CN111981092B - 26-gear PST full-load gear shifting speed change device for tractor - Google Patents
26-gear PST full-load gear shifting speed change device for tractor Download PDFInfo
- Publication number
- CN111981092B CN111981092B CN202010817970.6A CN202010817970A CN111981092B CN 111981092 B CN111981092 B CN 111981092B CN 202010817970 A CN202010817970 A CN 202010817970A CN 111981092 B CN111981092 B CN 111981092B
- Authority
- CN
- China
- Prior art keywords
- stage
- gear
- sun gear
- brake
- planetary
- 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.)
- Active
Links
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
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0078—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratio comprising twelve or more forward speeds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/0082—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
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital 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
- 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
- F16H2200/2058—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eleven engaging means
-
- 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
- F16H2716/00—Control devices for speed-change mechanisms of planetary gearings, with toothed wheels remaining engaged, e.g. also for devices to simplify the control or for synchronising devices combined with control devices
- F16H2716/04—Control devices for speed-change mechanisms of planetary gearings, with toothed wheels remaining engaged, e.g. also for devices to simplify the control or for synchronising devices combined with control devices the control being hydraulic or pneumatic
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A26-gear PST full-load gear shifting speed change device for a tractor relates to a speed change device for the tractor, and the device comprises a three-stage transmission combination device; the power of a clutch C1 (35) of the first-stage device is directly transmitted to a second-stage small sun gear (14) with a shaft; the power of the clutch C3 (33) is directly transmitted to the secondary large sun gear (11); the power of the brake B1 (32) is transmitted to the primary annular gear (9) through the planetary mechanism in a speed increasing way and then transmitted to the secondary large sun gear (11); the power of the brake B2 (31) is transmitted to the primary annular gear (9) through the planetary mechanism in a speed increasing way and then transmitted to the secondary large sun gear (11); clutch C1 (35) and clutch C2 (34) are simultaneously engaged; the secondary small sun gear (14) with the shaft of the secondary device is driven, and the secondary small annular gear (12) is locked by the brake B3 (30). The speed changing device is formed by three-stage planetary transmission in series, and eleven hydraulic control elements are respectively controlled by a gear shifting valve. The gear shifting operation is simple and quick, other gears except the first three gears are basically arranged in an geometric progression, and the requirements of farm tools on the speed of the tractor can be fully met.
Description
Technical Field
The invention relates to a tractor speed change device, in particular to a 26-gear PST full-load gear shift speed change device for a tractor.
Background
The transmission device of the tractor is an important component of the tractor, and the transmission device can not well meet the requirements of agricultural machinery, fully exert the efficiency of a unit, perfectly complete field operation and serve agricultural production. Meanwhile, the method is also more, faster, better and less expensive.
Because the gears of the traditional tractor are few, when a certain farm tool is carried, the selection of the speed is limited, and the speed is either fast or slow. Moreover, some time is consumed for shifting, and shifting is stopped.
Disclosure of Invention
The invention aims to provide a 26-gear PST full-load gear shifting speed change device for a tractor, which is formed by three-stage planetary transmission in series, wherein eleven hydraulic control elements are respectively controlled by a gear shifting valve. The gear shifting operation is simple and quick, other gears except the first three gears are basically arranged in an geometric progression, and the requirements of farm tools on the speed of the tractor can be fully met.
The invention aims at realizing the following technical scheme:
a 26-speed PST full load shift transmission for a tractor, the device comprising a three stage transmission combination; the power of a clutch C1 of the first-stage device is directly transmitted to a second-stage small sun gear with a shaft; the power of the clutch C3 is directly transmitted to the secondary large sun gear; the power of the brake B1 is accelerated by a planetary mechanism and is transmitted to the primary annular gear and then to the secondary large sun gear; the power of the brake B2 is accelerated by a planetary mechanism and is transmitted to the primary annular gear and then transmitted to the secondary large sun gear; the clutch C1 and the clutch C2 are combined at the same time; the second-stage small sun gear of the second-stage device is driven, the second-stage small inner gear ring is locked by a brake B3, the second-stage small sun gear of the second-stage device is driven, the second-stage large inner gear ring is locked by a brake B4, the second-stage large sun gear is driven, the second-stage small inner gear ring is locked by the brake B3, the second-stage large inner gear ring is locked by the brake B4, and the second-stage large sun gear has three different speeds, so six different speeds can be obtained through the second-stage large planet carrier in two different braking states, the second-stage small sun gear of the second-stage small inner gear shaft and the second-stage large sun gear simultaneously perform driving rotation, and the rotation speeds of the second-stage small sun gear of the second-stage small inner gear ring and the second-stage large sun gear are both 1; the three-stage clutch C4 of the third-stage device is combined, the whole planetary mechanism becomes a solid whole, so that the rotation obtained by the two-stage big planetary frame is transmitted to the three-stage big sun gear in a ratio of 1 to 1, the brake B7 is combined, the two-stage big planetary frame rotates around the sun gear in the three stages fixed by the brake B7 with the whole planetary mechanism, the power is output by the three-stage big sun gear, the brake B5 is combined, the two-stage big planetary frame rotates in the three-stage inner gear fixed by the brake B5 with the whole planetary mechanism, and the three-stage big sun gear outputs the rotating speed according to minus 0.928; and when the brake B6 is combined, the two-stage large planet carrier rotates around the three-stage small sun gear fixed by the brake B6 with the whole planetary mechanism, and the three-stage large sun gear outputs rotating speed according to the ratio of 1 to 0.571.
The 26-gear PST full-load gear shifting speed change device for the tractor comprises a supporting shaft, a first-stage planet carrier, a first-stage small sun gear with a shaft, a first-stage large sun gear with a shaft, a first-stage triple planetary gear, a first-stage planetary gear shaft, a first-stage annular gear, a clutch C1, a clutch C2, a clutch C3, a brake B1, a brake B2 and a second-stage small sun gear with a shaft.
The planetary mechanism of the second-stage device comprises a second-stage big planet carrier, a second-stage small sun gear with a shaft, a second-stage big sun gear, a second-stage duplex planetary gear, a second-stage planetary gear shaft, a second-stage small inner gear ring, a second-stage big inner gear ring, a brake B3 and a brake B4.
The planetary mechanism of the third-stage device comprises a two-stage big planetary frame, a three-stage big sun gear, a three-stage middle sun gear, a three-stage small sun gear, a three-stage duplex small planetary gear, a three-stage big planetary gear, a three-stage small planetary gear, a three-stage planetary gear shaft, a three-stage big planetary gear shaft, a three-stage small planetary gear shaft, a three-stage annular gear, a brake B5, a clutch C4 brake B6 and a brake B7.
The invention has the advantages and effects that:
the speed changing device is formed by three-stage planetary transmission in series, and eleven hydraulic control elements are respectively controlled by a gear shifting valve. The gear shifting operation is simple and quick, other gears except the first three gears are basically arranged in an geometric progression, and the requirements of farm tools on the speed of the tractor can be fully met. The 26-gear PST full-load gear shifting speed changing device can meet the operation requirements under various complex conditions, the speed of the tractor can be conveniently switched in the running process, and the operation efficiency is greatly improved.
The design of the duplex planetary gear is very critical, so that the duplex planetary gear can be assembled well, three triplex gears are arranged in the first stage, and three duplex gears are arranged in the second stage, thereby reducing the manufacturing cost, improving the overall performance of the transmission device and greatly reducing the maintenance cost.
Drawings
FIG. 1 is a schematic illustration of a 26 speed change of a transmission of the present invention;
FIG. 2 is a schematic structural view of a transmission according to the present invention;
FIG. 3 is a schematic diagram of the transmission principle of the transmission of the present invention;
FIG. 4 is an isometric view of a transmission of the present invention;
fig. 5 is an isometric view of a third stage planetary mechanism of the present invention.
The components in the figure: the support shaft 1, the primary planet gear shaft 2, the primary triple planetary gear 3, the primary large sun gear 4 with a shaft, the primary small sun gear 5 with a shaft, the secondary planet gear shaft 6, the primary planet carrier 7, the secondary double planetary gear 8, the primary annular gear 9, the tertiary planet gear shaft 10, the secondary large sun gear 11, the secondary small annular gear 12, the secondary large annular gear 13, the secondary small sun gear 14 with a shaft, the tertiary large planet gear shaft 15, the tertiary annular gear 16, the tertiary large sun gear 17, the tertiary large planet gear 18, the tertiary medium sun gear 19, the tertiary small sun gear 20, the tertiary double small planet gear 21, the tertiary small planet gear 22, the secondary large planet carrier 23, the tertiary small planet gear shaft 24, the brake B7 25, the brake B6 26, the tertiary clutch C4 27, the brake B5 28, the brake B4 29, the brake B3 30, the brake B2, the brake B1 32, the clutch C3 33, the clutch C2 and the clutch C1 35.
Detailed Description
The present invention will be described in detail with reference to the embodiments shown in the drawings.
The gear set of the invention is formed by three-stage planetary transmission in series, and other gears are arranged in an equal ratio series except the first three gears. In addition to good power performance, it is necessary to ensure ease of assembly and ease of assembly, for example, three triple gears in the first stage and three double gears in the second stage.
The installation sequence of the invention is as follows: firstly, a supporting shaft is installed, a small sun gear with a second-level belt shaft is installed, a large second-level sun gear is installed,
the novel planetary gear comprises a primary annular gear, a primary planet carrier, a primary small sun gear with a shaft, a primary large sun gear with a shaft, a primary planetary gear and a primary planetary gear shaft, a brake B2, a brake B1, a clutch C3, a clutch C2, a clutch C1, a secondary small annular gear, a large planet carrier, a secondary double planetary gear and a shaft, a secondary small annular gear, a brake B3, a secondary large annular gear, a brake B4, a tertiary large sun gear, a tertiary medium sun gear, a tertiary small sun gear, a front small double planetary gear, a rear small planetary gear, a middle double planetary gear, a tertiary annular gear, a brake B, a clutch C4, a brake B6 and a brake B7.
Example 1
In the present invention, C represents a clutch and B represents a brake.
First stage:
first stage: the planetary gear transmission mechanism consists of a support shaft 1, a primary planet carrier 7, a primary small sun gear 5 with a shaft, a primary large sun gear 4 with a shaft, a primary triple planetary gear 3, a primary planetary gear shaft 2, a primary annular gear 9, a clutch C1 35, a clutch C2 34, a clutch C3 33, a brake B1 32, a brake B2 31 and a secondary small sun gear 14 with a shaft.
1. The clutch C1 35 is directly connected with power to the secondary small sun gear 14 with the shaft.
2. Clutch C2 34 is engaged:
2.1. clutch C3 is engaged-power is directly sent to the secondary large sun gear 11. The speed ratio is 1 to 1.
2.2. Brake B1 32 combines-power is transferred to primary ring gear 9 through planetary mechanism acceleration and then to secondary large sun gear 11, and speed is increased from 1 to 1.102.
2.3. The brake B2 31 is combined, the power is transmitted to the primary annular gear 9 through the planetary mechanism in a speed increasing way, and then transmitted to the secondary large sun gear 11, and the speed is increased from 1 to 1.206.
3. The clutches C1 and C2 and C35 and 34 are simultaneously engaged. (there are the following three cases respectively)
3.1. Clutch C3 is engaged-the planetary mechanism becomes a solid whole, transmitting power 1 to the secondary large sun gear 11. At the same time, clutch C1 35 transmits power in a 1 to 1 ratio to the secondary, small, sun gear 14.
3.2. The brake B1 32 is combined, the power is increased through a planetary mechanism and is transmitted to the primary annular gear 9 and then to the secondary large sun gear 11, and the speed is increased from 1 to 1.102. Simultaneously, the clutch C1 35 transmits power to the secondary small male wheel 14 with the shaft according to the ratio of 1 to 1.
3.3. The brake B2 31 combines with the power, the power is increased through the planetary mechanism and is transmitted to the primary annular gear 9 and then to the secondary large sun gear 11, and the speed is increased from 1 to 1.206. At the same time, clutch C1 35 transmits power to the secondary small sun gear 14 with shaft in a 1 to 1 ratio.
Second stage:
second-stage planetary mechanism: the planetary gear consists of a second-level large planet carrier 23, a second-level small sun gear 14 with a shaft, a second-level large sun gear 11, a second-level duplex planetary gear 8, a second-level planetary gear shaft 6, a second-level small annular gear 12, a second-level large annular gear 13, a brake B3 30 and a brake B4 29.
1. When the secondary small sun gear 14 with the shaft is driven, the secondary small inner gear ring 12 is locked by the brake B3, so that the rotating speed obtained by the secondary large planet carrier 23 is 0.143.
2. When the secondary small sun gear 14 with the shaft is driven, the secondary large annular gear 13 is locked by the brake B4 29, so that the rotating speed obtained by the secondary large planet carrier 23 is 0.210.
3. When the second-stage large sun gear 11 is driven, the second-stage small annular gear 12 is locked by the brake B3, so that the rotation speed obtained by the second-stage large planet carrier 23 is 0.351.
4. When the secondary large sun gear 11 is active, the secondary large annular gear 13 is locked by the brake B4 29, so that the rotation speed obtained by the secondary large planet carrier 23 is 0.463.
Because the secondary large sun gear 11 has three different speeds, six different speeds are obtained by the two different braking states of the secondary large carrier 23.
Because the secondary, small, sun gear 14 has only one speed, two different speeds are achieved by the two different braking states of the secondary, tertiary, large planet carrier 23.
5. When the secondary small sun gear 14 with the shaft and the secondary large sun gear 11 simultaneously do active rotation, and the brake B3 and the brake B4 do not work:
5.1. when the rotation speeds of the secondary small sun gear 14 with the shaft and the secondary large sun gear 11 are the same, the rotation speed of the secondary large planet carrier is 1.
5.2. When the rotation speed of the secondary small sun gear 14 with the shaft is 1 and the rotation speed of the secondary large sun gear 11 is 1.102, the rotation speed of the secondary large planet carrier 23 is 1.148.
5.3. When the rotation speed of the secondary small sun gear 14 with the shaft is 1 and the rotation speed of the secondary large sun gear 11 is 1.206, the output rotation speed of the secondary large planet carrier 23 is 1.298.
Therefore, in the two-stage planetary mechanismThe speed of the end, i.e. the second three-stage large planet carrier 23, is 32+2+3=11 different variations.
Third stage:
third-stage planetary mechanism: the three-stage planetary gear system consists of a two-stage large planet carrier 23, a three-stage large sun gear 17, a three-stage middle sun gear 19, a three-stage small sun gear 20, a three-stage duplex small planet gear 21, a three-stage large planet gear 18, a three-stage small planet gear 22, a three-stage planet gear shaft 10, a three-stage large planet gear shaft 15, a three-stage small planet gear shaft 24, a three-stage annular gear 16, a brake B5 28, a clutch C4, a brake B6, and a brake B7.
The third stage planetary mechanism has four different states:
1. when clutch C4 27 is engaged, the entire planetary mechanism becomes a solid whole, so that the rotation obtained by the second three-stage large carrier 23 is transmitted to the third large sun gear 17 in a ratio of 1 to 1.
2. When the brake B7 is engaged, the two-three-stage large planet carrier rotates with the whole planetary mechanism around the three-stage medium sun gear 19 fixed by the brake B7, and power is output by the three-stage large sun gear 17 at a speed of 1.643. (the second three-stage large planet carrier 23 is 1, and the third large sun gear 17 is 1.643).
3. When the brake B5 28 is combined, the second-third-stage large planet carrier 23 rotates in the third-stage annular gear 16 fixed by the brake B5 28 with the whole planetary mechanism, and the third-stage large sun gear 17 outputs the rotating speed according to-0.928. (the second three-stage big planet carrier 23 is 1, the third three-stage big sun gear 17 is-0.928, which is reverse gear)
4. When the brake B6 is combined, the two-stage big planet carrier 23 rotates around the three-stage small sun gear 20 fixed by the brake B6 with the whole planetary mechanism, and the three-stage big sun gear 17 outputs rotating speed according to the ratio of 1 to 0.571. (the second three-stage big planet carrier is 1, and the third-stage big sun gear 17 is 0.571).
11 can be obtained at the output end of the third-stage planetary mechanism3 advancesAnd the speed is 11 reverse speeds, and the non-ideal gears are removed through selection, so that 26 forward gears and 8 reverse gears are obtained.
Tractor operating speed, as shown in the following table: kilometers per hour
The control system works as follows:
note that: the speed coefficient is the inverse of the transmission ratio. I.e. speed coefficient = 1/gear ratio.
Claims (4)
1. A 26-gear PST full-load gear shifting speed changing device for a tractor, which is characterized by comprising a three-stage transmission combination device; the power of a clutch C1 (35) of the first-stage device is directly transmitted to a second-stage small sun gear (14) with a shaft; the power of the clutch C3 (33) is directly transmitted to the secondary large sun gear (11); the power of the brake B1 (32) is transmitted to the primary annular gear (9) through the first-stage planetary mechanism in a speed increasing way and then transmitted to the secondary large sun gear (11); the power of the brake B2 (31) is transmitted to the primary annular gear (9) through the first-stage planetary mechanism in a speed increasing way and then transmitted to the secondary large sun gear (11); clutch C1 (35) and clutch C2 (34) are simultaneously engaged; the second-stage small sun gear (14) of the second-stage device is driven, the second-stage small inner gear ring (12) is locked by a brake B3 (30), the second-stage small sun gear (14) is driven, the second-stage large inner gear ring (13) is locked by a brake B4 (29), the second-stage large sun gear (11) is driven, the second-stage small inner gear ring (12) is locked by the brake B3 (30), the second-stage large sun gear (11) is driven, the second-stage large inner gear ring (13) is locked by the brake B4 (29), and the second-stage large sun gear (11) has three different speeds, so six different speeds are obtained through the two different braking states of the second-stage large planet carrier (23), the second-stage small sun gear (14) with the second-stage large inner gear ring gear (11) and the second-stage large sun gear (11) are simultaneously driven to rotate, and the rotating speeds of the second-stage small sun gear (14) with the second-stage large sun gear (11) are the same as 1; the three-stage clutch C4 (27) of the third-stage device is combined, the third-stage planetary mechanism becomes a solid whole, so that the rotation obtained by the two-stage big planetary frame (23) is transmitted to the three-stage big sun gear (17) in a ratio of 1 to 1, the brake B7 (25) is combined, the two-stage big planetary frame rotates around the three-stage middle sun gear (19) fixed by the brake B7 (25) with the whole planetary mechanism, power is output by the three-stage big sun gear (17), the brake B5 (28) is combined, the two-stage big planetary frame (23) rotates in the three-stage inner gear ring (16) fixed by the brake B5 (28), and the three-stage big sun gear (17) outputs a rotating speed according to minus 0.928; when the brake B6 (26) is combined, the two-stage big planet carrier (23) rotates around the three-stage small sun gear (20) fixed by the brake B6 (26) with the whole planetary mechanism, and the three-stage big sun gear (17) outputs rotating speed according to the ratio of 1 to 0.571.
2. The 26-gear PST full-load gear shifting speed change device for the tractor, which is disclosed in claim 1, is characterized in that the first-stage device comprises a supporting shaft (1), a first-stage planet carrier (7), a first-stage small sun gear with a shaft (5), a first-stage large sun gear with a shaft (4), a first-stage triple planetary gear (3), a first-stage planetary gear shaft (2), a first-stage annular gear (9), a clutch C1 (35), a clutch C2 (34), a clutch C3 (33), a brake B1 (32), a brake B2 (31) and a second-stage small sun gear with a shaft (14).
3. The 26-gear PST full-load gear shifting speed changing device for the tractor, according to claim 1, is characterized in that the planetary mechanism of the second-stage device comprises a second-stage big planetary carrier (23), a second-stage small sun gear with a shaft (14), a second-stage big sun gear (11), a second-stage duplex planetary gear (8), a second-stage planetary gear shaft (6), a second-stage small annular gear (12), a second-stage big annular gear (13), a brake B3 (30) and a brake B4 (29).
4. The 26-gear PST full-load gear shifting transmission for the tractor, according to claim 1, is characterized in that the planetary mechanism of the third-stage device comprises a two-stage large planetary frame (23), a three-stage large sun gear (17), a three-stage middle sun gear (19), a three-stage small sun gear (20), a three-stage duplex small planetary gear (21), a three-stage large planetary gear (18), a three-stage small planetary gear (22), a three-stage planetary gear shaft (10), a three-stage large planetary gear shaft (15), a three-stage small planetary gear shaft (24), a three-stage inner gear ring (16), a brake B5 (28), a clutch C4 (27), a brake B6 (26) and a brake B7 (25).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010817970.6A CN111981092B (en) | 2020-08-14 | 2020-08-14 | 26-gear PST full-load gear shifting speed change device for tractor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010817970.6A CN111981092B (en) | 2020-08-14 | 2020-08-14 | 26-gear PST full-load gear shifting speed change device for tractor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111981092A CN111981092A (en) | 2020-11-24 |
| CN111981092B true CN111981092B (en) | 2023-08-01 |
Family
ID=73434435
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010817970.6A Active CN111981092B (en) | 2020-08-14 | 2020-08-14 | 26-gear PST full-load gear shifting speed change device for tractor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111981092B (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0276954A (en) * | 1988-09-09 | 1990-03-16 | Toyota Motor Corp | Planetary gear type transmission |
| JPH08261299A (en) * | 1995-03-27 | 1996-10-08 | Jatco Corp | Planetary gear train for automatic transmission and gear speed changer for automatic transmission |
| CN102089551A (en) * | 2008-09-09 | 2011-06-08 | 腓特烈斯港齿轮工厂股份公司 | Hybrid drive train of a motor 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 |
| KR101817536B1 (en) * | 2016-07-04 | 2018-02-21 | 안동대학교 산학협력단 | Transmission apparatus for vehicles |
| KR101897971B1 (en) * | 2017-07-12 | 2018-09-12 | 안동대학교 산학협력단 | Transmission apparatus for vehicles |
| CN109798333A (en) * | 2019-03-14 | 2019-05-24 | 吉林大学 | A kind of tractor full power shift and the gearbox that commutates |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20110177911A1 (en) * | 2010-01-20 | 2011-07-21 | Alexander Serkh | Planetary gear mechanism for a bicycle |
-
2020
- 2020-08-14 CN CN202010817970.6A patent/CN111981092B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0276954A (en) * | 1988-09-09 | 1990-03-16 | Toyota Motor Corp | Planetary gear type transmission |
| JPH08261299A (en) * | 1995-03-27 | 1996-10-08 | Jatco Corp | Planetary gear train for automatic transmission and gear speed changer for automatic transmission |
| CN102089551A (en) * | 2008-09-09 | 2011-06-08 | 腓特烈斯港齿轮工厂股份公司 | Hybrid drive train of a motor 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 |
| KR101817536B1 (en) * | 2016-07-04 | 2018-02-21 | 안동대학교 산학협력단 | Transmission apparatus for vehicles |
| KR101897971B1 (en) * | 2017-07-12 | 2018-09-12 | 안동대학교 산학협력단 | Transmission apparatus for vehicles |
| CN109798333A (en) * | 2019-03-14 | 2019-05-24 | 吉林大学 | A kind of tractor full power shift and the gearbox that commutates |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111981092A (en) | 2020-11-24 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US3897697A (en) | Infinitely variable drive ratio hydro-mechanical transmission for vehicles or the like | |
| US5813488A (en) | Electric wheel drive for a utility vehicle | |
| JP4294429B2 (en) | Power split type two-range transmission | |
| CN110617312B (en) | All-gear stepless automatic speed change and speed ratio active control system | |
| CN107654605B (en) | Single-row compound planetary gear type multi-section hydraulic mechanical stepless transmission | |
| KR20120055978A (en) | continuous variable transmission for use a vehicle | |
| CN109681591B (en) | Four-gear planetary speed change mechanism | |
| JPS6343620B2 (en) | ||
| CN103527732A (en) | Seven-gear planet automatic gearbox | |
| CN107893838B (en) | Multi-section multi-mode continuously variable transmission for high-power vehicle | |
| CN108488333B (en) | Full power gear shifting gearbox of tractor | |
| CN109519512B (en) | Hydraulic power split stepless gearbox of tractor and use method | |
| CN103925345A (en) | Electric driving planetary transmission | |
| CN113561748A (en) | Electric drive axle system | |
| CN111981092B (en) | 26-gear PST full-load gear shifting speed change device for tractor | |
| CN205503881U (en) | Novel ten grades of automatic gearbox drive mechanism | |
| CN104595453A (en) | Self-adaptation stepless speed changing box of hydraulic planetary gear | |
| CN109578544B (en) | Single-planet-row multi-mode hydraulic mechanical stepless speed changer | |
| CN109751381B (en) | Multifunctional stepless speed change transmission device | |
| CN115325116B (en) | Multi-gear planetary gear transmission device | |
| CN115325117A (en) | Large speed ratio, multi-gear automatic transmission | |
| CN214838192U (en) | Speed change mechanism for high-speed and low-speed two-gear transmission | |
| CN209638337U (en) | Planet and dead axle compound variable speed mechanism | |
| CN111306262B (en) | Four-gear speed change mechanism | |
| CN209781609U (en) | 2-stage type friction starting hydraulic shunting stepless gearbox |
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 | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |