CN106402293B - Eight-gear planetary automatic transmission - Google Patents
Eight-gear planetary automatic transmission Download PDFInfo
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- CN106402293B CN106402293B CN201610871967.6A CN201610871967A CN106402293B CN 106402293 B CN106402293 B CN 106402293B CN 201610871967 A CN201610871967 A CN 201610871967A CN 106402293 B CN106402293 B CN 106402293B
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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
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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
- F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set 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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
- F16H2200/0086—Transmissions for multiple ratios characterised by the number of reverse speeds the gear ratios comprising two reverse 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
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides an eight-gear planetary automatic transmission which comprises a planetary row, an input member, an output member, a connecting member, a brake and a clutch, wherein the input member and the output member are arranged at two ends of the planetary row and are respectively connected with an input shaft and an output shaft. The number of the planetary rows is four, the number of the connecting members is five, the number of the brakes is four, and the number of the clutches is two. Therefore, the planetary automatic transmission realizes eight forward gears and two reverse gears, the step ratios of adjacent gears between five forward gears and eight forward gears are all smaller than 1.25, the radial size is reduced by 20mm, the weight is reduced by 25.8kg, and four planetary rows are all single-star simple planetary rows.
Description
The technical field is as follows:
the invention belongs to the technical field of vehicle transmission, and particularly relates to an eight-gear planetary automatic transmission for a road vehicle.
Background art:
as a planetary automatic transmission for a road wheel type vehicle, power of an internal combustion engine or the like is transmitted to an input shaft of the planetary automatic transmission through a torque converter, and after shifting according to a current gear, the power is output from an output shaft and transmitted to left and right drive wheels through a differential. The transmission is mostly composed of a plurality of planetary rows, brakes and clutches. At present, the prior art with patent application publication numbers CN20120402156, publication dates 2013, 02/06, and a name of "a seven-gear planetary automatic transmission" shows an automatic speed change mode with large step size, large radial size, heavy weight and poor vehicle economy between adjacent high-gear gears, and therefore a planetary automatic transmission with small transmission ratio, small radial size and light weight is required to be found, and is more suitable for road wheeled vehicles.
The invention content is as follows:
the invention aims to provide an eight-gear planetary automatic transmission for a road wheeled vehicle, which utilizes four planetary rows, two clutches and four brakes to realize eight forward gears and two reverse gears, wherein three forward high gears are overdrive gears, the step ratio between adjacent gears of the high gears is small, the radial size is small, the weight is light, and the high economic requirement of the road wheeled vehicle can be met.
The invention provides an eight-gear planetary automatic transmission, which comprises planetary rows, an input member 1, an output member 2, transmission members, brakes and clutches, wherein the input member 1 and the output member 2 are arranged at two ends of the planetary rows and are respectively connected with an input shaft and an output shaft, the four planetary rows are respectively a planetary row PGS1, a planetary row PGS2, a planetary row PGS3 and a planetary row PGS4, the five transmission members are respectively a connecting member 3, a connecting member 4, a connecting member 5, a connecting member 6 and a connecting member 7, the four brakes are respectively a brake B1, a brake B2, a brake B3 and a brake B4, the two clutches are respectively a clutch C1 and a clutch C2, and the eight-gear planetary automatic transmission is characterized in that a sun gear S1, a planet carrier CA1 and a ring gear R1 of the planetary row PGS1 are respectively connected with the input member 1, the connecting member 4 and the connecting member 3;
the sun gear S2, carrier CA2 and ring gear R2 of the row PGS2 are connected with the input member 1, connecting member 5 and connecting member 4, respectively;
the sun gear S3, carrier CA3 and ring gear R3 of the planetary row PGS3 are connected with the connecting member 7, connecting member 6 and connecting member 5, respectively;
the sun gear S4, carrier CA4 and ring gear R4 of the row PGS4 are connected to the connecting member 5, connecting member 6 and output member 2, respectively;
the input member 1 is connected with the sun gear S1 of planetary row PGS1, the sun gear S2 of planetary row PGS2, the inner hub of clutch C1 and the outer hub of clutch C2;
the output member 2 is connected with the ring gear R4 of the planet row PGS 4;
the connecting member 3 is connected with the ring gear R1 of the planet row PGS1 and the inner hub of the brake B1;
the connecting member 4 is connected with the carrier CA1 of the row PGS1, the ring gear R2 of the row PGS2 and the inner hub of the brake B2;
the connecting member 5 is connected with carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B3 and the sun gear S4 of row PGS 4;
the connecting member 6 is connected with carrier CA3 of planetary row PGS3, carrier CA4 of planetary row PGS4, the inner hub of brake B4 and the inner hub of clutch C2;
the connecting member 7 is connected with the sun gear S3 of the planetary row PGS3 and the outer hub of the clutch C1;
the brake B1 brakes the connecting member 3;
the brake B2 brakes the connecting member 4;
the brake B3 brakes the connecting member 5;
the brake B4 brakes the connecting member 6;
the clutch C1 connects the input member 1 with the connecting member 7;
the clutch C2 connects the input member 1 with the connecting member 6.
The first preferred scheme is that the planet rows are all simple planet rows.
According to a second preferred scheme, the planet row comprises a sun gear, a planet carrier and a gear ring;
the input shaft is a turbine shaft of a hydraulic torque converter, and the power of an engine is transmitted to the planetary automatic transmission through the hydraulic torque converter;
the brake and the clutch are multi-plate friction control members, and are combined by pressurizing a piston driven by hydraulic oil.
In summary, compared with the closest technical solution, the technical solution provided by the present invention has the following excellent effects:
1. the invention provides an eight-gear planetary automatic transmission which adopts a scheme of four planetary rows, four brakes and two clutches to realize 8 forward gears and 2 reverse gears.
2. According to the eight-gear planetary automatic transmission provided by the invention, the step ratios of adjacent gears between a third forward gear and an eighth forward gear are all smaller than 1.36, the radial size is reduced by 20mm, and the weight is reduced by 25.8 kg.
3. The eight-gear planetary automatic transmission provided by the invention can enable a vehicle to obtain better economy.
Drawings
FIG. 1 is a schematic diagram of the connection of the components of an eight speed planetary automatic transmission according to the present invention.
PGS 1-PGS 4 are four planet rows; S1-S4 are four sun gears; CA 1-CA 4 are four planet carriers; R1-R4 are four gear rings; B1-B4 are four brakes; C1-C2 are two clutches; 1 is an input member; 2 is an output member; 3-7 are five connecting components.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions in the embodiments of the present invention are clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all, embodiments in the present invention. All other embodiments obtained by the person skilled in the art based on the embodiments of the present invention without any inventive step are within the scope of the present invention. The technical scheme provided by the invention is explained in detail in the following with reference to the attached drawings.
Example one
As shown in fig. 1, the present invention provides an eight-speed planetary automatic transmission which is suitable for road wheeled vehicles. Wherein the planetary rows are arranged in a sequence, the planetary rows are connected by a connecting member, and the input shaft is connected to an input member 1, typically a turbine shaft of a torque converter, for transmitting power of an engine to the planetary automatic transmission through the torque converter. The output shaft is connected with the output member 2, and power is transmitted to the front and rear axles or the left and right driving wheels through a transfer case or a differential. The planetary automatic transmission is completely symmetrical with respect to the rotation center, and the lower half of the rotation center is omitted in fig. 1, and will not be described below.
As shown in fig. 1, an eight speed planetary automatic transmission includes a planetary row, an input member 1 and an output member 2 mounted at both ends thereof to be connected to an input shaft and an output shaft, respectively, a connecting member, a brake and a clutch, characterized in that the planetary row includes a planetary row PGS1, a planetary row PGS2, a planetary row PGS3 and a planetary row PGS 4; the connecting members include a connecting member 3, a connecting member 4, a connecting member 5, a connecting member 6, and a connecting member 7; the brake comprises a brake B1, a brake B2, a brake B3 and a brake B4; the clutches include clutch C1 and clutch C2;
each planet row comprises a sun gear, a planet carrier and a gear ring.
The planetary row PGS1 includes three rotary members, i.e., a sun gear S1, a carrier CA1 and a ring gear R1, which are connected to the input member 1, the connecting member 4 and the connecting member 3, respectively, the sun gear S1 is connected to the input member 1 to input power, and the ring gear R1 is braked by a brake B1 so that the carrier CA1 acts as an intermediate output member to decelerate the rotational speed of the input member 1 and output it.
The planetary row PGS2 includes three rotary members, i.e., a sun gear S2, a carrier CA2, and a ring gear R2, which are connected to the input member 1, the connecting member 5, and the connecting member 4, respectively, and can brake the ring gear R2 via a brake B4 so that the carrier CA2 acts as an intermediate output member to decelerate the rotational speed of the input member 1 and output it.
Planetary row PGS3 includes three rotary elements, i.e., sun gear S3, carrier CA3 and ring gear R3, and is connected to connecting member 7, connecting member 6 and connecting member 5, respectively, and can output the rotation speed of sun gear S3 at a reduced speed by braking ring gear R3 with brake B3 so that carrier CA3 serves as an output element, or output the rotation speed of sun gear S3 in the reverse direction by braking carrier CA3 with brake B4 so that ring gear R3 serves as an output element.
Planetary row PGS4 includes three rotary elements, i.e., a sun gear S4, a carrier CA4, and a ring gear R4, and is connected to connecting member 5, connecting member 6, and output member 2, respectively, and can output the rotational speed of carrier CA4 at an increased speed by braking sun gear S4 with brake B5 so that ring gear R4 serves as the output element, or output the rotational speed of sun gear S4 at a decreased speed and in the reverse direction by braking carrier CA4 with brake B4 so that ring gear R4 serves as the output element.
The input member 1 is connected with the sun gear S1 of planetary row PGS1, the sun gear S2 of planetary row PGS2, the inner hub of clutch C1 and the outer hub of clutch C2;
the output member 2 is connected with the ring gear R4 of the planet row PGS 4;
the connecting member 3 is connected with the ring gear R1 of the planet row PGS1 and the inner hub of the brake B1;
the connecting member 4 is connected with the carrier CA1 of the row PGS1, the ring gear R2 of the row PGS2 and the inner hub of the brake B2;
the connecting member 5 is connected with carrier CA2 of row PGS2, ring gear R3 of row PGS3, the inner hub of brake B3 and the sun gear S4 of row PGS 4;
the connecting member 6 is connected with carrier CA3 of planetary row PGS3, carrier CA4 of planetary row PGS4, the inner hub of brake B4 and the inner hub of clutch C2;
the connecting member 7 is connected with the sun gear S3 of the planetary row PGS3 and the outer hub of the clutch C1;
the brake B1 is used for braking the connecting member 3;
the brake B2 is used for braking the connecting member 4;
the brake B3 is used for braking the connecting member 5;
the brake B4 is used for braking the connecting member 6;
the clutch C1 connects the input member 1 with the connecting member 7;
the clutch C2 connects the input member 1 with the connecting member 6;
the planet rows are all simple planet rows.
The brakes B1-B4, the clutches C1 and C2 are generally multi-plate friction operating members, and are pressurized by driving pistons with hydraulic oil. The operating scheme for each gear is implemented as shown in table 1.
TABLE 1 eight-gear planetary automatic transmission realization mode and corresponding transmission ratio and step ratio schematic table
O means handling member engagement
Referring now to fig. 1 and table 1, an example of the present invention will be described in detail, wherein the transmission ratio is the ratio of the input shaft speed to the output shaft speed, and the k value of the planetary row is the ratio of the number of teeth of the ring gear to the number of teeth of the sun gear of the planetary row.
When the clutch C1 and brake B4 are engaged, the input member 1 and the coupling member 7 rotate as a unit, and the coupling member 6 brakes to achieve first gear "1 st".
When clutch C1 and brake B3 are engaged, the input member 1 and connecting member 7 rotate as a unit and connecting member 5 brakes to achieve second gear "2 nd".
When clutch C1 and brake B2 are engaged, the input member 1 and connecting member 7 rotate as a unit and connecting member 4 brakes to achieve third gear "3 rd".
When clutch C1 and brake B1 are engaged, the input member 1 and connecting member 7 rotate in unison and connecting member 3 brakes to achieve a ratio of "4 th" in fourth gear.
When clutch C1 and clutch C2 are engaged, the input member 1 and connecting member 7 rotate as a unit and the input member 1 and connecting member 6 rotate as a unit, achieving fifth gear "5 th".
When clutch C2 and brake B1 are engaged, the input member 1 and the connecting member 6 rotate as a unit and the connecting member 3 brakes to achieve sixth gear "6 th".
When clutch C2 and brake B2 are engaged, the input member 1 and connecting member 6 rotate as a unit and connecting member 4 brakes to achieve seven speed "7 th".
When clutch C2 and brake B3 are engaged, the input member 1 and connecting member 6 rotate as a unit and connecting member 5 brakes to achieve eighth gear "8 th".
When brake B2 and brake B4 are engaged, connecting member 4 and connecting member 6 brake, achieving reverse first gear "Rev 1".
When brake B1 and brake B4 are engaged, connecting member 3 and connecting member 6 brake, achieving reverse second gear "Rev 2".
The gear ratios are determined by the k values of the four planetary rows. For example, when k1 is 1.712, k3 is 3.696, and k4 is 1.640, the gear ratios of the gears shown in table 1 can be obtained, the step ratios of the gear ratios of adjacent gears between 5 and 8 are all smaller than 1.25, meanwhile, the total gear ratio range 6.061/0.621 of the forward gear reaches 9.757, and by the structural design, compared with a seven-gear planetary automatic transmission CN20120402156 product: the radial dimension is reduced by 20mm, and the weight is reduced by 25.8kg, so that the vehicle has better economy.
The four planet rows PGS 1-PGS 4 of the eight-gear planetary automatic transmission are all single-planet simple planet rows.
Finally, it should be noted that: the above embodiments are only used for illustrating the technical solutions of the present application and not for limiting the protection scope thereof, and although the present application is described in detail with reference to the above embodiments, those of ordinary skill in the art should understand that: numerous variations, modifications, and equivalents will occur to those skilled in the art upon reading the present application and are within the scope of the claims appended hereto.
Claims (2)
1. An eight-gear planetary automatic transmission comprises a planetary row, an input member (1) and an output member (2) which are arranged at two ends and respectively connected with an input shaft and an output shaft, a transmission member, a brake and a clutch, four planet rows, respectively planet row PGS1, planet row PGS2, planet row PGS3 and planet row PGS4, five transmission members, respectively a first connecting member (3), a second connecting member (4), a third connecting member (5), a fourth connecting member (6) and a fifth connecting member (7), the brake comprises four brakes which are a brake B1, a brake B2, a brake B3 and a brake B4 respectively, the clutch comprises two clutches which are a clutch C1 and a clutch C2 respectively, characterized in that the sun gear S1, the planet carrier CA1 and the ring gear R1 of the planet row PGS1 are connected to the input member (1), the second connecting member (4) and the first connecting member (3), respectively;
the sun gear S2, carrier CA2 and ring gear R2 of the planetary row PGS2 are connected with the input member (1), third connecting member (5) and second connecting member (4), respectively;
the sun gear S3, the carrier CA3 and the ring gear R3 of the planetary row PGS3 are connected with the fifth connecting member (7), the fourth connecting member (6) and the third connecting member (5), respectively;
the sun gear S4, carrier CA4 and ring gear R4 of the planetary row PGS4 are connected with the third connecting member (5), fourth connecting member (6) and output member (2), respectively;
the input member (1) is connected with the sun gear S1 of the planetary row PGS1, the sun gear S2 of the planetary row PGS2, the inner hub of the clutch C1 and the outer hub of the clutch C2;
the output member (2) is connected with the ring gear R4 of the planet row PGS 4;
the first connecting member (3) is connected with the ring gear R1 of the planet row PGS1 and the inner hub of the brake B1;
the second connecting member (4) is connected with the carrier CA1 of the planet row PGS1, the ring gear R2 of the planet row PGS2 and the inner hub of the brake B2;
said third connecting member (5) is connected to carrier CA2 of row PGS2, to ring gear R3 of row PGS3, to the inner hub of brake B3 and to the sun gear S4 of row PGS 4;
the fourth connecting member (6) is connected with the carrier CA3 of the planet row PGS3, the carrier CA4 of the planet row PGS4, the inner hub of the brake B4 and the inner hub of the clutch C2;
the fifth connecting member (7) is connected with the sun gear S3 of the planetary row PGS3 and the outer hub of the clutch C1;
the brake B1 brakes the first connecting member (3);
the brake B2 brakes the second connecting member (4);
the brake B3 brakes the third connecting member (5);
the brake B4 brakes the fourth connecting member (6);
the clutch C1 connects the input member (1) and a fifth connecting member (7);
the clutch C2 connects the input member (1) and the fourth connecting member (6);
the planet row comprises a sun gear, a planet carrier and a gear ring;
the input shaft is a turbine shaft of a hydraulic torque converter, and the power of an engine is transmitted to the planetary automatic transmission through the hydraulic torque converter;
the brake and the clutch are multi-plate friction control members, and are combined by pressurizing a piston driven by hydraulic oil.
2. The eight speed planetary automatic transmission as in claim 1, wherein the planetary rows are simple planetary rows of single stars.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610871967.6A CN106402293B (en) | 2016-09-30 | 2016-09-30 | Eight-gear planetary automatic transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610871967.6A CN106402293B (en) | 2016-09-30 | 2016-09-30 | Eight-gear planetary automatic transmission |
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| CN106402293A CN106402293A (en) | 2017-02-15 |
| CN106402293B true CN106402293B (en) | 2021-02-23 |
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Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107606080B (en) * | 2017-10-13 | 2023-11-14 | 中南林业科技大学 | Seven-gear electric control mechanical planetary automatic transmission for automatic gearbox |
| CN109854690A (en) * | 2018-12-21 | 2019-06-07 | 中国北方车辆研究所 | A kind of eight-gear planetary automatic speed changer |
| CN110439975A (en) * | 2019-07-15 | 2019-11-12 | 中国北方车辆研究所 | A kind of eight-gear planetary automatic speed changer |
| CN113108040A (en) * | 2021-03-29 | 2021-07-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission of mining truck integrating hydraulic retarber arranged in parallel shafts |
| CN113175506B (en) * | 2021-04-20 | 2023-10-31 | 中国北方车辆研究所 | Eight-gear compound planetary transmission mechanism with three degrees of freedom |
| CN112984060A (en) * | 2021-04-27 | 2021-06-18 | 北京航空航天大学 | Eight-front two-reverse planetary gear automatic transmission |
| CN113251119A (en) * | 2021-06-03 | 2021-08-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
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| JPS5845612B2 (en) * | 1975-12-25 | 1983-10-11 | アイシンセイキ カブシキガイシヤ | Hensokuuchi |
| JP2008215393A (en) * | 2007-02-28 | 2008-09-18 | Aisin Aw Co Ltd | Automatic transmission |
| CN102221076B (en) * | 2011-05-12 | 2013-05-08 | 贵州凯星液力传动机械有限公司 | Multi-gear planet type hydraulic transmission driving mechanism |
| US8915819B2 (en) * | 2012-03-05 | 2014-12-23 | Gm Global Technology Operations, Llc | Multi-speed planetary gear set transmission |
| CN103591248B (en) * | 2013-11-12 | 2016-01-20 | 北京科技大学 | A kind of planetary automatic transmission |
| CN104565238B (en) * | 2014-12-26 | 2017-08-11 | 燕山大学 | A kind of 8 speed automatic transmissions |
| CN104595435B (en) * | 2014-12-26 | 2017-08-29 | 燕山大学 | Eight shift transmissions |
| CN105003633B (en) * | 2015-07-17 | 2017-11-07 | 中国地质大学（武汉） | A kind of shift transmission of modified eight |
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