CN112984058A - Nine-gear transmission - Google Patents
Nine-gear transmission Download PDFInfo
- Publication number
- CN112984058A CN112984058A CN202110456576.9A CN202110456576A CN112984058A CN 112984058 A CN112984058 A CN 112984058A CN 202110456576 A CN202110456576 A CN 202110456576A CN 112984058 A CN112984058 A CN 112984058A
- Authority
- CN
- China
- Prior art keywords
- gear
- rotating shaft
- planetary gear
- closed
- transmission mechanism
- 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
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
-
- 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
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/10—Braking arrangements
-
- 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
- F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
- F16H59/02—Selector apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H2057/087—Arrangement and support of friction devices in planetary gearings, e.g. support of clutch drums, stacked arrangements of friction devices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a nine-gear transmission, which comprises 4 planetary gear transmission mechanisms (1 plus planetary gear transmission mechanism and 3 minus planetary gear transmission mechanisms) and 6 switching elements (2 clutches and 4 brakes), wherein each gear is closed by 2 switching elements, so that 9 forward gears and 1 reverse gear can be realized, the number of gears is more, and the speed ratio range is wider; the brake and the planet row are nested and arranged, and are connected with the gear ring of the planet row, so that the structure is more compact.
Description
Technical Field
The invention belongs to the technical field of vehicle transmissions, and particularly relates to a 9-front-1-reverse transmission for a vehicle automatic transmission.
Background
With the great promotion of green travel, the number of gears of passenger cars is more and more, and the hydraulic mechanical automatic transmission of the commercial vehicle is also developed towards the direction of more gears, wider transmission ratio range and smaller step difference. This is to meet the fuel economy and dynamics requirements of the vehicle. In the prior art, 8-gear planetary automatic transmissions are mentioned, which comprise 4 planetary rows, 5 shift elements (3 clutches and 2 brakes), and 3 shift elements per gear engaged achieve 8 forward gears and 1 reverse gear. However, the scheme can only realize 8 forward gears, 3 clutches in 5 shifting elements are arranged in the middle of the transmission, oil supply to the clutches is difficult, an oil supply channel is complex, and the processing and manufacturing cost is increased.
Also, an eight-speed automatic transmission has been proposed which includes 4 planetary rows, 6 shift elements (2 clutches and 4 brakes), and 2 shift elements are engaged to achieve 8 forward gears and 2 reverse gears per gear. However, this solution can only achieve 8 forward gears, which are fewer than the present invention. Although there are four brakes, the brakes mainly connect the sun gear and the carrier, and the connection of the brakes with the sun gear results in a large connection span, increases the rotational inertia of the rotating shaft, and is more expensive to manufacture.
Disclosure of Invention
In order to solve the defects of the prior art, the invention provides a nine-gear transmission, which has the following specific technical scheme:
a nine-gear transmission comprises a switching element, four planetary gear transmission mechanisms, seven rotating shafts and a shell, wherein,
the switching element comprises four brakes, namely a first member, a second member, a third member and a fourth member; two clutches, a fifth member and a sixth member, respectively;
the four planetary gear transmission mechanisms are respectively a first planetary gear transmission mechanism P1, a second planetary gear transmission mechanism P2, a third planetary gear transmission mechanism P3 and a fourth planetary gear transmission mechanism P4;
the seven rotating shafts comprise a first rotating shaft, a second rotating shaft, a third rotating shaft, a fourth rotating shaft, a fifth rotating shaft, a sixth rotating shaft and a seventh rotating shaft; the first rotating shaft is an input shaft, and the second rotating shaft is an output shaft and is used for power input and power output respectively; the third rotating shaft, the fourth rotating shaft, the fifth rotating shaft, the sixth rotating shaft and the seventh rotating shaft are used for power transmission among the planetary gear transmission mechanisms;
wherein the fifth member connects the first rotating shaft and the third rotating shaft; the sixth member connects the first rotating shaft and the fourth rotating shaft;
the first member is connected with the seventh rotating shaft and the shell, the second member is connected with the sixth rotating shaft and the shell, the third member is connected with the fifth rotating shaft and the shell, and the fourth member is connected with the fourth rotating shaft and the shell; the first member, the second member, the third member and the fourth member are tightly attached to the inner wall of the housing, the first member is nested outside the ring gear of the first planetary gear transmission P1, the second member is nested outside the ring gear of the second planetary gear transmission P2, the third member is nested outside the ring gear of the third planetary gear transmission P3, and the fourth member is nested outside the ring gear of the fourth planetary gear transmission P4;
the sun gear of the first planetary gear transmission mechanism P1 is positioned on the first rotating shaft, the planet carrier is positioned on the sixth rotating shaft, and the ring gear is positioned on the seventh rotating shaft; a sun gear of the second planetary gear transmission mechanism P2 is positioned on the first rotating shaft, a planet carrier is positioned on the fifth rotating shaft, and a gear ring is positioned on the sixth rotating shaft; the sun gear of the third planetary gear transmission mechanism P3 is positioned on the third rotating shaft, the planet carrier is positioned on the fourth rotating shaft, and the ring gear is positioned on the fifth rotating shaft; the sun gear of the fourth planetary gear transmission mechanism P4 is positioned on the third rotating shaft, the planet carrier is positioned on the second rotating shaft, and the ring gear is positioned on the fourth rotating shaft;
the shell is used for mounting the transmission mechanism, and the brake is connected with the shell to realize the opening and closing of the brake so as to realize the switching of a gear shifting mode and is a fixed component;
the shift elements can be selectively actuated, so that nine forward gears and one reverse gear can be realized by means of different transmission ratios between the first and second rotary shafts, only two shift elements having to be engaged per gear.
Preferably, all the planetary gear transmission mechanisms comprise a sun gear, a planet gear and a gear ring; the first planetary gear transmission mechanism P1 is a plus planetary gear transmission mechanism, a sun gear is externally meshed with a planetary gear, double planetary gears are mutually meshed, the planetary gear is internally meshed with a gear ring, and the main transmission ratio is a positive value; the second planetary gear train P2, the third planetary gear train P3 and the fourth planetary gear train P4 are simple minus planetary gear trains, and the main gear ratios are all negative.
Preferably, nine forward gears are realized in the following manner: a first forward gear is achieved by the first member and the fourth member being closed, and a second forward gear is achieved by the fifth member and the fourth member being closed; a third forward gear is achieved by the fifth and the first closed members, a fourth forward gear is achieved by the fifth and the third closed members, a fifth forward gear is achieved by the fifth and the second closed members, a sixth forward gear is achieved by the fifth and the sixth closed members, a seventh forward gear is achieved by the sixth and the second closed members, an eighth forward gear is achieved by the sixth and the third closed members, and a ninth forward gear is achieved by the sixth and the first closed members;
the reverse gear is realized by the following steps: reverse gear is achieved by the closed second and fourth members.
The invention has the beneficial effects that:
1. the invention increases the gear number of the transmission, comprising 9 forward gears and 1 reverse gear; the speed ratio range is wider, gear shifting is smoother, the step ratio is more reasonable to set, and the economy and the dynamic performance are improved;
2. the nine-gear transmission has only three layers of sleeve shafts at most, the number of the sleeve shafts is small, and the processing and assembling cost is low;
3. according to the invention, the planet carrier of the first planetary gear transmission mechanism P1 is directly connected with the gear ring of the second planetary gear transmission mechanism P2, so that the span is small, and the processing cost is reduced;
4. the planetary gear transmission mechanism comprises a plurality of components which are connected with the gear ring of the planetary gear transmission mechanism, and can be nested with the planetary gear transmission mechanism, so that the structure is more compact, and the design of an oil supply passage is simple;
5. the sleeve without the long rotating shaft is simpler to process and assemble.
Drawings
In order to illustrate embodiments of the present invention or technical solutions in the prior art more clearly, the drawings which are needed in the embodiments will be briefly described below, so that the features and advantages of the present invention can be understood more clearly by referring to the drawings, which are schematic and should not be construed as limiting the present invention in any way, and for a person skilled in the art, other drawings can be obtained on the basis of these drawings without any inventive effort. Wherein:
FIG. 1 is a structural view of a transmission of the present invention, showing 1-a first shaft, 2-a second shaft, 3-a third shaft, 4-a fourth shaft, 5-a fifth shaft, 6-a sixth shaft, and 7-a seventh shaft; 01-first member, 02-second member, 03-third member, 04-fourth member, 11-fifth member, 12-sixth member.
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments of the present invention and features of the embodiments may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.
The nine speed transmission shown in fig. 1 comprises a switching element, four planetary gear mechanisms, seven rotating shafts and a shell, wherein the switching element comprises four brakes which are a first member 01, a second member 02, a third member 03 and a fourth member 04 respectively; two clutches, a fifth member 11 and a sixth member 12;
four planetary gear trains, a first planetary gear train P1, a second planetary gear train P2, a third planetary gear train P3 and a fourth planetary gear train P4, respectively;
the seven rotating shafts comprise a first rotating shaft 1, a second rotating shaft 2, a third rotating shaft 3, a fourth rotating shaft 4, a fifth rotating shaft 5, a sixth rotating shaft 6 and a seventh rotating shaft 7; the first rotating shaft 1 is an input shaft, and the second rotating shaft 2 is an output shaft and is used for power input and power output respectively; the third rotating shaft 3, the fourth rotating shaft 4, the fifth rotating shaft 5, the sixth rotating shaft 6 and the seventh rotating shaft 7 are used for power transmission among the planetary gear transmission mechanisms;
wherein the fifth member 11 connects the first shaft 1 and the third shaft 3; the sixth member 12 connects the first rotating shaft 1 and the fourth rotating shaft 4;
the first member 01 is connected with the seventh rotating shaft 7 and the shell, the second member 02 is connected with the sixth rotating shaft 6 and the shell, the third member 03 is connected with the fifth rotating shaft 5 and the shell, and the fourth member 04 is connected with the fourth rotating shaft 4 and the shell; the first member 01, the second member 02, the third member 03 and the fourth member 04 are tightly attached to the inner wall of the shell, the first member 01 is nested outside the ring gear of the first planetary gear transmission mechanism P1, the second member 02 is nested outside the ring gear of the second planetary gear transmission mechanism P2, the third member 03 is nested outside the ring gear of the third planetary gear transmission mechanism P3, and the fourth member 04 is nested outside the ring gear of the fourth planetary gear transmission mechanism P4;
the sun gear of the first planetary gear transmission mechanism P1 is located on the first rotating shaft 1, the planet carrier is located on the sixth rotating shaft 6, and the ring gear is located on the seventh rotating shaft 7; the sun gear of the second planetary gear transmission mechanism P2 is positioned on the first rotating shaft 1, the planet carrier is positioned on the fifth rotating shaft 5, and the gear ring is positioned on the sixth rotating shaft 6; the sun gear of the third planetary gear transmission mechanism P3 is positioned on the third rotating shaft 3, the planet carrier is positioned on the fourth rotating shaft 4, and the ring gear is positioned on the fifth rotating shaft 5; the sun gear of the fourth planetary gear transmission mechanism P4 is positioned on the third rotating shaft 3, the planet carrier is positioned on the second rotating shaft 2, and the gear ring is positioned on the fourth rotating shaft 4;
the shell is used for mounting a transmission mechanism, and the brake is connected with the shell to realize the opening and closing of the brake so as to realize the switching of a gear shifting mode and is a fixed component;
the shift elements can be selectively actuated, so that nine forward gears and one reverse gear, each of which only requires two shift elements to be closed, can be realized by means of different transmission ratios between the first rotary shaft 1 and the second rotary shaft 2.
Preferably, all the planetary gear transmission mechanisms comprise a sun gear, a planet gear and a gear ring; the first planetary gear transmission mechanism P1 is a plus planetary gear transmission mechanism, a sun gear is externally meshed with planetary gears, double planetary gears are mutually meshed, the planetary gears are internally meshed with a gear ring, and the main transmission ratio is a positive value; the second, third and fourth planetary gear transmissions P2, P3, P4 are simple minus planetary gear transmissions, and the primary ratios are negative.
The nine forward gears are realized in the following mode: a first forward gear is achieved by the first and fourth closed members 01 and 04, and a second forward gear is achieved by the fifth and fourth closed members 11 and 04; a third forward gear is realized by the closed fifth element 11 and the first element 01, a fourth forward gear is realized by the closed fifth element 11 and the closed third element 03, a fifth forward gear is realized by the closed fifth element 11 and the closed second element 02, a sixth forward gear is realized by the closed fifth element 11 and the closed sixth element 12, a seventh forward gear is realized by the closed sixth element 12 and the closed second element 02, an eighth forward gear is realized by the closed sixth element 12 and the closed third element 03, and a ninth forward gear is realized by the closed sixth element 12 and the closed first element 01;
the reverse gear is realized by the following steps: reverse gear is achieved by the closed second member 02 and the fourth member 04.
The nine-gear transmission comprises 4 planetary gear transmission mechanisms (comprising 1 positive planetary gear transmission mechanism and 3 negative planetary gear transmission mechanisms), 7 rotating shafts, 6 switching elements (comprising 2 clutches and 4 brakes), 4 brakes are nested in the planetary gear transmission mechanisms, and 2 clutches are positioned at the front part of the transmission, so that the structural layout is more compact.
According to the invention, each gear is closed by 2 switching elements, 9 forward gears and 1 reverse gear can be realized, the number of gears is more, the transmission ratio range is wider, and a wider speed ratio range and a more uniform transmission step ratio can be obtained along with the increase of the number of gears.
Table 1 shows the shift logic of the present solution and the possible gear ratios of the gears, where the adjacent gears are simple shifts, ● indicates the switching element is closed, and x indicates the switching element is open. 1 great 1-gear speed ratio can be realized, and the low-speed running operation of the commercial vehicle is facilitated.
TABLE 1 Shift logic and one possible Gear ratio
| |
11 | 12 | 01 | 02 | 03 | 04 | Transmission ratio |
| Reverse gear | × | × | × | ● | × | ● | -4.483 |
| 1 gear | × | × | ● | × | × | ● | 4.895 |
| 2 keeps off | ● | × | × | × | × | ● | 3.1 |
| 3 grade | ● | × | ● | × | × | × | 2.458 |
| 4-gear | ● | × | × | × | ● | × | 1.811 |
| 5-gear | ● | × | × | ● | × | × | 1.406 |
| 6-gear | ● | ● | × | × | × | × | 1 |
| 7 shift | × | ● | × | ● | × | × | 0.711 |
| 8 keep off | × | ● | × | × | ● | × | 0.614 |
| 9 gear | × | ● | ● | × | × | × | 0.545 |
According to the invention, through 6 switching elements, wherein 2 clutches and 4 brakes are mutually engaged and disengaged, the switching of different gear modes can be effectively realized, and 9 forward gears and 1 reverse gear with different transmission ratios can be effectively realized in the process from an input rotating shaft to an output rotating shaft. The main function of the switching element is to realize mode switching better, and a proper wet or dry friction type switching element can be selected in a targeted manner in the design process of an actual product, and for the selection of specific specifications of different switching elements, the limit load born by the switching element in the process of different power transmission routes should be matched for matching, so that the reliability of the automatic transmission product is ensured.
The invention adopts the structural characteristics of few clutches and multiple brakes, and the planetary gear transmission mechanism is nested in the brakes for arrangement, and 6 switching elements, namely 2 clutches and 4 brakes are used for realizing the mode switching of 9 forward gears and 1 reverse gear, so that the switching elements are easy to assemble, and a required hydraulic system can be directly supplied from a shell, and the structural design size of the 9-gear transmission is more compact.
Although exemplary embodiments of the present invention have been described for illustrative purposes, those skilled in the art will appreciate that various modifications, additions, substitutions and the like can be made in form and detail without departing from the scope and spirit of the invention as disclosed in the accompanying claims, all of which shall fall within the scope of the claims appended hereto, and that the various steps of the claimed method can be combined together in any combination. Therefore, the description of the embodiments disclosed in the present invention is not intended to limit the scope of the present invention, but to describe the present invention. Accordingly, the scope of the present invention is not limited by the above embodiments, but is defined by the claims or their equivalents.
Claims (3)
1. A nine-gear transmission is characterized by comprising a switching element, four planetary gear transmission mechanisms, seven rotating shafts and a shell, wherein,
the switching element comprises four brakes, a first member (01), a second member (02), a third member (03) and a fourth member (04), respectively; two clutches, respectively a fifth member (11) and a sixth member (12);
the four planetary gear transmission mechanisms are respectively a first planetary gear transmission mechanism P1, a second planetary gear transmission mechanism P2, a third planetary gear transmission mechanism P3 and a fourth planetary gear transmission mechanism P4;
the seven rotating shafts comprise a first rotating shaft (1), a second rotating shaft (2), a third rotating shaft (3), a fourth rotating shaft (4), a fifth rotating shaft (5), a sixth rotating shaft (6) and a seventh rotating shaft (7); the first rotating shaft (1) is an input shaft, and the second rotating shaft (2) is an output shaft and is used for power input and power output respectively; the third rotating shaft (3), the fourth rotating shaft (4), the fifth rotating shaft (5), the sixth rotating shaft (6) and the seventh rotating shaft (7) are used for power transmission among planetary gear transmission mechanisms;
wherein the fifth member (11) connects the first shaft (1) and the third shaft (3); the sixth member (12) connects the first shaft (1) and the fourth shaft (4);
the first member (01) is connected with the seventh rotating shaft (7) and the shell, the second member (02) is connected with the sixth rotating shaft (6) and the shell, the third member (03) is connected with the fifth rotating shaft (5) and the shell, and the fourth member (04) is connected with the fourth rotating shaft (4) and the shell; the first member (01), the second member (02), the third member (03) and the fourth member (04) are tightly attached to the inner wall of the shell, the first member (01) is nested outside the ring gear of the first planetary gear transmission mechanism P1, the second member (02) is nested outside the ring gear of the second planetary gear transmission mechanism P2, the third member (03) is nested outside the ring gear of the third planetary gear transmission mechanism P3, and the fourth member (04) is nested outside the ring gear of the fourth planetary gear transmission mechanism P4;
the sun gear of the first planetary gear mechanism P1 is positioned on the first rotating shaft (1), the planet carrier is positioned on the sixth rotating shaft (6), and the ring gear is positioned on the seventh rotating shaft (7); the sun gear of the second planetary gear transmission mechanism P2 is positioned on the first rotating shaft (1), the planet carrier is positioned on the fifth rotating shaft (5), and the gear ring is positioned on the sixth rotating shaft (6); the sun gear of the third planetary gear mechanism P3 is positioned on the third rotating shaft (3), the planet carrier is positioned on the fourth rotating shaft (4), and the ring gear is positioned on the fifth rotating shaft (5); the sun gear of the fourth planetary gear mechanism P4 is located on the third rotating shaft (3), the planet carrier is located on the second rotating shaft (2), and the ring gear is located on the fourth rotating shaft (4);
the shell is used for mounting the transmission mechanism, and the brake is connected with the shell to realize the opening and closing of the brake so as to realize the switching of a gear shifting mode and is a fixed component;
the shift elements can be selectively actuated, so that nine forward gears and one reverse gear can be realized by means of different transmission ratios between the first rotary shaft (1) and the second rotary shaft (2), wherein only two shift elements need to be closed in each gear.
2. The nine speed transmission of claim 1, wherein all planetary gear trains comprise a sun gear, planet gears, and a ring gear; the first planetary gear transmission mechanism P1 is a plus planetary gear transmission mechanism, a sun gear is externally meshed with a planetary gear, double planetary gears are mutually meshed, the planetary gear is internally meshed with a gear ring, and the main transmission ratio is a positive value; the second planetary gear train P2, the third planetary gear train P3 and the fourth planetary gear train P4 are simple minus planetary gear trains, and the main gear ratios are all negative.
3. The nine speed transmission of claim 1 or 2,
the nine forward gears are realized in the following mode: a first forward gear is achieved by the first member (01) and the fourth member (04) being closed, and a second forward gear is achieved by the fifth member (11) and the fourth member (04) being closed; a third forward gear is achieved by the fifth element (11) and the first element (01) being closed, a fourth forward gear is achieved by the fifth element (11) and the third element (03) being closed, a fifth forward gear is achieved by the fifth element (11) and the second element (02) being closed, a sixth forward gear is achieved by the fifth element (11) and the sixth element (12) being closed, a seventh forward gear is achieved by the sixth element (12) and the second element (02) being closed, an eighth forward gear is achieved by the sixth element (12) and the third element (03) being closed, and a ninth forward gear is achieved by the sixth element (12) and the first element (01) being closed;
the reverse gear is realized by the following steps: reverse gear is achieved by the closed second member (02) and the closed fourth member (04).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110456576.9A CN112984058A (en) | 2021-04-27 | 2021-04-27 | Nine-gear transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202110456576.9A CN112984058A (en) | 2021-04-27 | 2021-04-27 | Nine-gear transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112984058A true CN112984058A (en) | 2021-06-18 |
Family
ID=76340297
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202110456576.9A Pending CN112984058A (en) | 2021-04-27 | 2021-04-27 | Nine-gear transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112984058A (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4683776A (en) * | 1986-02-27 | 1987-08-04 | General Motors Corporation | Transmission gearing arrangement |
| CN1936363A (en) * | 2005-09-23 | 2007-03-28 | 通用汽车公司 | Nine speed automatic transmission with six torque-transmitting mechanisms |
| CN102644705A (en) * | 2011-02-17 | 2012-08-22 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| CN104896038A (en) * | 2015-06-19 | 2015-09-09 | 陕西法士特齿轮有限责任公司 | Multi-gear transmission and planetary gear train thereof |
| JP2016011681A (en) * | 2014-06-27 | 2016-01-21 | アイシン精機株式会社 | Automatic transmission for vehicle |
| CN105299156A (en) * | 2015-11-10 | 2016-02-03 | 中国北方车辆研究所 | Multi-gear transmission |
| CN106609816A (en) * | 2015-10-22 | 2017-05-03 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| WO2017134950A1 (en) * | 2016-02-01 | 2017-08-10 | 株式会社小松製作所 | Planetary gear transmission |
| CN108223718A (en) * | 2017-12-29 | 2018-06-29 | 广州汽车集团股份有限公司 | Four planet row automatic transmission and vehicle |
| US20190264783A1 (en) * | 2016-09-28 | 2019-08-29 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| CN110608270A (en) * | 2019-09-24 | 2019-12-24 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN111577843A (en) * | 2020-04-10 | 2020-08-25 | 中国北方车辆研究所 | Nine-gear planetary automatic transmission |
-
2021
- 2021-04-27 CN CN202110456576.9A patent/CN112984058A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4683776A (en) * | 1986-02-27 | 1987-08-04 | General Motors Corporation | Transmission gearing arrangement |
| CN1936363A (en) * | 2005-09-23 | 2007-03-28 | 通用汽车公司 | Nine speed automatic transmission with six torque-transmitting mechanisms |
| CN102644705A (en) * | 2011-02-17 | 2012-08-22 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| JP2016011681A (en) * | 2014-06-27 | 2016-01-21 | アイシン精機株式会社 | Automatic transmission for vehicle |
| CN104896038A (en) * | 2015-06-19 | 2015-09-09 | 陕西法士特齿轮有限责任公司 | Multi-gear transmission and planetary gear train thereof |
| CN106609816A (en) * | 2015-10-22 | 2017-05-03 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN105299156A (en) * | 2015-11-10 | 2016-02-03 | 中国北方车辆研究所 | Multi-gear transmission |
| WO2017134950A1 (en) * | 2016-02-01 | 2017-08-10 | 株式会社小松製作所 | Planetary gear transmission |
| US20190264783A1 (en) * | 2016-09-28 | 2019-08-29 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| CN108223718A (en) * | 2017-12-29 | 2018-06-29 | 广州汽车集团股份有限公司 | Four planet row automatic transmission and vehicle |
| CN110608270A (en) * | 2019-09-24 | 2019-12-24 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN111577843A (en) * | 2020-04-10 | 2020-08-25 | 中国北方车辆研究所 | Nine-gear planetary automatic transmission |
Non-Patent Citations (2)
| Title |
|---|
| HARALD NAUNHEIMER: "《汽车变速器理论基础、选择、设计与应用》", 31 August 2017, 机械工业出版社 * |
| 孙静霞 等: "《汽车自动变速器构造与检修》", 31 July 2019, 北京理工大学出版社 * |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US9759291B2 (en) | Multi-speed automatic transmission | |
| US8894536B2 (en) | Multistep gear mechanism | |
| US8944953B2 (en) | Multistep gear mechanism | |
| JP5300873B2 (en) | Multi-speed transmission | |
| US8529394B2 (en) | Multi-ratio transmission | |
| US8241170B2 (en) | Multi step transmission | |
| US8231495B2 (en) | Multi step transmission | |
| US20120172172A1 (en) | Multi-ratio transmission | |
| JP2010156351A (en) | Planetary gear type gearbox | |
| US10352403B2 (en) | Multistep automatic transmission | |
| JP2009293762A (en) | Multistage shift planetary gear train | |
| CN111536211B (en) | Multi-gear planetary gear speed change device | |
| CN205383227U (en) | Nine -gear automatic gearbox drive mechanism | |
| CN104334920A (en) | Multi-speed gearbox | |
| CN104395641B (en) | Multiple-speed gear-box | |
| CN105757190A (en) | Seven-gear automatic transmission | |
| KR101697637B1 (en) | Automatic transmission | |
| US9803722B2 (en) | Multi-stage automatic transmission | |
| US20090221395A1 (en) | Automatic transmission | |
| CN112324874A (en) | Nine-gear automatic transmission with stable step ratio | |
| CN112984059B (en) | Longitudinal rear-drive planetary gear automatic gearbox | |
| CN112984058A (en) | Nine-gear transmission | |
| CN106917849B (en) | Eight-speed automatic transmission | |
| CN112324875B (en) | Nine-gear automatic transmission with small step ratio | |
| CN112984060A (en) | Eight-front two-reverse planetary gear automatic transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20210618 |