CN110500389B - Nine-gear planetary automatic transmission - Google Patents
Nine-gear planetary automatic transmission Download PDFInfo
- Publication number
- CN110500389B CN110500389B CN201910633295.9A CN201910633295A CN110500389B CN 110500389 B CN110500389 B CN 110500389B CN 201910633295 A CN201910633295 A CN 201910633295A CN 110500389 B CN110500389 B CN 110500389B
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- connecting member
- planet
- brake
- row
- clutch
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
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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 a nine-gear planetary automatic transmission of a vehicle driving system. The transmission comprises four planet rows, an input member, an output member, connecting members, brakes and clutches, wherein the input member and the output member are arranged at two ends of each planet row and are respectively connected with an input shaft and an output shaft, and the four planet rows, the five connecting members, the four brakes and the two clutches are arranged. Compared with the prior art, the automatic transmission adopts the scheme of four planet rows, four brakes and two clutches, realizes nine forward gears and has wide transmission ratio range. The invention is convenient for realizing compact structure and reduces the volume and weight of the automatic transmission.
Description
Technical Field
The invention belongs to the technical field of vehicle transmission, and particularly relates to a nine-gear planetary automatic transmission for a road vehicle.
Background
As a planetary automatic transmission for road vehicles, 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 driving wheels through a differential, and most of the transmission is composed of a plurality of planetary rows, a brake and a clutch. At present, the seven-gear planetary automatic transmission for road vehicles in the mainstream has a small transmission ratio range and uneven transmission ratio, and therefore, a nine-gear planetary automatic transmission with better performance than the current planetary automatic transmission needs to be found.
Disclosure of Invention
Technical problem to be solved
The invention aims to provide a nine-gear planetary automatic transmission for a road vehicle, which utilizes four planetary rows, two clutches and four brakes to realize nine forward gears and one reverse gear, has a large transmission ratio range and uniform transmission ratio, and can meet the use requirements of heavy vehicles.
(II) technical scheme
In order to solve the technical problem, the invention provides a nine-gear planetary automatic transmission which comprises a planetary row, an input member 1, an output member 2, a connecting member, a brake and a clutch, wherein the input member 1 and the output member 2 are arranged at two ends of the planetary row and are respectively connected with an input shaft and an output shaft; the planetary gear train is characterized in that the number of the planetary rows is four, and the four planetary rows are a planetary row PGS1, a planetary row PGS2, a planetary row PGS3 and a planetary row PGS4 respectively; five connecting 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 number of the brakes is four, namely 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.
The sun gear S1, the planet carrier CA1 and the ring gear R1 of the planet row PGS1 are respectively connected with a connecting member 3, a connecting member 4 and a connecting member 5;
the sun gear S2, the carrier CA2 and the ring gear R2 of the planetary row PGS2 are connected to the input member 1, the connecting member 5 and the connecting member 4, respectively;
the sun gear S3, the carrier CA3 and the ring gear R3 of the planetary row PGS3 are connected to a connecting member 7, a connecting member 5 and a connecting member 6, respectively;
the sun gear S4, the carrier CA4 and the ring gear R4 of the planetary row PGS4 are connected to the connecting member 4, the connecting member 6 and the output member 2, respectively;
the input member 1 connects the sun gear S2 of the planetary row PGS2 and the inner hub of the clutch C2;
the output member 2 is connected with a ring gear R4 of a planet row PGS4;
the connecting member 3 connects the sun gear S1 of the planetary row PGS1 and the inner hub of the brake B1;
the connecting member 4 connects the carrier CA1 of the planetary row PGS1, the ring gear R2 of the planetary row PGS2, the sun gear S4 of the planetary row PGS4, the inner hub of the brake B2, and the outer hub of the clutch C1;
the connecting member 5 connects the ring gear R1 of the planet row PGS1, the carrier CA2 of the planet row PGS2, the carrier CA3 of the planet row PGS3 and the inner hub of the brake B3;
the connecting member 6 connects the ring gear R3 of the planetary row PGS3, the carrier CA4 of the planetary row PGS4, the inner hub of the brake B4 and the outer hub of the clutch C2;
the connecting member 7 connects the sun gear S3 of the planetary row PGS3 and the inner 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 component 4;
the brake B3 is used for braking the connecting member 5;
the brake B4 is used for braking the connecting component 6;
the clutch C1 connects the connecting member 4 and the connecting member 7;
the clutch C2 connects the connecting member 6 with the input member 1.
(III) advantageous effects
Compared with the prior art, the invention has the following beneficial effects:
the invention provides a nine-gear planetary automatic transmission, which adopts a scheme of four planetary rows, four brakes and two clutches to realize nine forward gears, and the transmission ratio range can reach 10.473. The k value of three planet rows is in the range of 2.5-2.7, which is convenient for realizing compact structure and reducing the volume and weight of the automatic transmission.
Drawings
Fig. 1 is a schematic diagram of a connection relationship of each component of a nine-gear planetary automatic transmission of the present invention, in which PGS1 to PGS4 are four planetary rows, S1 to S4 are four sun gears, CA1 to CA4 are four planetary carriers, R1 to R4 are four ring gears, B1 to B4 are four brakes, C1 to C2 are two clutches, 1 is an input component, 2 is an output component, and 3 to 7 are connecting components.
Detailed Description
In order to make the objects, contents and advantages of the present invention clearer, a detailed description of the present invention will be given below with reference to the accompanying drawings and examples.
The nine-gear planetary automatic transmission is suitable for a vehicle transmission system. 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 an output member 2, and power is transmitted to a front axle and a rear axle or a left driving wheel and a right driving wheel 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.
The nine-speed planetary automatic transmission shown in fig. 1 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. The number of the planet rows is four, and the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS4 respectively; five connecting 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 number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; the two clutches are a clutch C1 and a clutch C2.
Each planet row comprises a sun gear, a planet carrier and a ring gear.
The sun gear S1, the planet carrier CA1 and the ring gear R1 of the planet row PGS1 are respectively connected with a connecting member 3, a connecting member 4 and a connecting member 5;
the sun gear S2, the carrier CA2 and the ring gear R2 of the planetary row PGS2 are connected to the input member 1, the connecting member 5 and the connecting member 4, respectively;
the sun gear S3, the carrier CA3 and the ring gear R3 of the planetary row PGS3 are connected to a connecting member 7, a connecting member 5 and a connecting member 6, respectively;
the sun gear S4, the carrier CA4 and the ring gear R4 of the planetary row PGS4 are connected to the connecting member 4, the connecting member 6 and the output member 2, respectively;
the input member 1 connects the sun gear S2 of the planetary row PGS2 and the inner hub of the clutch C2;
the output member 2 is connected with a ring gear R4 of a planet row PGS4;
the connecting member 3 connects the sun gear S1 of the planetary row PGS1 and the inner hub of the brake B1;
the connecting member 4 connects the carrier CA1 of the planetary row PGS1, the ring gear R2 of the planetary row PGS2, the sun gear S4 of the planetary row PGS4, the inner hub of the brake B2, and the outer hub of the clutch C1;
the connecting member 5 connects the ring gear R1 of the planet row PGS1, the carrier CA2 of the planet row PGS2, the carrier CA3 of the planet row PGS3 and the inner hub of the brake B3;
the connecting member 6 connects the ring gear R3 of the planetary row PGS3, the carrier CA4 of the planetary row PGS4, the inner hub of the brake B4 and the outer hub of the clutch C2;
the connecting member 7 connects the sun gear S3 of the planetary row PGS3 and the inner 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 component 6;
the clutch C1 connects the connecting member 4 and the connecting member 7;
the clutch C2 connects the connecting member 6 and the input member 1.
The planet row PGS1, the planet row PGS2, the planet row PGS3 and the planet row PGS4 are all single planet rows.
The brakes B1-B4 and the clutches C1 and C2 are multi-plate friction control pieces, and hydraulic oil is used for driving pistons to pressurize. The operating scheme for each gear is shown in table 1.
TABLE 1 schematic table of each gear implementation mode, corresponding transmission ratio and intermediate ratio of nine-gear planetary automatic transmission
In the table ". Smallcircle" indicates the handling member engagement
In the following, an example of the present invention is described in detail with reference to fig. 1 and table 1, wherein the transmission ratio described herein refers to the ratio of the input shaft speed to the output shaft speed, and the planetary 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 planetary row.
When the brake B3 and the brake B4 are engaged, the connecting member 5 and the connecting member 6 are simultaneously braked, and the first gear "1st" is achieved.
When the clutch C1 and the brake B4 are engaged, the coupling member 4 and the coupling member 7 integrally rotate, and the coupling member 6 brakes, and the second gear "2nd" is achieved.
When the clutch C1 and the brake B3 are engaged, the coupling member 4 and the coupling member 7 integrally rotate, and the coupling member 5 brakes, and the third gear "3rd" is achieved.
When the clutch C1 and the brake B2 are engaged, the coupling member 4 and the coupling member 7 integrally rotate, and the coupling member 4 brakes, realizing the fourth gear "4th".
When the clutch C1 and the brake B1 are engaged, the coupling member 4 and the coupling member 7 integrally rotate, and the coupling member 3 brakes, realizing the fifth gear "5th".
When the clutch C1 and the clutch C2 are engaged, the coupling member 4 and the coupling member 7 rotate integrally, and the input member 1 and the coupling member 6 rotate integrally, thereby realizing a sixth gear "6th".
When the clutch C2 and the brake B1 are engaged, the coupling member 1 and the coupling member 6 integrally rotate, and the coupling member 3 brakes, achieving seven gear "7th".
When the clutch C2 and the brake B2 are engaged, the input member 1 and the connecting member 6 rotate integrally, and the connecting member 4 brakes, achieving eight gear "8th".
When the clutch C2 and the brake B3 are engaged, the input member 1 and the coupling member 6 rotate integrally, and the coupling member 5 brakes to realize the nine speed "9th".
When the brake B2 and the brake B4 are engaged, the connecting member 4 and the connecting member 6 are braked simultaneously, achieving the reverse gear "Rev".
The gear ratios of the gears are determined by the k values of the four planetary rows. For example, when k1=2.641, k2 ≈ 2.572, k3 ≈ 3.791, and k4 ≈ 2.683, the gear ratios shown in table 1 can be obtained, the total gear ratio range (6.901/0.659) of the forward gears reaches 10.473, and a wide gear ratio range and a relatively uniform inter-gear ratio are obtained. The k values of the planet row PGS1, the planet row PGS2 and the planet row PGS4 are in the range of 2.5-2.7, so that the radial sizes of the three planet rows are small, the compact structure is convenient to realize, and the volume and the weight of the automatic transmission are reduced.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, it is possible to make various improvements and modifications without departing from the technical principle of the present invention, such as: such modifications and variations as adjusting the order of the planetary rows, changing the position of the brakes, changing the clutch connections, changing the planetary rows to a double star simple planetary row or a simple planetary row to a compound planetary row, etc., should also be considered as within the scope of the present invention.
Claims (3)
1. The utility model provides a nine keep off planet automatic gearbox, includes the planet row, installs input member (1), output member (2), connecting elements, stopper and clutch that both ends are connected with input shaft, output shaft respectively, its characterized in that: the number of the planet rows is four, and the four planet rows are a planet row PGS1, a planet row PGS2, a planet row PGS3 and a planet row PGS4 respectively; the number of the connecting members is five, namely a connecting member III, a connecting member IV, a connecting member V, a connecting member VI and a connecting member VII; the number of the brakes is four, namely a brake B1, a brake B2, a brake B3 and a brake B4; the number of the clutches is two, namely a clutch C1 and a clutch C2;
the sun gear S1, the planet carrier CA1 and the ring gear R1 of the planet row PGS1 are respectively connected with a third connecting member, a fourth connecting member and a fifth connecting member;
the sun gear S2, the planet carrier CA2 and the ring gear R2 of the planet row PGS2 are respectively connected with the input member (1), the connecting member V and the connecting member IV;
the sun gear S3, the planet carrier CA3 and the gear ring R3 of the planet row PGS3 are respectively connected with a seventh connecting member, a fifth connecting member and a sixth connecting member;
the sun gear S4, the planet carrier CA4 and the ring gear R4 of the planet row PGS4 are respectively connected with a fourth connecting member, a sixth connecting member and an output member (2);
the input member (1) connects the sun gear S2 of the planetary row PGS2 and the inner hub of the clutch C2;
the output member (2) is connected with a ring gear R4 of a planet row PGS4;
the third connecting member connects the sun gear S1 of the planetary row PGS1 and the inner hub of the brake B1;
the fourth connecting component is connected with a planet carrier CA1 of the planet row PGS1, a ring gear R2 of the planet row PGS2, a sun gear S4 of the planet row PGS4, an inner hub of the brake B2 and an outer hub of the clutch C1;
the fifth connecting member is connected with the ring gear R1 of the planet row PGS1, the planet carrier CA2 of the planet row PGS2, the planet carrier CA3 of the planet row PGS3 and the inner hub of the brake B3;
the sixth connecting member connects the ring gear R3 of the planetary row PGS3, the carrier CA4 of the planetary row PGS4, the inner hub of the brake B4, and the outer hub of the clutch C2;
the seventh connecting member connects the sun gear S3 of the planetary row PGS3 and the inner hub of the clutch C1;
the brake B1 is used for braking a third connecting component;
the brake B2 is used for braking the connecting component IV;
the brake B3 is used for braking the connecting component V;
the brake B4 is used for braking the connecting component six;
the clutch C1 is connected with a fourth connecting component and a seventh connecting component;
the clutch C2 connects the connecting member six and the input member (1).
2. The nine-speed planetary automatic transmission according to claim 1, characterized in that: the planet row PGS1, the planet row PGS2, the planet row PGS3 and the planet row PGS4 are single planet rows.
3. The nine-speed planetary automatic transmission according to claim 1, characterized in that:
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.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910633295.9A CN110500389B (en) | 2019-07-15 | 2019-07-15 | Nine-gear planetary automatic transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910633295.9A CN110500389B (en) | 2019-07-15 | 2019-07-15 | Nine-gear planetary automatic transmission |
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| Publication Number | Publication Date |
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| CN110500389A CN110500389A (en) | 2019-11-26 |
| CN110500389B true CN110500389B (en) | 2022-10-04 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201910633295.9A Active CN110500389B (en) | 2019-07-15 | 2019-07-15 | Nine-gear planetary automatic transmission |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112324877B (en) * | 2020-11-19 | 2023-04-18 | 中国地质大学（武汉） | Nine-gear automatic transmission |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101021250A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| DE102006006622A1 (en) * | 2006-02-14 | 2007-09-13 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE202014009891U1 (en) * | 2014-12-13 | 2015-01-09 | Zf Friedrichshafen Ag | Multi-stage automatic transmission |
| CN106438878A (en) * | 2016-09-30 | 2017-02-22 | 中国北方车辆研究所 | Nine-gear planet automatic transmission |
| CN109372959A (en) * | 2018-12-10 | 2019-02-22 | 肇庆学院 | Nine speed automatic transmissions |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006006639A1 (en) * | 2006-02-14 | 2007-08-30 | Zf Friedrichshafen Ag | Automatic transmission for a motor vehicle comprises a drive shaft and a driven shaft arranged in a housing with planetary sets and switching elements |
| DE102009031544A1 (en) * | 2009-07-02 | 2011-01-05 | Daimler Ag | Gear unit for drive train of motor vehicle, has four planetary gears arranged one behind other along main rotation axis, where driven unit, hollow wheel of one of planetary gears and coupling element are fixedly connected with one another |
| KR101713732B1 (en) * | 2015-06-02 | 2017-03-22 | 현대자동차 주식회사 | Planetary gear train of automatic transmission for vehicles |
| KR20170104795A (en) * | 2016-03-08 | 2017-09-18 | 현대자동차주식회사 | Planetary gear train of automatic transmission for vehicles |
-
2019
- 2019-07-15 CN CN201910633295.9A patent/CN110500389B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101021250A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| DE102006006622A1 (en) * | 2006-02-14 | 2007-09-13 | Zf Friedrichshafen Ag | Multi-speed transmission |
| DE202014009891U1 (en) * | 2014-12-13 | 2015-01-09 | Zf Friedrichshafen Ag | Multi-stage automatic transmission |
| CN106438878A (en) * | 2016-09-30 | 2017-02-22 | 中国北方车辆研究所 | Nine-gear planet automatic transmission |
| CN109372959A (en) * | 2018-12-10 | 2019-02-22 | 肇庆学院 | Nine speed automatic transmissions |
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| CN110500389A (en) | 2019-11-26 |
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