmission.
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 or more automatic transmissions are used for individual high-grade vehicles. 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 planetary gear transmission with the highest energy-producing gear number on the market at present is a 10-gear planetary gear transmission. There are mainly the Toyota AWR10L65 series and the GM/Ford co-developed 10R80 series.
In the present invention patent relating to an automatic transmission mechanism using a planetary gear mechanism for a high gear, there are mainly the following types of planetary gear mechanisms.
Patent CN202010953345.4 of the limited responsibility company of fasciate gear of shanxi: the invention discloses an eleven-gear transmission based on a planetary gear train. However, the invention requires engagement of three coupling elements in each gear, which is relatively complex in terms of gearbox shift control. University of homotaxis patent No. cn201410256053.X: the eleven-gear speed changer adopts four single-planet planetary rows, and is matched with two brakes and four clutches to obtain eleven forward gears and one reverse gear, and each gear only needs to be connected with two combining elements
Planetary transmissions are composed and achieve multiple gear ratios using planetary gear trains, clutches, and brake arrangements. 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
The present invention aims to solve the above-mentioned drawbacks of the prior art and to provide a thirteenth-gear planetary transmission.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
the invention provides a thirteenth-gear planetary gear transmission, which comprises a transmission shell, an input shaft, an output shaft, a planetary gear row group and a torque transmission device, wherein the input shaft, the output shaft, the planetary gear row group and the torque transmission device are arranged in the transmission shell, and 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 along the direction from the input shaft to the output shaft, and is characterized in that:
the first planet 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 meshed transmission, the second planet gear and the second gear ring are in internal meshed 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 consists of a fourth sun gear, a fourth planet carrier, a fourth planet gear and a fourth gear ring, wherein the fourth sun gear and the fourth planet gear are in external meshed transmission, the fourth planet gear and the fourth gear ring are in internal meshed transmission, and the fourth planet gear is rotatably supported on the fourth planet carrier;
the first gear ring is fixedly connected with the transmission shell, the first sun gear is fixedly connected with the input shaft, the second planet carrier is fixedly connected with the third gear ring, the second gear ring is fixedly connected with the third planet carrier, the third planet carrier is fixedly connected with the fourth gear ring, and the third sun gear is fixedly connected with the fourth sun gear;
the torque transmitting device includes:
a first clutch that connects the first carrier with the second carrier;
a second clutch that connects the first carrier with the second sun gear;
a third clutch that connects the first carrier with the second ring gear;
a fourth clutch connecting the input shaft with the third carrier;
a fifth clutch connecting the input shaft with the third sun gear;
a first brake connected to the third ring gear;
a second brake connected to the fourth sun gear;
wherein two combinations of the first clutch, the second clutch, the third clutch, the fourth clutch, the fifth clutch, the first brake and the second brake are selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft and the output shaft.
Further, 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 planet carrier through the first clutch, the first planet carrier is connected with the second sun gear through the second clutch, the first planet carrier is connected with the second gear ring through the third clutch, the input shaft is connected with the third planet carrier through the fourth clutch, and the input shaft is connected with the third sun gear through the fifth clutch.
Further, the transmission housing is connected to the third ring gear through the first brake, and the transmission housing is connected to the fourth sun gear through the second brake.
Further, the thirteen gear transmission ratios of the thirteen-gear planetary transmission are nine speed reduction gears, one direct gear and three overdrive gears respectively.
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 brake;
establishing a three-speed gear ratio between the input shaft and the output shaft by engaging the third clutch and the second brake;
establishing a fourth gear ratio between the input shaft and the output shaft by engaging the first clutch and the third clutch;
establishing a five-speed gear ratio between the input shaft and the output shaft by engaging the third clutch and the first brake;
establishing a six-speed gear ratio between the input shaft and the output shaft by engaging the third clutch and the fifth clutch;
establishing a seven speed ratio between the input shaft and the output shaft by engaging the fifth clutch and the first brake;
establishing an eight speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the first clutch;
establishing a nine speed gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the second clutch;
establishing a ten speed ratio between the input shaft and the output shaft by engaging the fifth clutch and the fourth clutch;
establishing an eleven-speed gear ratio between the input shaft and the output shaft by engaging the second clutch and the fourth clutch;
establishing a twelve speed transmission ratio between the input shaft and the output shaft by engaging the first clutch and the fourth clutch;
a thirteenth gear ratio is established between the input shaft and the output shaft by engaging the first brake and the fourth clutch.
Further, a reverse gear ratio is established between the input shaft and the output shaft by engaging the first brake and the second clutch.
Further, the first clutch, the second clutch, the third clutch, the fourth clutch and the fifth clutch are all multi-plate wet clutches or jaw clutches. .
Further, the first brake and the second brake are both a multi-plate wet brake or a drum brake.
Further, the first brake and the second brake are each fixed to the transmission housing.
Compared with the prior art, the technical scheme provided by the invention has the beneficial effects that:
(1) The thirteenth-gear planetary gear transmission provided by the invention comprises four planetary gear row structures which are sequentially arranged along the direction from an input shaft to an output shaft; clutches in the torque transfer device are connected with an input shaft and a planetary gear train, brakes in the torque transfer device are connected with a transmission shell and the planetary gear train, two combinations of the clutches and the brakes are selectively engaged, thirteen forward speed ratios and one reverse speed ratio are established between the input shaft and an output shaft, the transmission ratios of the gears are respectively 11.67, 7.37, 4.84, 3.85, 2.76, 2.43, 2.09, 1.63, 1.32, 1.0, 0.90, 0.77, 0.72, -4.69, the overdrive step ratio is small, and gear shifting is more stable during high-speed running;
(2) The thirteenth-gear planetary gear transmission provided by the invention adopts a single planetary gear planetary row for transmission, the four planetary gear rows have simple and compact structure and small volume, and the common simpson is combined with other planetary rows, so that the manufacturing process is mature;
(3) The thirteen-gear planetary gear transmission provided by the invention has the advantages that the number of torque transmission components is small, seven torque transmission components are adopted, and the control difficulty and the corresponding volume of the transmission are reduced to a certain extent;
(4) The control of each gear of the thirteen-gear planetary gear transmission provided by the invention only needs to combine two torque transmission members (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.
Drawings
FIG. 1 is a schematic representation of a thirteenth planetary gear transmission of the present invention;
fig. 2 is a logic diagram of the operation of the thirteen-speed planetary transmission of the present invention.
In the figure: 1. an input shaft; 2. an output shaft; 3. a transmission housing; 11. a first ring gear; 12. a first planetary gear; 13. a first planet carrier; 14. a first sun gear; 21. a second ring gear; 22. a second planetary gear; 23. a second carrier; 24. a second sun gear; 31. a third ring gear; 32. a third planetary gear; 33. a third carrier; 34. a third sun gear; 41. a fourth ring gear; 42. a fourth planetary gear; 43. a fourth carrier; 44. a fourth sun gear; 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
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. The following presents a preferred one of a number of possible embodiments of the invention in order to provide a basic understanding of the invention, but is not intended to identify key or critical elements of the invention or to delineate the scope of the invention.
In the description of the present invention, unless explicitly stated and limited otherwise, the terms "mounted" and "connected" are to be interpreted broadly, for example, as being fixedly connected, detachably connected, integrally connected, mechanically connected, electrically connected, directly connected, indirectly connected through an intermediary, and communicating between the two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Referring to fig. 1, an embodiment of the present invention provides a thirteenth-gear planetary transmission including a transmission housing 3, and an input shaft 1, an output shaft 2, a planetary gear row group, and a torque transmitting device mounted inside the transmission housing 3.
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 that are installed in order along the direction of the input shaft 1 to the output shaft 2:
the first planetary gear row is composed of a first sun gear 14, a first planet carrier 13, a first planet gear 12 and a first gear ring 11, the first sun gear 14 and the first planet gear 12 are in external engagement transmission, the first planet gear 12 and the first gear ring 11 are in internal engagement transmission, and the first planet 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 composed of a third gear ring 41, a third planetary gear 42, a third planetary carrier 43 and a third sun gear 44, the third sun gear 44 and the third planetary gear 42 are in external engagement transmission, the third planetary gear 42 and the third gear ring 41 are in internal engagement transmission, and the third planetary gear 42 is rotatably supported on the third planetary carrier 43 through a rolling or sliding bearing.
The first gear ring 11 is fixedly connected with the transmission housing 3, the first sun gear 14 is fixedly connected with the input shaft 1, the second planet carrier 23 is fixedly connected with the third gear ring 31, the second gear ring 21 is fixedly connected with the third planet carrier 33, the third planet carrier 33 is fixedly connected with the fourth gear ring 41, and the third sun gear 34 is fixedly connected with the fourth sun gear 44.
The torque transmitting devices include five clutches and two brakes. The five clutches are a first clutch C1, a second clutch C2, a third clutch C3, a fourth clutch C4 and a fifth clutch C5 respectively, and the two brakes are a first brake B1 and a second brake B2 respectively.
Wherein a first clutch C1 connects the first carrier 13 with the second carrier 23;
a second clutch C2 that connects the first carrier 13 with the second sun gear 24;
a third clutch C3 that connects the first carrier 13 with the second ring gear 21;
a fourth clutch C4 that connects the input shaft 1 with the third carrier 33;
a fifth clutch C5 that connects the input shaft 1 with the third sun gear 34;
a first brake B1 connected to the third ring gear 31;
a second brake B2 connected to the fourth sun gear 44;
two combinations 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 B1 are selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft 1 and the output shaft 2.
In the present embodiment, the input shaft 1 is fixedly connected to the first sun gear 14, the output shaft 2 is connected to the fourth carrier 43, the first carrier 13 is connected to the second carrier 23 via the first clutch C1, the first carrier 13 is connected to the second sun gear 24 via the second clutch C2, the first carrier 13 is connected to the second ring gear 21 via the third clutch C3, the input shaft 1 is connected to the third carrier 33 via the fourth clutch C4, and the input shaft 1 is connected to the third sun gear 34 via the fifth clutch C5.
In this embodiment, the five clutches and two brakes are structurally characterized in the transmission as follows: the first clutch C1 is connected to the second carrier 23 and the third ring gear 31, the second clutch C2 is connected to the second sun gear 24, the third clutch C3 is connected to the second ring gear 21, the fourth clutch C4 is connected to the third carrier 33, and the fifth clutch C5 is connected to the third sun gear 34 and the fourth sun gear 44. The first brake B1 is connected to the second carrier 23 and the third ring gear 31, respectively; the second brake B2 is connected to the third sun gear 34 and the fourth sun gear 44.
The input shaft 1 can be directly connected with the fourth clutch C4 and the fifth clutch C5; the fourth clutch C4 and the fifth clutch C5 may each be an input member. In the transmission mechanism, the input shaft 1 is directly connected with the first sun gear 14, so that the first sun gear 14 always has power input during the whole transmission process. The input shaft 1 is connected to an engine through a torque converter, and power supplied from the engine is transmitted to the input shaft through the torque converter.
The output shaft 2 is connected to driving wheels of a vehicle (an automobile, a special vehicle, a construction machine) through a differential mechanism, and transmits the output power to the driving wheels of the vehicle.
In the embodiment, the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4 and the fifth clutch C5 are all wet multi-plate clutches or jaw clutches, when the driving plate and the driven plate of the clutches are pressed under the action of hydraulic pressure, the clutches are engaged and are in a working state, and at the moment, the movable members connected with the two ends of the clutches are engaged and have the same rotating speed; on the contrary, when the clutch is in a non-working state, the movable components connected with the two ends of the clutch are separated and have different rotating speeds.
In this embodiment, the first brake B1 and the second brake B2 are each a wet-type multi-disc brake or a drum brake for connecting the movable member and the transmission case, and when the brake is in an operating state, the movable member is engaged with the transmission case, the movable member cannot rotate, and the brake is in a braking state.
The invention establishes thirteen forward gears respectively including nine decelerating gears, one direct gear and three overdrive gears, and specifically comprises the following steps:
by engaging the second clutch C2 and the second brake B2, a first gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the first clutch C1 and the second brake B2, a second gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the third clutch C3 and the second brake B2, a three-speed gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the first clutch C1 and the third clutch C3, a four-speed gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the third clutch C3 and the first brake B1, a five-speed gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the third clutch C3 and the fifth clutch C5, a six-speed transmission ratio is established between the input shaft 1 and the output shaft 2;
by engaging the fifth clutch C5 and the first brake B1, a seven-speed gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the fifth clutch C5 and the first clutch C1, an eight-speed gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the fifth clutch C5 and the second clutch C2, a nine speed gear ratio is established between the input shaft 1 and the output shaft 2;
by engaging the fifth clutch C5 and the fourth clutch C4, a ten-speed transmission ratio is established between the input shaft 1 and the output shaft 2;
by engaging the second clutch C2 and the fourth clutch C4, an eleven-gear transmission ratio is established between the input shaft 1 and the output shaft 2;
by engaging the first clutch C1 and the fourth clutch C4, a twelve speed transmission ratio is established between the input shaft 1 and the output shaft 2;
by engaging the first brake B1 and the fourth clutch C4, a thirteenth gear ratio is established between the input shaft 1 and the output shaft 2.
The transmission of the present invention can also achieve reverse gear by engaging the first brake B1 and the second clutch C2 to establish a reverse gear ratio between the input shaft and the output shaft.
The gear ratio of the planetary transmission mechanism is the ratio of the rotational speeds of the input member to the output member. The planetary transmission of the present invention can achieve 14 different gear ratios, namely 14 gears, including 13 forward gears and 1 reverse gear. Each gear can be realized by controlling the working states of the clutch and the brake.
Referring to fig. 1 and the operating logic table shown in fig. 2, it is 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. In the present embodiment, k1= 2.8462, k2= -1.6957, k3= -1.9091, k4= -3.875. The specific implementation process of each gear ratio of the transmission is as follows:
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 sun gear 44 with the transmission case 3, rotation of the fourth sun gear 44 relative to the transmission case 3 is prevented. The second clutch C2 is engaged to connect the first carrier 13 and the second sun gear 24 for rotation together. Thus, a first gear ratio is established between the input shaft 1 and the output shaft 2, the first gear ratio being 11.67.
By engaging the first clutch C1 and the second brake B2 to establish a second gear ratio between the input shaft 1 and the output shaft 2, specifically, the second brake B2 is engaged to connect the fourth sun gear 44 with the transmission case 3, rotation of the fourth sun gear 44 relative to the transmission case 3 is prevented. The first clutch C1 is engaged to connect the first carrier 13 and the second carrier 23 for rotation together. Thus, a second gear ratio of 7.37 and a step ratio of 1.58 is established between the input shaft 1 and the output shaft 2.
By engaging the third clutch C3 and the second brake B2 to establish a three-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the second brake B2 is engaged to connect the fourth sun gear 44 with the transmission case 3, rotation of the fourth sun gear 44 relative to the transmission case 3 is prevented. The third clutch C3 is engaged to connect the first carrier 13 and the second ring gear 21 for rotation together. Thus, a three-speed gear ratio is established between the input shaft 1 and the output shaft 2, the three-speed gear ratio being 4.84 and the ratio step being 1.52.
By engaging the third clutch C3 and the first clutch C1 to establish a four-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first clutch C1 is engaged to connect the first carrier 13 and the second carrier 23 for rotation together. The third clutch C3 is engaged to connect the first carrier 13 and the second ring gear 21 for rotation together. Thus, a four-speed gear ratio of 3.85 and a step ratio of 1.26 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 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 second carrier 23 with the transmission housing 3, rotation of the second carrier 23 relative to the transmission housing 3 is prevented. The third clutch C3 is engaged to connect the first carrier 13 and the second ring gear 21 for rotation together. Thus, a five-speed gear ratio of 2.76 and a step-up gear ratio of 1.39 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 six-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 34 for rotation together. The third clutch C3 is engaged to connect the first carrier 13 and the second ring gear 21 for rotation together. Thus, a six-speed gear ratio of 2.43 and a step-up of 1.14 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 seven-speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first brake B1 is engaged to connect the second carrier 23 with the transmission housing 3, rotation of the second carrier 23 relative to the transmission housing 3 is prevented. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for rotation together. Thus, a seven-speed transmission ratio of 2.09 and a step-ratio of 1.16 is established between the input shaft 1 and the output shaft 2.
By engaging the fifth clutch C5 and the first clutch C1 to establish an eight speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the first clutch C1 is engaged to connect the first carrier 13 and the second carrier 23 for rotation together. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for rotation together. Thus, an eight-gear transmission ratio is established between the input shaft (1) and the output shaft (2), the eight-gear transmission ratio is 1.63, and the speed ratio step is 1.28.
By engaging the fifth clutch C5 and the second clutch C2 to establish a nine speed gear ratio between the input shaft 1 and the output shaft 2, specifically, the second clutch C2 is engaged to connect the first carrier 13 and the second sun gear 24 for rotation together. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for rotation together. Thus, a nine speed gear ratio of 1.32 and a step ratio of 1.23 is established between the input shaft 1 and the output shaft 2.
By engaging the fifth clutch C5 and the fourth clutch C4 to establish a ten-speed transmission ratio between the input shaft 1 and the output shaft 2, specifically, the fourth clutch C4 is engaged to connect the input shaft 1 and the third carrier 33 for rotation together. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for rotation together. Thus, a ten-speed transmission ratio of 1.0 and a step-up ratio of 1.32 is established between the input shaft 1 and the output shaft 2.
By engaging the second clutch C2 and the fourth clutch C4 to establish an eleven-gear transmission ratio between the input shaft 1 and the output shaft 2, specifically, the fourth clutch C4 is engaged to connect the input shaft 1 and the third carrier 33 for rotation together. The second clutch C2 is engaged to connect the first carrier 13 and the second sun gear 24 for rotation together. Thus, an eleven-gear transmission ratio of 0.90 and a step-ratio of 1.11 is established between the input shaft 1 and the output shaft 2.
By engaging the first clutch C1 and the fourth clutch C4 to establish a twelve speed transmission ratio between the input shaft 1 and the output shaft 2, specifically, the fourth clutch C4 is engaged to connect the input shaft 1 and the third carrier 33 for rotation together. The first clutch C1 is engaged to connect the first carrier 13 and the second carrier 23 for rotation together. Thus, a twelve speed transmission ratio of 0.77 is established between the input shaft 1 and the output shaft 2, with a step-up of 1.16.
By engaging the first brake B1 and the fourth clutch C4 to establish a thirteen gear ratio between the input shaft 1 and the output shaft 2, specifically, the fourth clutch C4 is engaged to connect the input shaft 1 and the third carrier 33 for rotation together. The first brake B1 is engaged to connect the second carrier 23 with the transmission housing 3, preventing rotation of the second carrier 23 relative to the transmission housing 3. Thus, a gear ratio of thirteen gears is established between the input shaft 1 and the output shaft 2, the gear ratio of thirteen gears being 0.72 and the step ratio being 1.08.
By engaging the first brake B1 and the second clutch C2 to establish a reverse gear ratio between the input shaft 1 and the output shaft 2, specifically, the second clutch C2 is engaged to connect the first carrier 13 and the second sun gear 24 for rotation together. The first brake B1 is engaged to connect the second carrier 23 with the transmission housing 3, preventing rotation of the second carrier 23 relative to the transmission housing 3. Thus, a reverse gear ratio of 4.69 is established between the input shaft 1 and the output shaft 2.
In the present embodiment, 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.
The clutch and brake working states are easy to control, and when each gear is switched, only two control elements are needed to work, so that the control difficulty of the transmission is reduced. The step ratio between each gear is stable, and gear shifting is smooth.
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 (9)

1. The utility model provides a thirteen keep off planetary gear transmission, includes the derailleur shell and installs in inside input shaft, output shaft, planetary gear row group and the torque transmission device of derailleur shell, planetary gear row group is including following input shaft (1) to output shaft (2) direction installs first planetary gear row, second planetary gear row, third planetary gear row and fourth planetary gear row in proper order, its characterized in that:
the first planetary gear row consists of a first sun gear (14), a first planet carrier (13), a first planet gear (12) and a first gear ring (11), wherein the first sun gear (14) and the first planet gear (12) are in external engagement transmission, the first planet gear (12) and the first gear ring (11) are in internal engagement transmission, and the first planet gear (12) is rotatably supported on the first planet carrier (13);
the second planetary gear row consists of a second sun gear (24), a second planet carrier (23), a second planet gear (22) and a second gear ring (21), wherein the second sun gear (24) and the second planet gear (22) are in external engagement transmission, the second planet gear (22) and the second gear ring (21) are in internal engagement transmission, and the second planet gear (22) is rotatably supported on the second planet carrier (23);
the third planetary gear row consists of a third sun gear (34), a third planet carrier (33), a third planet gear (32) and a third gear ring (31), wherein the third sun gear (34) and the third planet gear (32) are in external engagement transmission, the third planet gear (32) and the third gear ring (31) are in internal engagement transmission, and the third planet gear (32) is rotatably supported on the third planet carrier (33);
the fourth planetary gear row consists of a fourth sun gear (44), a fourth planet carrier (43), a fourth planet gear (42) and a fourth gear ring (41), wherein the fourth sun gear (44) and the fourth planet gear (42) are in external engagement transmission, the fourth planet gear (42) and the fourth gear ring (41) are in internal engagement transmission, and the fourth planet gear (42) is rotatably supported on the fourth planet carrier (43);
the first gear ring (11) is fixedly connected with the transmission shell (3), the first sun gear (14) is fixedly connected with the input shaft (1), the second planet carrier (23) is fixedly connected with the third gear ring (31), the second gear ring (21) is fixedly connected with the third planet carrier (33), the third planet carrier (33) is fixedly connected with the fourth gear ring (41), and the third sun gear (34) is fixedly connected with the fourth sun gear (44);
the torque transmitting device includes:
a first clutch (C1) that connects the first carrier (13) with the second carrier (23);
a second clutch (C2) that connects the first carrier (13) with the second sun gear (24);
a third clutch (C3) that connects the first carrier (13) with the second ring gear (21);
a fourth clutch (C4) that connects the input shaft (1) with the third carrier (33);
a fifth clutch (C5) that connects the input shaft (1) with the third sun gear (34);
a first brake (B1) connected to the third ring gear (31);
a second brake (B2) connected to the fourth sun gear (44);
wherein two combinations 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 selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft and the output shaft.
2. Thirteenth gear planetary transmission according to claim 1, characterised in that the input shaft (1) is fixedly connected with the first sun gear (14), the output shaft (2) is connected with the fourth planet carrier (43), the first planet carrier (13) is connected with the second planet carrier (23) via the first clutch (C1), the first planet carrier (13) is connected with the second sun gear (24) via the second clutch (C2), the first planet carrier (13) is connected with the second ring gear (21) via the third clutch (C3), the input shaft (1) is connected with the third planet carrier (33) via the fourth clutch (C4), and the input shaft (1) is connected with the third sun gear (34) via the fifth clutch (C5).
3. A thirteenth gear planetary transmission as claimed in claim 2, characterised in that said transmission housing (3) is connected to said third ring gear (31) by means of said first brake (B1), said transmission housing (3) being connected to said fourth sun gear (44) by means of said second brake (B2).
4. A thirteen-gear planetary transmission according to claim 3, wherein the thirteen-gear transmission has thirteen gear ratios of nine gear steps, one direct gear and three overdrive gears, respectively.
5. The thirteenth gear planetary transmission of claim 4 wherein:
-establishing a first gear ratio between the input shaft (1) and the output shaft (2) by engaging the second clutch (C2) and the second brake (B2);
-establishing a second gear ratio between the input shaft (1) and the output shaft (2) by engaging the first clutch (C1) and the second brake (B2);
-establishing a three-gear transmission ratio between the input shaft (1) and the output shaft (2) by engaging the third clutch (C3) and the second brake (B2);
-establishing a fourth gear ratio between the input shaft (1) and the output shaft (2) by engaging the first clutch (C1) and the third clutch (C3);
-establishing a five-gear transmission ratio between the input shaft (1) and the output shaft (2) by engaging the third clutch (C3) and the first brake (B1);
-establishing a six-speed transmission ratio between the input shaft (1) and the output shaft (2) by engaging the third clutch (C3) and the fifth clutch (C5);
-establishing a seven-speed transmission ratio between the input shaft (1) and the output shaft (2) by engaging the fifth clutch (C5) and the first brake (B1);
-establishing an eight speed transmission ratio between the input shaft (1) and the output shaft (2) by engaging the fifth clutch (C5) and the first clutch (C1);
-establishing a nine speed transmission ratio between the input shaft (1) and the output shaft (2) by engaging the fifth clutch (C5) and the second clutch (C2);
-establishing a ten-speed transmission ratio between the input shaft (1) and the output shaft (2) by engaging the fifth clutch (C5) and the fourth clutch (C4);
by engaging the second clutch (C2) and the fourth clutch (C4) to establish an eleven gear transmission ratio between the input shaft (1) and the output shaft (2);
-establishing a twelve speed transmission ratio between the input shaft (1) and the output shaft (2) by engaging the first clutch (C1) and the fourth clutch (C4);
by engaging the first brake (B1) and the fourth clutch (C4), a thirteen gear ratio is established between the input shaft (1) and the output shaft (2).
6. The thirteenth gear planetary transmission of claim 5 wherein:
by engaging the first brake (B1) and the second clutch (C2), a reverse gear ratio is established between the input shaft (1) and the output shaft (2).
7. The thirteenth gear planetary transmission according to claim 1, characterized in that the first clutch (C1), the second clutch (C2), the third clutch (C3), the fourth clutch (C4) and the fifth clutch (C5) are all multi-plate wet clutches or dog clutches.
8. A thirteenth gear planetary transmission according to claim 1 characterised in that the first brake (B1) and the second brake (B2) are each a multi-plate wet brake or a drum brake.
9. A thirteenth gear planetary transmission as claimed in claim 1, characterised in that said first brake (B1) and said second brake (B2) are both fixed to said transmission housing (3).
CN202310608833.5A 2023-05-24 2023-05-24 Thirteen-gear planetary gear transmission Pending CN116608244A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310608833.5A CN116608244A (en) 2023-05-24 2023-05-24 Thirteen-gear planetary gear transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310608833.5A CN116608244A (en) 2023-05-24 2023-05-24 Thirteen-gear planetary gear transmission

Publications (1)

Publication Number Publication Date
CN116608244A true CN116608244A (en) 2023-08-18

Family

ID=87677824

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202310608833.5A Pending CN116608244A (en) 2023-05-24 2023-05-24 Thirteen-gear planetary gear transmission

Country Status (1)

Country Link
CN (1) CN116608244A (en)

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