CN112555364A - Planetary gear transmission mechanism - Google Patents
Planetary gear transmission mechanism Download PDFInfo
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- CN112555364A CN112555364A CN202011363403.4A CN202011363403A CN112555364A CN 112555364 A CN112555364 A CN 112555364A CN 202011363403 A CN202011363403 A CN 202011363403A CN 112555364 A CN112555364 A CN 112555364A
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- gear
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- planet
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02039—Gearboxes for particular applications
- F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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
- F16H2200/2015—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with five 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
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
Abstract
The invention provides a planetary gear transmission mechanism which comprises an input shaft, an output shaft, a planetary row P1, a planetary row P2, a planetary row P3, a planetary row P4, a planetary row P5, a clutch L1 and a clutch L2, wherein the planetary row P1, the planetary row P2, the planetary row P3, the planetary row P4 and the planetary row P5 all comprise sun gears, planet gears and ring gears, the clutch L1, the planetary row P1 sun gear, the planetary row P3 sun gear and the planetary row P4 sun gear are sequentially connected in series, the clutch L2, the planetary row P3, the planetary row P4 ring gear and the planetary row P5 ring gear are sequentially connected in series, the clutch L1 is connected with the clutch L2 in parallel and then connected with the input shaft, and the planetary row P5 sun gear is connected with the planetary row P4 in parallel and then connected with the output shaft. By adopting the technical scheme of the invention, a plurality of groups of planet rows are utilized to transmit power, so that the selectivity of a user on the output speed ratio is more, more forward gears are added to the automobile, the change of the output speed ratio is smoother, the running of the automobile is more stable, and the comfort is improved.
Description
Technical Field
The invention belongs to the technical field of automobile transmissions, and particularly relates to a planetary gear transmission mechanism.
Background
AT present, automobile models widely sold in the market are mainly divided into a manual transmission and an automatic transmission according to the type of a speed change mechanism adopted by the automobile models, automobiles equipped with the automatic transmission are more and more popular, the automatic transmission is an important part in the automobiles, the automatic transmission mainly comprises modules such as a gear shifting handle, a transmission control unit, a gear shifting electromagnetic valve and the like, gears in the automobile speed change mechanism are switched according to the current running speed of the automobiles through a corresponding electric control system, however, the planetary gear transmission of the AT automatic transmission is only provided with 6-9 forward gears generally, and the first gear ratio is smaller than 5 generally. Although a gear with the maximum speed ratio of more than 7 is arranged in an individual wide-speed-ratio transmission, the speed ratio difference between the individual wide-speed-ratio transmission and the adjacent gear is large, and the output speed is reflected to have large fluctuation on the output speed, so that the work is not smooth. Therefore, more forward gears and larger speed ratio are beneficial to improving the gear shifting comfort of the vehicle, and the requirements of high-speed running and low-speed slow running can be better met.
Disclosure of Invention
In order to solve the technical problem, the invention provides a planetary gear transmission mechanism.
The invention is realized by the following technical scheme.
The invention provides a planetary gear transmission mechanism which comprises an input shaft, an output shaft, a planetary row P1, a planetary row P2, a planetary row P3, a planetary row P4, a planetary row P5, a clutch L1 and a clutch L2, the planet row P1, the planet row P2, the planet row P3, the planet row P4 and the planet row P5 all comprise sun gears, planet gears meshed with the corresponding sun gears and ring gears meshed with the corresponding planet gears, the clutch L1, the sun gear of the planet row P1, the sun gear of the planet row P3 and the sun gear of the planet row P4 are connected in series in turn, the clutch L2, the planet carrier of the planet row P3, the ring gear of the planet row P4 and the ring gear of the planet row P5 are connected in series in turn, the clutch L1 is connected with the input shaft after being connected with the clutch L2 in parallel, and the sun gear of the planet row P5 is connected with the planet carrier of the planet row P4 in parallel and then connected with the output shaft.
The planetary gear transmission mechanism further comprises a brake Z1, a brake Z2, a brake Z3, a brake Z4 and a brake Z5, the brake Z1 is connected with the planetary row P1 gear ring and the planetary row P2 sun gear respectively, the brake Z2 is connected with the planetary row P2 gear ring, the brake Z3 is connected with the planetary row P1 gear carrier, the planetary row P2 gear carrier and the planetary row P3 gear ring, the brake Z4 is connected with the planetary row P3 gear carrier, the planetary row P4 gear ring and the planetary row P5 gear ring respectively, and the brake Z5 is connected with the planetary row P5 gear carrier.
A countershaft is also connected between the clutch L1 and the sun gear of the planetary row P1.
The gear ratio of the planet wheels in the planet row P1 to the ring gear is alpha 1-1.71.
The gear ratio of the planet wheels in the planet row P2 to the ring gear is alpha 2-2.158.
The gear ratio of the planet wheels in the planet row P3 to the ring gear is alpha 3-1.98.
The gear ratio of the planet wheels in the planet row P4 to the ring gear is 2.51 which is alpha 4.
The gear ratio of the planet wheels in the planet row P5 to the ring gear is alpha 5-3.
The invention has the beneficial effects that: by adopting the technical scheme of the invention, a plurality of groups of planet rows are utilized to transmit power, the running state of each group of planet rows is controlled after flexible combination of a plurality of clutches and a plurality of brakes, so that the selectivity of a user on the output speed ratio is more, an automobile can have more forward gears and a wider speed regulation range, in addition, the output speed ratio difference between adjacent gears is reduced, the output speed ratio change of the automobile is smoother after the gears are switched, the corresponding automobile running speed change range is smaller, the corresponding transmission mechanism works more smoothly, the automobile runs more stably, the imperial gear shifting of a driver and the riding comfort of passengers are improved, and the automobile can better meet the requirements of high-speed running and low-speed slow running.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Detailed Description
The technical solutions of the present invention are further described below, but the scope of the claims is not limited thereto.
As shown in fig. 1, the present invention provides a planetary gear transmission mechanism including an input shaft, an output shaft, a planetary row P1, a planetary row P2, a planetary row P3, a planetary row P4, a planetary row P5, a clutch L1, and a clutch L2, the planet row P1, the planet row P2, the planet row P3, the planet row P4 and the planet row P5 all comprise sun gears, planet gears meshed with the corresponding sun gears and ring gears meshed with the corresponding planet gears, the clutch L1, the sun gear of the planet row P1, the sun gear of the planet row P3 and the sun gear of the planet row P4 are connected in series in turn, the clutch L2, the planet carrier of the planet row P3, the ring gear of the planet row P4 and the ring gear of the planet row P5 are connected in series in turn, the clutch L1 is connected with the input shaft after being connected with the clutch L2 in parallel, and the sun gear of the planet row P5 is connected with the planet carrier of the planet row P4 in parallel and then connected with the output shaft.
Further, the planetary gear transmission mechanism further comprises a brake Z1, a brake Z2, a brake Z3, a brake Z4 and a brake Z5, the brake Z1 is connected with the planetary row P1 gear ring and the planetary row P2 sun gear respectively, the brake Z2 is connected with the planetary row P2 gear ring, the brake Z3 is connected with the planetary row P1 planet carrier, the planetary row P2 planet carrier and the planetary row P3 gear ring, the brake Z4 is connected with the planetary row P3 planet carrier, the planetary row P4 gear ring and the planetary row P5 gear ring respectively, and the brake Z5 is connected with the planetary row P5 planet carrier.
In addition, a countershaft is connected between the clutch L1 and the sun gear of the planetary row P1. Preferably, the gear ratio of the planet row P1 to the ring gear is α 1-1.71. The gear ratio of the planet wheels in the planet row P2 to the ring gear is alpha 2-2.158. The gear ratio of the planet wheels in the planet row P3 to the ring gear is alpha 3-1.98. The gear ratio of the planet wheels in the planet row P4 to the ring gear is 2.51 which is alpha 4. The gear ratio of the planet wheels in the planet row P5 to the ring gear is alpha 5-3.
By adopting the technical scheme of the invention, a plurality of groups of planet rows are utilized to transmit power, the running state of each group of planet rows is controlled after flexible combination of a plurality of clutches and a plurality of brakes, so that the selectivity of a user on the output speed ratio is more, an automobile can have more forward gears and a wider speed regulation range, in addition, the output speed ratio difference between adjacent gears is reduced, the output speed ratio change of the automobile is smoother after the gears are switched, the corresponding automobile running speed change range is smaller, the corresponding transmission mechanism works more smoothly, the automobile runs more stably, the imperial gear shifting of a driver and the riding comfort of passengers are improved, and the automobile can better meet the requirements of high-speed running and low-speed slow running.
By adopting the technical scheme of the invention, when the gears are switched, the corresponding combination relationship among each gear state, the corresponding clutch L1, the corresponding clutch L2, the corresponding brake Z1, the corresponding brake Z2, the corresponding brake Z3, the corresponding brake Z4 and the corresponding brake Z5 is as follows:
neutral position: with brake Z5 engaged, there is no output from the output shaft.
First gear: in conjunction with brake Z2 and brake Z5, the planetary row P2 with the ring gear and the planetary row P5 with the carrier brake, has an overall transmission ratio of (α 1 × α 2-1) × (α 3+ α 4 × α 5+ α 4+ α 5+1)/(α 3 × α 5) of i 1.
Second gear: second gear has two mode states available for user selection, the first mode selected to engage brake Z2 and brake Z4. The planet row P2 ring gear, the planet row P3 planet carrier, the planet row P4 ring gear and the planet row P5 ring gear are braked, and the speed ratio of the planetary gear transmission mechanism is i2a ═ (alpha 4+1) × (alpha 1 × alpha 2-1)/alpha 3; the second option is to engage clutch L1 and brake Z5. The input shaft is connected through clutch L1 and the layshaft to the sun gear of row P3 and the sun gear of row P4, and the planet carrier of row P5 brakes. The planetary gear set speed ratio is i2b ═ α 4+ α 4/α 5+ 1.
Third gear: by combining the clutch L1 and the brake Z4, the input shaft is connected with the sun gear of the planetary row P3 and the sun gear of the planetary row P4 through the clutch L1 and the intermediate shaft; the planet carrier of the planet row P3, the ring gear of the planet row P4 and the ring gear of the planet row P5 are braked, and the speed ratio of the planetary transmission mechanism is equal to (alpha 4+1) when the speed ratio is i 3.
Fourth gear: by combining the clutch L1 and the brake Z2, the input shaft is connected with the sun gear of the planetary row P3 and the sun gear of the planetary row P4 through the clutch L1 and the intermediate shaft; the ring gear of the planetary row P3 is braked, at which time the planetary transmission ratio is i4 ═ α 3+1 × (α 4+1) × (1- α 1 × α 2)/(- α 1 × α 2 × α 3- α 1 × α 2 × α 4- α 1 × α 2+ α 3 × α 4+ α 3+ α 4+ 1).
Fifth gear: by combining the clutch L1 and the brake Z3, the input shaft is connected with the sun gear of the planetary row P3 and the sun gear of the planetary row P4 through the clutch L1 and the intermediate shaft; the planet carrier of the planet row P1, the planet carrier of the planet row P2 and the ring gear of the planet row P3 are braked, and the planetary gear transmission mechanism has the speed ratio of i5 ═ α 3+1 × (α 4+1)/(α 3+ α 4+ 1).
A sixth gear: by combining the clutch L1 and the brake Z1, the input shaft is connected with the sun gear of the planetary row P3 and the sun gear of the planetary row P4 through the clutch L1 and the intermediate shaft; the ring gear of the planet row P1 and the sun gear of the planet row P2 are braked, at which time the epicyclic transmission has a speed ratio of i6 ═ α 1+1 × (α 3+1) × (α 4+1)/(α 1 × α 3+ α 1 × α 4+ α 1+ α 3 × α 4+ α 3+ α 4+ 1).
Seventh gear: by combining the clutch L1 and the clutch L2, the input shaft is connected with the sun gear of the planetary row P3 and the sun gear of the planetary row P4 through the clutch L1 and the intermediate shaft; the input shaft is also connected through clutch L2 to the planet carrier of row P3, the ring gear of row P4 and the ring gear of row P5, at which time the planetary transmission ratio is i7 — 1.
Eighth gear: by combining the clutch L2 and the brake Z1, the input shaft is connected with a planet carrier of a planet row P3, a ring gear of the planet row P4 and a ring gear of a planet row P5 through a clutch L2; the ring gear of the planetary row P1 and the sun gear of the planetary row P2 are braked, in which case the planetary transmission ratio is i8 ═ α 1+1 × (α 4+1)/(α 1 × α 3+ α 1 × α 4+ α 1+ α 4+ 1).
Nine gears: by combining the clutch L2 and the brake Z3, the input shaft is connected with a planet carrier of a planet row P3, a ring gear of the planet row P4 and a ring gear of a planet row P5 through a clutch L2; the planet carrier of the planetary row P1, the planet carrier of the planetary row P2 and the ring gear of the planetary row P3 are braked, at which time the planetary transmission has a speed ratio i9 ═ α 4+1)/(α 3+ α 4+ 1).
Ten gears: by combining the clutch L2 and the brake Z2, the input shaft is connected with a planet carrier of a planet row P3, a ring gear of the planet row P4 and a ring gear of a planet row P5 through a clutch L2; the ring gear of the planetary row P3 is braked, with the planetary gear ratio i10 ═ α 4+1 × (α 1 × α 2-1)/(α 1 × α 2 × α 3+ α 1 × α 2 × α 4+ α 1 × α 2- α 4-1).
Reverse gear one: in conjunction with the combination of brake Z1 and brake Z5, the planetary row P1 ring gear, the planetary row P2 sun gear and the planetary row P5 carrier brake, at which time the planetary transmission ratio is iR1 ═ - (α 1+1) × (α 3+ α 4 × α 5+ α 4+ α 5+1)/(α 3 × α 5).
And B, reverse gear II: in combination with brake Z1 and brake Z4, the planetary row P1 ring gear, the planetary row P2 sun gear and planetary row P3 planet carrier, the planetary row P4 ring gear and the planetary row P5 ring gear brake, at which time the planetary transmission ratio is iR2 ═ α 1+1) × (α 4+1)/α 3.
By adopting the technical scheme of the invention, except that the neutral gear is only combined with one brake Z5, other gears are required to be combined with two clutches or brakes, one clutch or brake is kept in a combined state when being switched to an adjacent gear every time, and only the other clutch or brake is required to be combined in a changed mode, so that the gear shifting operation is smoother, and the operating conditions of all gears are shown in tables 1 and 2.
When α 1 is 1.71, α 2 is 2.158, α 3 is 1.98, α 4 is 2.51, α 5 is 3, the total transmission speed of the planetary gear transmission mechanism in each gear is as shown in table 3, the forward first gear transmission ratio is 7.29, the ten gear transmission ratio is 0.56, as shown in the table, the difference of the transmission speed ratio between adjacent gears is small, the gear shifting is smoother, the planetary gear transmission mechanism is an ideal wide-ratio planetary gear transmission mechanism, and the symbol "+" in tables 1, 2 and 3 indicates the corresponding clutch or brake combination
TABLE 1 operating mode of each gear in the first operating mode of the present invention
TABLE 2 operating mode of each gear in the second operating mode of the present invention
TABLE 3 operating mode and Total Transmission ratio of the various gears in the first operating mode of the present invention
Claims (8)
1. A planetary gear transmission mechanism comprises an input shaft, an output shaft, a planetary row P1, a planetary row P2, a planetary row P3, a planetary row P4, a planetary row P5, a clutch L1 and a clutch L2, wherein the planetary row P1, the planetary row P2, the planetary row P3, the planetary row P4 and the planetary row P5 all comprise a sun gear, planetary gears meshed with the corresponding sun gear and a ring gear meshed with the corresponding planetary gears, the clutch L1, the sun gear P1, the sun gear P3 and the sun gear P4 are sequentially connected in series, the clutch L2, the planet carrier P3, the ring gear P4 and the ring gear P5 are sequentially connected in series, the clutch L1 is connected with the clutch L2 in parallel and then connected with the input shaft, and the sun gear P5 is connected with the planetary row P4 in parallel and then connected with the output shaft.
2. The planetary gear transmission as in claim 1, wherein: the planetary gear transmission mechanism further comprises a brake Z1, a brake Z2, a brake Z3, a brake Z4 and a brake Z5, the brake Z1 is connected with the planetary row P1 gear ring and the planetary row P2 sun gear respectively, the brake Z2 is connected with the planetary row P2 gear ring, the brake Z3 is connected with the planetary row P1 gear carrier, the planetary row P2 gear carrier and the planetary row P3 gear ring, the brake Z4 is connected with the planetary row P3 gear carrier, the planetary row P4 gear ring and the planetary row P5 gear ring respectively, and the brake Z5 is connected with the planetary row P5 gear carrier.
3. The planetary gear transmission as in claim 1, wherein: a countershaft is also connected between the clutch L1 and the sun gear of the planetary row P1.
4. The planetary gear transmission as in claim 1, wherein: the gear ratio of the planet wheels in the planet row P1 to the ring gear is alpha 1-1.71.
5. The planetary gear transmission as in claim 1, wherein: the gear ratio of the planet wheels in the planet row P2 to the ring gear is alpha 2-2.158.
6. The planetary gear transmission as in claim 1, wherein: the gear ratio of the planet wheels in the planet row P3 to the ring gear is alpha 3-1.98.
7. The planetary gear transmission as in claim 1, wherein: the gear ratio of the planet wheels in the planet row P4 to the ring gear is 2.51 which is alpha 4.
8. The planetary gear transmission as in claim 1, wherein: the gear ratio of the planet wheels in the planet row P5 to the ring gear is alpha 5-3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN202011363403.4A CN112555364B (en) | 2020-11-27 | 2020-11-27 | Planetary gear transmission mechanism |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011363403.4A CN112555364B (en) | 2020-11-27 | 2020-11-27 | Planetary gear transmission mechanism |
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| CN112555364A true CN112555364A (en) | 2021-03-26 |
| CN112555364B CN112555364B (en) | 2023-05-05 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113108032A (en) * | 2021-03-29 | 2021-07-13 | 北方汤臣传动科技有限公司 | Nine-gear planetary automatic transmission for mining truck |
| CN115217919A (en) * | 2022-06-20 | 2022-10-21 | 陕西法士特齿轮有限责任公司 | Ten-gear transmission and vehicle |
Citations (24)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1983000201A1 (en) * | 1981-07-07 | 1983-01-20 | Windish, Willis, E. | Planetary transmission |
| US4531428A (en) * | 1983-01-10 | 1985-07-30 | Caterpillar Tractor Co. | Planetary transmission |
| US4742733A (en) * | 1984-10-04 | 1988-05-10 | Zahnradfabrik Friedrichshafen, Ag. | Control system for automatic change speed transmission |
| US5924951A (en) * | 1997-12-11 | 1999-07-20 | Caterpillar Inc. | Planetary transmission with direct drive through the front triple planetary gearsets by a single clutch |
| JP2005172123A (en) * | 2003-12-11 | 2005-06-30 | Kyowa Metal Work Co Ltd | Multi-stage shift planetary gear series |
| US20100184554A1 (en) * | 2007-09-25 | 2010-07-22 | Komatsu Ltd. | Planetary gear type gearbox |
| US20120142486A1 (en) * | 2009-08-20 | 2012-06-07 | Zf Friedrichshafen Ag | Multi-ratio transmission |
| CN103244623A (en) * | 2013-05-29 | 2013-08-14 | 新乡市恒润机电有限公司 | Nine-gear planetary automatic gearbox |
| US20140364269A1 (en) * | 2013-06-05 | 2014-12-11 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN104728365A (en) * | 2013-12-20 | 2015-06-24 | 贵州凯星液力传动机械有限公司 | Drive mechanism of hydrodynamic transmission |
| CN105697674A (en) * | 2014-12-15 | 2016-06-22 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| US20160178034A1 (en) * | 2014-12-17 | 2016-06-23 | Zf Friedrichshafen Ag | Multistep Automatic Transmission |
| JP2017172717A (en) * | 2016-03-24 | 2017-09-28 | アイシン・エィ・ダブリュ株式会社 | Automatic transmission |
| US20180087621A1 (en) * | 2016-09-28 | 2018-03-29 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US9958033B1 (en) * | 2017-05-10 | 2018-05-01 | Hyundai Motor Company | Planetary gear train of automatic transmission for vehicles |
| DE102016222226A1 (en) * | 2016-11-11 | 2018-05-17 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US20180245670A1 (en) * | 2015-09-09 | 2018-08-30 | Volvo Construction Equipment Ab | A transmission arrangement for a vehicle |
| DE102017206829A1 (en) * | 2017-04-24 | 2018-10-25 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| US20180328459A1 (en) * | 2017-05-10 | 2018-11-15 | Hyundai Motor Company | Planetary gear train of automatic transmission for vehicles |
| US20190128383A1 (en) * | 2017-10-31 | 2019-05-02 | Hyundai Motor Company | Planetary gear train of an automatic transmission for a vehicle |
| DE102017219506A1 (en) * | 2017-11-02 | 2019-05-02 | Zf Friedrichshafen Ag | 4WD automatic transmission |
| CN110023648A (en) * | 2016-12-15 | 2019-07-16 | 沃尔沃建筑设备公司 | Transmission for a vehicle |
| US20200182333A1 (en) * | 2018-12-11 | 2020-06-11 | GM Global Technology Operations LLC | Hybrid powertrain |
| CN111536211A (en) * | 2020-06-23 | 2020-08-14 | 北京航空航天大学 | Multi-gear planetary gear speed change device |
-
2020
- 2020-11-27 CN CN202011363403.4A patent/CN112555364B/en active Active
Patent Citations (25)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1983000201A1 (en) * | 1981-07-07 | 1983-01-20 | Windish, Willis, E. | Planetary transmission |
| US4531428A (en) * | 1983-01-10 | 1985-07-30 | Caterpillar Tractor Co. | Planetary transmission |
| US4742733A (en) * | 1984-10-04 | 1988-05-10 | Zahnradfabrik Friedrichshafen, Ag. | Control system for automatic change speed transmission |
| US5924951A (en) * | 1997-12-11 | 1999-07-20 | Caterpillar Inc. | Planetary transmission with direct drive through the front triple planetary gearsets by a single clutch |
| JP2005172123A (en) * | 2003-12-11 | 2005-06-30 | Kyowa Metal Work Co Ltd | Multi-stage shift planetary gear series |
| US20100184554A1 (en) * | 2007-09-25 | 2010-07-22 | Komatsu Ltd. | Planetary gear type gearbox |
| US20120142486A1 (en) * | 2009-08-20 | 2012-06-07 | Zf Friedrichshafen Ag | Multi-ratio transmission |
| CN103244623A (en) * | 2013-05-29 | 2013-08-14 | 新乡市恒润机电有限公司 | Nine-gear planetary automatic gearbox |
| US20140364269A1 (en) * | 2013-06-05 | 2014-12-11 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN104728365A (en) * | 2013-12-20 | 2015-06-24 | 贵州凯星液力传动机械有限公司 | Drive mechanism of hydrodynamic transmission |
| CN105697674A (en) * | 2014-12-15 | 2016-06-22 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| US20160178034A1 (en) * | 2014-12-17 | 2016-06-23 | Zf Friedrichshafen Ag | Multistep Automatic Transmission |
| US20180245670A1 (en) * | 2015-09-09 | 2018-08-30 | Volvo Construction Equipment Ab | A transmission arrangement for a vehicle |
| JP2017172717A (en) * | 2016-03-24 | 2017-09-28 | アイシン・エィ・ダブリュ株式会社 | Automatic transmission |
| US20180087621A1 (en) * | 2016-09-28 | 2018-03-29 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| DE102016222226A1 (en) * | 2016-11-11 | 2018-05-17 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US20190293153A1 (en) * | 2016-11-11 | 2019-09-26 | Zf Friedrichshafen Ag | Multispeed transmission |
| CN110023648A (en) * | 2016-12-15 | 2019-07-16 | 沃尔沃建筑设备公司 | Transmission for a vehicle |
| DE102017206829A1 (en) * | 2017-04-24 | 2018-10-25 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| US9958033B1 (en) * | 2017-05-10 | 2018-05-01 | Hyundai Motor Company | Planetary gear train of automatic transmission for vehicles |
| US20180328459A1 (en) * | 2017-05-10 | 2018-11-15 | Hyundai Motor Company | Planetary gear train of automatic transmission for vehicles |
| US20190128383A1 (en) * | 2017-10-31 | 2019-05-02 | Hyundai Motor Company | Planetary gear train of an automatic transmission for a vehicle |
| DE102017219506A1 (en) * | 2017-11-02 | 2019-05-02 | Zf Friedrichshafen Ag | 4WD automatic transmission |
| US20200182333A1 (en) * | 2018-12-11 | 2020-06-11 | GM Global Technology Operations LLC | Hybrid powertrain |
| CN111536211A (en) * | 2020-06-23 | 2020-08-14 | 北京航空航天大学 | Multi-gear planetary gear speed change device |
Non-Patent Citations (4)
| Title |
|---|
| ANONYMOUS: "《IP.COM非专利全文库》", 30 July 2015, IP.COM * |
| 蒋永富;蒋文波;冯玉平;杨吉胜;孙娟;王春梅;王春会;段洪炎;: "Allison CLBT5861型传动箱变速及受力分析" * |
| 詹长书等: "基于杠杆法计算ZF8HP 8速自动变速器传动比", 《机械传动》 * |
| 邓正思: "自动变速器行星齿轮机构的速比计算", 《汽车维修》 * |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113108032A (en) * | 2021-03-29 | 2021-07-13 | 北方汤臣传动科技有限公司 | Nine-gear planetary automatic transmission for mining truck |
| CN113108032B (en) * | 2021-03-29 | 2022-04-08 | 北方汤臣传动科技有限公司 | Nine-gear planetary automatic transmission for mining truck |
| CN115217919A (en) * | 2022-06-20 | 2022-10-21 | 陕西法士特齿轮有限责任公司 | Ten-gear transmission and vehicle |
| CN115217919B (en) * | 2022-06-20 | 2024-04-09 | 陕西法士特齿轮有限责任公司 | Ten-gear transmission and vehicle |
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