CN111765221A - Compound differential planetary mechanism of stepless speed change tractor - Google Patents
Compound differential planetary mechanism of stepless speed change tractor Download PDFInfo
- Publication number
- CN111765221A CN111765221A CN202010612617.4A CN202010612617A CN111765221A CN 111765221 A CN111765221 A CN 111765221A CN 202010612617 A CN202010612617 A CN 202010612617A CN 111765221 A CN111765221 A CN 111765221A
- Authority
- CN
- China
- Prior art keywords
- gear
- hollow shaft
- bearing
- planetary
- compound differential
- 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.)
- Granted
Links
- 150000001875 compounds Chemical class 0.000 title claims abstract description 43
- 230000007246 mechanism Effects 0.000 title claims abstract description 21
- 230000008859 change Effects 0.000 title claims abstract description 15
- 238000005192 partition Methods 0.000 claims description 39
- 230000005540 biological transmission Effects 0.000 claims description 21
- 125000006850 spacer group Chemical group 0.000 claims description 5
- 230000008844 regulatory mechanism Effects 0.000 abstract description 2
- 230000003068 static effect Effects 0.000 description 2
- 239000000446 fuel Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
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
- F16H3/46—Gearings having only two central gears, connected by 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
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
-
- 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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Retarders (AREA)
Abstract
The invention relates to a compound differential planetary mechanism of a stepless speed change tractor, which comprises a mechanical flow input gear, a hydraulic flow input gear, a first output gear, a second output gear and a compound differential planetary row, wherein the mechanical flow input gear is used for receiving a mechanical flow from an engine and driving an input sun gear of the compound differential planetary row to rotate, and the hydraulic flow input gear is used for receiving a hydraulic flow which can be subjected to stepless speed regulation and is transmitted from a CVT pump motor and driving a planetary gear ring of the compound differential planetary row to rotate, so that the mechanical flow and the hydraulic flow are converged in the compound differential planetary row to form a mechanical hydraulic double-power flow and divided into two paths of output to respectively drive the first output gear and the second output gear. The compound differential planetary mechanism of the stepless speed change tractor has the stepless speed change function, has simple structure, can realize zero rotating speed output, realizes the power parking function of the tractor, and is an ideal stepless speed change planetary speed regulation mechanism of the tractor.
Description
Technical Field
The invention belongs to the field of tractors, and particularly relates to a compound differential planetary mechanism of a stepless speed change tractor.
Background
At present, a large-horsepower wheeled tractor produced in China generally uses a meshing sleeve or a synchronizer gear shifting stepped gearbox, the operation speed can only be adjusted through the rotating speed of an engine, and the tractor is difficult to obtain the ideal working speed of various farmland operations and make full use of the power of the engine so as to work at the optimal working point; while a Continuously Variable Transmission (CVT) can achieve this. The stepless speed change transmission system has the characteristic of continuous speed ratio of the gearbox, has stable power transmission and strong adaptability, and can ensure that the engine works at the optimal economic point or the optimal power point under any condition. The tractor is particularly suitable for occasions requiring ultra-low speed, occasions requiring frequent change of tractor load and occasions having high requirements on comfort and economy, has good fuel economy, dynamic property, comfort and emission performance, can adapt to the operation of the tractor in various occasions, can realize various functions required by fine agriculture, has incomparable advantages of other transmission systems, and represents the technical development direction of future high-end tractors.
The differential planetary mechanism of the existing continuously variable transmission is formed by combining two groups of simple single planetary rows, cannot realize zero output, needs to additionally increase HST (high speed transmission) to realize a low-speed section, and has a complex structure.
Disclosure of Invention
The invention aims to provide a compound differential planetary mechanism of a stepless speed change tractor, which adopts a group of compound differential planetary rows, can realize zero rotating speed output and power parking of vehicles, and has simple structure and high efficiency.
In order to achieve the purpose, the invention adopts the technical scheme that: a compound differential planetary mechanism of a stepless speed change tractor comprises a mechanical flow input gear, a hydraulic flow input gear and a compound differential planetary row, wherein the mechanical flow input gear is arranged on a first hollow shaft, and the first hollow shaft is sleeved on an input sun gear shaft of the compound differential planetary row through a spline so as to realize the transmission of mechanical flow to the input sun gear through the first hollow shaft; the hydraulic flow input gear is mounted on the first hollow shaft, the hydraulic flow input gear and the first hollow shaft rotate relatively, and the planetary gear ring of the compound differential planetary row is sleeved on one side of the hydraulic flow input gear through a spline so as to realize the transmission of hydraulic flow to the planetary gear ring; a plurality of planet shafts are arranged on a planet carrier of the compound differential planet row, a planet duplicate gear is rotatably arranged on each planet shaft, a pinion of the planet duplicate gear is meshed with a gear of the input sun gear, and a large gear on the planet duplicate gear is meshed with a gear on the output sun gear and the planet gear ring; the planet carrier is sleeved on the second hollow shaft through a spline, the second hollow shaft is also provided with a first output gear, the third hollow shaft and the second hollow shaft are coaxially arranged, a wheel axle of the output sun gear penetrates through inner holes of the second hollow shaft and the third hollow shaft, the wheel axle of the output sun gear is connected with the third hollow shaft through a spline, and the third hollow shaft is also provided with a second output gear; the mechanical flow input gear, the first output gear and the second output gear are respectively arranged in different shell spaces.
The mechanical flow input gear is in transmission connection with the first hollow shaft through a spline, the first output gear is in transmission connection with the second hollow shaft through a spline, and the second output gear is in transmission connection with the third hollow shaft through a spline.
Three planet shafts are arranged on the planet carrier of the compound differential planet row.
A first shell partition plate and a second shell partition plate are respectively arranged on two axial sides of the mechanical flow input gear, and are respectively sleeved on the first hollow shaft through first bearings; the axial both sides of first output gear set up third casing baffle and fourth casing baffle respectively, and the third casing baffle passes through the third bearing housing to be established outside the second hollow shaft, and fourth casing baffle one side is established on the second hollow shaft through the fourth bearing housing, and the opposite side is established on the third hollow shaft through the fifth bearing housing, the axial both sides of second output gear do respectively fourth casing baffle and fifth casing baffle, the fifth casing baffle passes through the sixth bearing housing and establishes on the third hollow shaft.
The first shell partition plate is also provided with a first bearing cover, and the first bearing cover axially positions the first bearing; and a second bearing cover is arranged on the fifth shell partition plate and used for axially positioning the sixth bearing.
And a first check ring is further mounted on the wheel shaft of the input sun wheel, and the first check ring is matched with a step on the wheel shaft of the input sun wheel to axially fix the first hollow shaft.
The hydraulic flow input gear is mounted on the first hollow shaft through two second bearings, an oil retainer ring is arranged on the outer side of one second bearing and sleeved on the first hollow shaft, second retainer rings are further respectively arranged on the outer sides of the other second bearing and the oil retainer ring, and the second retainer rings are sleeved on the first hollow shaft.
The hydraulic flow input gear is provided with a third check ring, and the third check ring axially fixes the planetary gear ring; the planetary double-gear transmission mechanism is characterized in that two planetary shaft needle roller bearings are sleeved on the planetary shafts, a needle roller bearing retaining ring is arranged between the two planetary shaft needle roller bearings, the planetary double-gear is installed on the planetary shafts through the planetary shaft needle roller bearings, and a friction ring is further sleeved at the shaft ends of the planetary shafts.
One end of the second hollow shaft is sleeved with a planet carrier check ring positioned on the inner side of the planet carrier so as to axially limit the planet carrier; the second hollow shaft is also sleeved with a positioning retainer ring positioned between the third bearing and the first output gear; a bearing spacer ring positioned between the fourth bearing and the fifth bearing is arranged on the fourth shell partition plate; and two fourth check rings are arranged on the wheel shaft of the output sun wheel and are respectively positioned at two ends of the third hollow shaft, so that the axial positioning of the third hollow shaft is realized.
The mechanical hydraulic double-power flow realizes confluence in the compound differential planet row, and the specific power transmission route is as follows: the mechanical flow transmitted by the engine is transmitted to the mechanical flow input gear, and then the mechanical flow input gear drives the first hollow shaft to rotate so as to drive the input sun gear of the compound differential planet row to rotate; the hydraulic flow which is transmitted by the CVT pump motor and can be subjected to stepless speed regulation is transmitted to the hydraulic flow input gear, and then the hydraulic flow input gear drives the planetary gear ring to rotate, so that the mechanical flow at the input sun gear and the hydraulic flow at the planetary gear ring achieve power confluence in the compound differential planetary row.
The mechanical hydraulic double-power flow after confluence is output through two paths, one path of mechanical hydraulic double-power flow is output through the planet carrier, then the first output gear is driven to rotate through the second hollow shaft, the other path of mechanical hydraulic double-power flow is output through the output sun gear, and then the mechanical hydraulic double-power flow is transmitted to the second output gear through the third hollow shaft, so that the second output gear is driven to rotate.
When the rotating speed of the hydraulic flow input gear is linearly and steplessly changed, the rotating speeds of the first output gear and the second output gear are also linearly and steplessly changed, so that the function of stepless speed regulation is realized.
The invention has the following innovation points and advantages: the compound differential planetary mechanism of the stepless speed change tractor has the stepless speed change function, has simple structure, can realize zero rotating speed output, realizes the power parking function of the tractor, and is an ideal stepless speed change planetary speed regulation mechanism of the tractor.
Drawings
FIG. 1 is a schematic structural view of the present invention;
the labels in the figure are: 1. A first housing partition, 2, a first bearing, 3, a first bearing cover, 4, an input sun gear, 5, a first retaining ring, 6, a mechanical flow input gear, 7, a first hollow shaft, 8, a retaining ring, 9, a second housing partition, 10, a second bearing, 11, a hydraulic flow input gear, 12, a second retaining ring, 13, a third retaining ring, 14, a planetary ring gear, 15, a planetary shaft, 16, a needle bearing retainer, 17, a planetary double gear, 18, a planetary shaft needle bearing, 19, a friction ring, 20, a planetary shaft fixing pin, 21, a planetary carrier, 22, a planetary carrier retainer, 23, a second hollow shaft, 24, a third housing partition, 25, a third bearing, 26, a positioning retainer, 27, a first output gear, 28, a fourth housing partition, 29, a fourth bearing, 30, a bearing spacer, 31, a fifth bearing, 32, a second output gear, 33, a fifth housing partition, 34. sixth bearing, 35, third hollow shaft, 36, output sun gear, 37, fourth retaining ring, 38, second bearing cover.
Detailed Description
The present invention will be described in further detail with reference to the following drawings and examples, but the invention is not limited thereto.
Referring to the drawings, a compound differential planetary mechanism of a continuously variable transmission tractor comprises a mechanical flow input gear 6, a hydraulic flow input gear 11, a first output gear 27, a second output gear 32 and a compound differential planetary row, wherein the mechanical flow input gear 6 is used for receiving mechanical flow from an engine and driving an input sun gear 4 of the compound differential planetary row to rotate, the hydraulic flow input gear 11 is used for receiving hydraulic flow which can be adjusted in a stepless mode and is transmitted from a CVT pump motor and driving a planetary gear ring 14 of the compound differential planetary row to rotate, therefore, the mechanical flow and the hydraulic flow are combined in the compound differential planetary row to form mechanical hydraulic double-power flow and are divided into two paths to be output, and the first output gear 27 and the second output gear 32 are respectively driven.
The axle of the input sun gear 4 of the compound differential planet row is arranged in a central hole of a first hollow axle 7 in a penetrating way through a spline, one end of the axle close to the gear of the input sun gear 4 is provided with a step, the axle end of the axle is sleeved with a first retainer ring 5, and the first hollow axle 7 is positioned between the first retainer ring 5 and the step, so that the axial positioning of the first hollow axle 7 is realized; a mechanical flow input gear 6 is arranged outside the first hollow shaft 7 through a spline, the mechanical flow input gear 6 is positioned in a space formed by a first shell partition plate 1 and a second shell partition plate 9, the first shell partition plate 1 and the second shell partition plate 9 are respectively sleeved on the first hollow shaft 7 through a first bearing 2, the two first bearings 2 are respectively positioned at two axial sides of the mechanical flow input gear 6, the inner ring of the first bearing 2 is arranged on the first hollow shaft 7, the outer ring is arranged on the first shell partition plate 1 or the second shell partition plate 9, when the mechanical flow input gear 6 drives the first hollow shaft 7 and the input sun gear 4 to rotate, the first casing partition 1 and the second casing partition 9 can be relatively static, a first bearing cap 3 is also provided at the shaft end of the first hollow shaft 7, the first bearing cap 3 being mounted on the first housing partition 1 and axially delimiting the first bearing 2.
Two second bearings 10 are arranged on the first hollow shaft 7 at intervals, the inner ring of each second bearing 10 is arranged on the first hollow shaft 7, the outer ring of each second bearing 10 is fixed in the inner hole of the hydraulic flow input gear 11, the oil slinger 8 is sleeved on the first hollow shaft 7 next to one second bearing 10, and second retainer rings 12 sleeved on the first hollow shaft 7 are respectively arranged on the outer sides of the oil slinger 8 and the other second bearing 10; one end of the planetary ring gear 14 is spline-mounted on the hydraulic flow input gear 11, and the planetary ring gear 14 is axially fixed by a third ring gear 13 mounted on the hydraulic flow input gear 11.
Three planet shafts 15 are arranged on a planet carrier 21 of the compound differential planet row, the planet shafts 15 are fixed by the planet shaft fixing pins 20 which are arranged on the planet carrier 21, a needle bearing baffle ring 16 is arranged on each planet shaft 15, two axial sides of the needle bearing baffle ring 16 are respectively provided with a planet shaft needle bearing 18, the planet shaft needle bearings 18 are sleeved on the planet shafts 15, a planet duplicate gear 17 is sleeved on the planet shafts 15 through the planet shaft needle bearings 18, two axial sides of the planet duplicate gear 17 are respectively provided with a friction ring 19, and the friction rings 19 are sleeved on the planet shafts 15. The gear of the input sun gear 4 is meshed with the pinion on the planet duplicate gear 17, one side of the big gear of the planet duplicate gear 17 is meshed with the internal gear of the planet ring gear 14, and the other side is meshed with the gear of the output sun gear 36.
The axle of the output sun gear 36 penetrates through the inner holes of the second hollow axle 23 and the third hollow axle 35, the axle of the output sun gear 36 is in transmission connection with the third hollow axle 35 through splines, two fourth retaining rings 37 are sleeved on the axle of the output sun gear 36, and the two fourth retaining rings 37 are used for axially positioning the third hollow axle 35.
The planet carrier 21 is sleeved on the second hollow shaft 23 through a spline, a planet carrier retaining ring 22 is sleeved on the second hollow shaft 23, and the planet carrier retaining ring 22 is located on the inner side of the planet carrier 21 and axially locates the planet carrier 21. The first output gear 27 is sleeved on the second hollow shaft 23 through a spline, the second output gear 32 is sleeved on the third hollow shaft 35 through a spline, the first output gear 27 is located in a space formed by the third shell partition plate 24 and the fourth shell partition plate 28, the second output gear 32 is located in a space formed by the fourth shell partition plate 28 and the fifth shell partition plate 33, and the fourth shell partition plate 28 is shared by the first output gear 27 and the second output gear 32. The third shell partition 24 is connected with the outer ring of the third bearing 25, the inner ring of the third bearing 25 is fixed on the second hollow shaft 23, and a positioning retainer ring 26 is arranged between the third bearing 25 and the first output gear 27; the fourth housing partition 28 is connected to the outer ring of the fourth bearing 29 across one side of the second hollow shaft 23, and the inner ring of the fourth bearing 29 is fixedly connected to the second hollow shaft 23, so that the third housing partition 24 and the fourth housing partition 28 can be kept relatively stationary while the second hollow shaft 23 rotates. The fourth shell partition 28 is connected with the outer ring of the fifth bearing 31 by spanning one side of the third hollow shaft 35, the inner ring of the fifth bearing 31 is fixed on the third hollow shaft 35, a bearing spacer ring 30 is arranged between the fifth bearing 31 and the fourth bearing 29, and the bearing spacer ring 30 is fixed on the fourth shell partition 28. The fifth bearing 31 is located on one axial side of the second output gear 32, the other axial side of the second output gear 32 is provided with a sixth bearing 34, an inner ring of the sixth bearing 34 is fixedly connected with the third hollow shaft 35, an outer ring of the sixth bearing is connected with the fifth housing partition 33, a second bearing cover 38 is installed on the fifth housing partition 33 and axially limits the sixth bearing 34, when the output sun gear 36 rotates, the third hollow shaft 35 is driven to rotate through a spline, so that the rotation of the second output gear 32 is realized, and at the moment, the fourth housing partition 28 and the fifth housing partition 33 can be relatively static.
Mechanical hydraulic double-power flow converging implementation mode: the mechanical flow from the engine is transmitted to the mechanical flow input gear 6, then transmitted to the input sun gear 4 through the first hollow shaft 7, the hydraulic flow capable of stepless speed regulation from the CVT pump motor is transmitted to the hydraulic flow input gear 11, then transmitted to the planetary gear ring 14 in spline connection therewith, the mechanical flow at the input sun gear 4 and the hydraulic flow at the planetary gear ring 14 achieve power confluence in the compound differential planetary row, the mechanical hydraulic double power after confluence is output through two paths, one path of mechanical hydraulic double power is output through the planetary carrier 21, then transmitted to the first output gear 27 through the second hollow shaft 23, and the other path of mechanical hydraulic double power is output through the output sun gear 36, and then transmitted to the second output gear 32 through the third hollow shaft 35. The rotating speed of the hydraulic flow input gear 11 is linearly and steplessly changed, and the rotating speeds of the first output gear 27 and the second output gear 32 are also linearly and steplessly changed, so that the stepless speed regulating function is realized.
The above embodiments are only intended to illustrate the technical solution of the present invention and not to limit the same, and it should be understood by those of ordinary skill in the art that the specific embodiments of the present invention can be modified or substituted with equivalents with reference to the above embodiments, and any modifications or equivalents without departing from the spirit and scope of the present invention are within the scope of the claims to be appended.
Claims (9)
1. A compound differential planetary mechanism of a stepless speed change tractor comprises a mechanical flow input gear, a hydraulic flow input gear and a compound differential planetary row, and is characterized in that: the mechanical flow input gear is arranged on a first hollow shaft, and the first hollow shaft is sleeved on an input sun gear shaft of the compound differential planet row through a spline so as to realize the transmission of mechanical flow to the input sun gear through the first hollow shaft; the hydraulic flow input gear is mounted on the first hollow shaft, the hydraulic flow input gear and the first hollow shaft rotate relatively, and the planetary gear ring of the compound differential planetary row is sleeved on one side of the hydraulic flow input gear through a spline so as to realize the transmission of hydraulic flow to the planetary gear ring; a plurality of planet shafts are arranged on a planet carrier of the compound differential planet row, a planet duplicate gear is rotatably arranged on each planet shaft, a pinion of the planet duplicate gear is meshed with a gear of the input sun gear, and a large gear on the planet duplicate gear is meshed with a gear on the output sun gear and the planet gear ring; the planet carrier is sleeved on the second hollow shaft through a spline, the second hollow shaft is also provided with a first output gear, the third hollow shaft and the second hollow shaft are coaxially arranged, a wheel axle of the output sun gear penetrates through inner holes of the second hollow shaft and the third hollow shaft, the wheel axle of the output sun gear is connected with the third hollow shaft through a spline, and the third hollow shaft is also provided with a second output gear; the mechanical flow input gear, the first output gear and the second output gear are respectively arranged in different shell spaces.
2. The compound differential planetary mechanism of a continuously variable tractor according to claim 1, characterized in that: the mechanical flow input gear is in transmission connection with the first hollow shaft through a spline, the first output gear is in transmission connection with the second hollow shaft through a spline, and the second output gear is in transmission connection with the third hollow shaft through a spline.
3. The compound differential planetary mechanism of a continuously variable tractor according to claim 1, characterized in that: three planet shafts are arranged on the planet carrier of the compound differential planet row.
4. The compound differential planetary mechanism of a continuously variable tractor according to claim 1, characterized in that: a first shell partition plate and a second shell partition plate are respectively arranged on two axial sides of the mechanical flow input gear, and are respectively sleeved on the first hollow shaft through first bearings; the axial both sides of first output gear set up third casing baffle and fourth casing baffle respectively, and the third casing baffle is established through the third bearing housing on the second hollow shaft, fourth casing baffle one side is established on the second hollow shaft through the fourth bearing housing, and the opposite side is established on the third hollow shaft through the fifth bearing housing, the axial both sides of second output gear be respectively fourth casing baffle and fifth casing baffle, the fifth casing baffle is established on the third hollow shaft through the sixth bearing housing.
5. The compound differential planetary mechanism of a continuously variable tractor according to claim 4, characterized in that: the first shell partition plate is also provided with a first bearing cover, and the first bearing cover axially positions the first bearing; and a second bearing cover is arranged on the fifth shell partition plate and used for axially positioning the sixth bearing.
6. The compound differential planetary mechanism of a continuously variable tractor according to claim 4, characterized in that: one end of the second hollow shaft is sleeved with a planet carrier check ring positioned on the inner side of the planet carrier so as to axially limit the planet carrier; the second hollow shaft is also sleeved with a positioning retainer ring positioned between the third bearing and the first output gear; a bearing spacer ring positioned between the fourth bearing and the fifth bearing is arranged on the fourth shell partition plate; and two fourth check rings are arranged on the wheel shaft of the output sun wheel and are respectively positioned at two ends of the third hollow shaft, so that the axial positioning of the third hollow shaft is realized.
7. The compound differential planetary mechanism of a continuously variable tractor according to claim 1, characterized in that: and a first check ring is further mounted on the wheel shaft of the input sun wheel, and the first check ring is matched with a step on the wheel shaft of the input sun wheel to axially fix the first hollow shaft.
8. The compound differential planetary mechanism of a continuously variable tractor according to claim 1, characterized in that: the hydraulic flow input gear is mounted on the first hollow shaft through two second bearings, an oil retainer ring is arranged on the outer side of one second bearing and sleeved on the first hollow shaft, second retainer rings are further respectively arranged on the outer sides of the other second bearing and the oil retainer ring, and the second retainer rings are sleeved on the first hollow shaft.
9. The compound differential planetary mechanism of a continuously variable tractor according to claim 1, characterized in that: the hydraulic flow input gear is provided with a third check ring, and the third check ring axially fixes the planetary gear ring; the planetary double-gear transmission mechanism is characterized in that two planetary shaft needle roller bearings are sleeved on the planetary shafts, a needle roller bearing retaining ring is arranged between the two planetary shaft needle roller bearings, the planetary double-gear is installed on the planetary shafts through the planetary shaft needle roller bearings, and a friction ring is further sleeved at the shaft ends of the planetary shafts.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010612617.4A CN111765221B (en) | 2020-06-30 | 2020-06-30 | Compound differential planetary mechanism of stepless speed change tractor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010612617.4A CN111765221B (en) | 2020-06-30 | 2020-06-30 | Compound differential planetary mechanism of stepless speed change tractor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN111765221A true CN111765221A (en) | 2020-10-13 |
| CN111765221B CN111765221B (en) | 2024-04-19 |
Family
ID=72724185
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010612617.4A Active CN111765221B (en) | 2020-06-30 | 2020-06-30 | Compound differential planetary mechanism of stepless speed change tractor |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111765221B (en) |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1896562A (en) * | 1999-11-12 | 2007-01-17 | 福尔布鲁克科技公司 | Continuously variable transmission |
| JP2011017329A (en) * | 2009-07-07 | 2011-01-27 | Takashi Matsuda | Two-cylinder one-crank pin type multiple cylinder cycloid reciprocating engine using planetary gear double eccentric disk |
| CN212509378U (en) * | 2020-06-30 | 2021-02-09 | 第一拖拉机股份有限公司 | Compound differential planetary mechanism of stepless speed change tractor |
-
2020
- 2020-06-30 CN CN202010612617.4A patent/CN111765221B/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1896562A (en) * | 1999-11-12 | 2007-01-17 | 福尔布鲁克科技公司 | Continuously variable transmission |
| JP2011017329A (en) * | 2009-07-07 | 2011-01-27 | Takashi Matsuda | Two-cylinder one-crank pin type multiple cylinder cycloid reciprocating engine using planetary gear double eccentric disk |
| CN212509378U (en) * | 2020-06-30 | 2021-02-09 | 第一拖拉机股份有限公司 | Compound differential planetary mechanism of stepless speed change tractor |
Also Published As
| Publication number | Publication date |
|---|---|
| CN111765221B (en) | 2024-04-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR101575272B1 (en) | Transmission system of hybrid electric vehicle | |
| US11441652B2 (en) | Multi-speed gearbox with high torque ratio and the drive axle made therewith | |
| CN109185417B (en) | Quick reversing power-dividing hydraulic mechanical stepless speed changer | |
| US11156271B2 (en) | Power unit for bionic robot, robot joint, and robot | |
| US20020040621A1 (en) | Gearbox, particularly for automotive vehicle with telescopic load-carrying arm | |
| CN110962570B (en) | Hybrid power driving system and vehicle | |
| US4003273A (en) | Multi-ratio transmission systems | |
| CN218777413U (en) | Electric drive bridge structure driven by single motor | |
| CN212509378U (en) | Compound differential planetary mechanism of stepless speed change tractor | |
| CN107542863B (en) | Three-planetary-row hybrid power two-gear automatic transmission assembly | |
| CN106678326B (en) | Hydraulic speed variator for light vehicle | |
| CN111765221B (en) | Compound differential planetary mechanism of stepless speed change tractor | |
| CN111271427A (en) | Integral double HST planetary differential steering gearbox | |
| US4028965A (en) | Multiple ratio power transmission mechanism adapted for improved engine fuel economy and high/low ratio traction | |
| CN212073679U (en) | Independent pump motor driving device of stepless speed change tractor | |
| CN211820623U (en) | Integrated gearbox planetary differential device | |
| CN210889972U (en) | Nested combined type main shaft of HMCVT | |
| CN115949716B (en) | Hydraulic mechanical compound stepless transmission device for high-speed engineering vehicle | |
| CN218267191U (en) | Three-speed input and output same-side power gear shifting mechanism | |
| CN212804170U (en) | Lubricating structure of compound differential planetary mechanism of stepless speed change tractor | |
| CN219139736U (en) | Stepless speed change harvester gearbox | |
| CN111204210B (en) | Independent pump motor driving device of stepless speed change tractor | |
| US4455891A (en) | Power transmission configuration having continuous variable progression of gear reduction ratios | |
| CN220791944U (en) | Continuously variable transmission of special vehicle | |
| CN220622622U (en) | Continuously variable planetary gear set transmission mechanism |
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 |