CN209781609U - 2-stage type friction starting hydraulic shunting stepless gearbox - Google Patents
2-stage type friction starting hydraulic shunting stepless gearbox Download PDFInfo
- Publication number
- CN209781609U CN209781609U CN201920609434.XU CN201920609434U CN209781609U CN 209781609 U CN209781609 U CN 209781609U CN 201920609434 U CN201920609434 U CN 201920609434U CN 209781609 U CN209781609 U CN 209781609U
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Abstract
The utility model relates to a 2-segment type friction starting hydraulic pressure shunting stepless gearbox, which comprises a power input shaft, a pump control hydraulic motor, a confluence planet bar and a power output shaft, wherein the power input shaft is provided with a pump shaft I gear, an L-segment I gear and an H-segment I gear; a pump shaft II gear is arranged on a pump shaft of the hydraulic motor, and a motor shaft L-I gear and a motor shaft H-I gear are connected to a motor shaft of the pump control hydraulic motor; the confluence planet bar comprises a sun gear, a gear ring and a planet gear, and an H section II gear and an L section II gear are connected to a gear ring shaft; a motor shaft L-II gear and a motor shaft H-II gear are arranged on the sun wheel shaft; an F-gear I gear and an R-gear I gear are fixedly arranged on the planet carrier shaft; and the power output shaft is connected with an F-gear II gear and an R-gear II gear. The utility model discloses an introduce two fender positions in the gear drive between motor shaft and sun gear axle, make the gearbox realize two adjacent stepless speed regulation district section drive ratio control range's unequal differential configuration, improved the travel and the acceleration performance of tractor.
Description
Technical Field
the utility model relates to a gearbox technical field especially involves hydraulic pressure reposition of redundant personnel buncher field, specifically indicates a 2 section formula cunning starts hydraulic pressure reposition of redundant personnel buncher.
Background
The tractor hydraulic pressure reposition of redundant personnel infinitely variable transmission's drive power is big, and the overall transmission efficiency is high, is ideal tractor stepless speed control system. The pump-controlled hydraulic motor is limited by larger energy loss, and a plurality of sections are commonly adopted to realize regional stepless speed regulation at present, so that the stepless speed regulation range is expanded, and the hydraulic power split level is limited. If the multi-section scheme is matched with a multi-planet-row confluence design, a stable section changing effect can be obtained, but the structure is complex, the miniaturization is difficult, and the application cost is high.
Disclosure of Invention
The utility model discloses to prior art's not enough, provide a 2 section formula cunning start hydraulic pressure reposition of redundant personnel buncher, realized two adjacent infinitely variable speed district section drive ratio control range's unequal error configuration to improve the travel and the acceleration performance of tractor.
The utility model is realized by the following technical scheme, a 2-section type friction-sliding starting hydraulic shunting stepless gearbox is provided, which comprises a power input shaft, a pump control hydraulic motor, a confluence planetary bar and a power output shaft, wherein a pump shaft I gear, an L section I gear and an H section I gear are sequentially and fixedly arranged on the power input shaft;
a pump shaft II gear meshed with the pump shaft I gear is fixedly arranged on a pump shaft of the pump control hydraulic motor, a motor shaft L-I gear is connected to a motor shaft of the pump control hydraulic motor through an M-L gear clutch, and a motor shaft H-I gear is connected to the motor shaft of the pump control hydraulic motor through an M-H gear clutch;
The confluence planet row comprises a sun gear, a gear ring and a planet wheel, wherein the sun gear and the gear ring are coaxially arranged, the planet wheel is positioned between the sun gear and the gear ring and is simultaneously meshed with the sun gear and the gear ring, a gear ring shaft fixedly connected with the gear ring is connected with an H-section II gear meshed with the H-section I gear through an H-section clutch, and an L-section II gear meshed with the L-section I gear is connected through an L-section clutch; a motor shaft L-II gear meshed with the motor shaft L-I gear and a motor shaft H-II gear meshed with the motor shaft H-I gear are fixedly arranged on a sun wheel shaft fixedly connected with the sun wheel; an F-gear I gear and an R-gear I gear are fixedly arranged on a planet carrier shaft fixedly connected with a planet carrier provided with a planet wheel, the R-gear I gear is in meshed connection with an R-gear idle wheel, and a ring gear shaft, a sun wheel shaft and the planet carrier shaft are coaxial;
And the power output shaft is connected with an F-gear II gear meshed with the F-gear I gear and an R-gear II gear meshed with the R-gear idle gear through a directional clutch.
When the scheme is used, the power input shaft is connected with the engine of the tractor, the power output shaft is connected with the central transmission gear pair of the rear axle of the tractor, and two gears are introduced into gear transmission between the motor shaft and the sun gear shaft, so that the 2-stage type friction starting hydraulic shunting stepless speed changing box can realize unequal difference configuration of transmission ratio adjusting ranges of two adjacent stepless speed adjusting sections.
preferably, the planet carrier is sleeved on the sun wheel shaft. The optimized scheme is that the planet carrier shaft is sleeved on the sun gear shaft, the structure is simple, and the planet carrier shaft and the sun gear shaft are conveniently ensured to be coaxial.
Preferably, the pump-controlled hydraulic motor is an integrated pump-controlled hydraulic motor. The pump-controlled hydraulic motor of the preferred scheme adopts the integrated pump-controlled hydraulic motor, so that the connection of an external oil pipe between a split pump and the motor is avoided, the installation space is saved, and the overall structure of the gearbox is more compact.
Preferably, the L-stage clutch, the H-stage clutch, the M-L-stage clutch and the M-H-stage clutch are wet clutches. The wet clutch adopted by the optimal selection scheme can meet the required functions, has smooth power transmission, long service life and low failure rate, and is more suitable for tractors.
Preferably, the directional clutch is a double-engageable mesh clutch or a double-directional wet clutch. This preferred scheme is favorable to simplifying the structure and reducing the installation occupation space.
The utility model has the advantages that:
1. Two gears are introduced into gear transmission between a motor shaft and a sun wheel shaft, so that the 2-section type sliding friction starting hydraulic shunting stepless speed changing box can realize non-equal difference configuration of the transmission ratio adjusting ranges of two adjacent stepless speed adjusting sections, and the running and accelerating performance of the tractor is improved;
2. The pump shaft I gear is arranged in front of the L section I gear, so that the axial size of the gearbox is reduced;
3. the gearbox starts based on the direct sliding friction of the L-section clutch, and compared with hydrostatic starting, a gear ring brake is omitted, and the problem of section changing impact when the hydrostatic section is switched to the hydraulic power shunt section during starting is solved;
4. the single-confluence planetary line design has a simple and compact integral structure and is beneficial to cost control.
Drawings
FIG. 1 is a schematic structural view of the present invention;
Shown in the figure:
1. a power input shaft, 2, a pump shaft I gear, 3, an L-section I gear, 4, an H-section I gear, 5, an L-section II gear, 6, an L-section clutch, 7, an H-section clutch, 8, an H-section II gear, 9, a ring gear shaft, 10, a ring gear, 11, a planet gear, 12, a sun gear, 13, a planet carrier, 14, a planet carrier shaft, 15, an F-range I gear, 16, an R-range I gear, 17, a motor shaft L-II gear, 18, a motor shaft H-II gear, 19, a sun gear shaft, 20, a pump shaft II gear, 21, a pump shaft, 22, a pump-controlled hydraulic motor, 23, a motor shaft, 24, a motor shaft L-I gear, 25, an M-L-range clutch, 26, an M-H range clutch, 27, a motor shaft H-I gear, 28, an F-range II gear, 29, a direction clutch, 30, an R range II gear, 31, a power output shaft, 32. the bus planet row, 33 and R gear idle wheels.
Detailed Description
In order to clearly illustrate the technical features of the present solution, the present solution is explained below by way of specific embodiments.
as shown in fig. 1, the 2-stage type slip friction starting hydraulic split continuously variable transmission comprises a power input shaft 1, a pump-controlled hydraulic motor 22, a confluence planetary row 32 and a power output shaft 31, wherein the pump-controlled hydraulic motor 22 is an integrated pump-controlled hydraulic motor. The power input shaft 1 is connected with a tractor engine, the power output shaft 31 is connected with a central transmission gear pair of a tractor rear axle, and a pump shaft I gear 2, an L section I gear 3 and an H section I gear 4 are fixedly arranged on the power input shaft 1 in sequence along the direction far away from the engine.
A pump shaft II gear 20 meshed with the pump shaft I gear 2 is fixedly arranged on a pump shaft 21 of the pump control hydraulic motor 22, a motor shaft L-I gear 24 is connected to a motor shaft 23 of the pump control hydraulic motor 22 through an M-L gear clutch 25, and a motor shaft H-I gear 27 is connected to the pump shaft I gear through an M-H gear clutch 26.
The busbar 32 comprises a sun gear 12 and a ring gear 10 which are coaxially arranged, and planet gears 11 which are positioned between the sun gear 12 and the ring gear 10 and are simultaneously meshed with the sun gear 12 and the ring gear 10, and the intrados of the ring gear is provided with meshing teeth, namely the planet gears 11 are meshed with the ring gear 10.
The gear ring shaft 9 fixedly connected with the gear ring is connected with an H-section II gear 8 meshed with the H-section I gear 4 through an H-section clutch 7, and is connected with an L-section II gear 5 meshed with the L-section I gear 3 through an L-section clutch 6.
A motor shaft L-II gear 17 meshed with a motor shaft L-I gear 24 and a motor shaft H-II gear 18 meshed with a motor shaft H-I gear 27 are fixedly arranged on a sun wheel shaft 19 fixedly connected with the sun wheel 12.
An F-gear I gear 15 and an R-gear I gear 16 are fixedly arranged on a planet carrier shaft 14 fixedly connected with a planet carrier 13 for mounting a planet wheel, the R-gear I gear 16 is connected with an R-gear idle wheel 33 in a meshed mode, a gear ring shaft 9, a sun wheel shaft 19 and a planet carrier shaft 14 are coaxial, the gear ring shaft 9 is located on the left side of a confluence planet row 32, the sun wheel shaft 19 and the planet carrier shaft 14 are located on the right side of the confluence planet row 32, the planet carrier shaft 14 is sleeved on the sun wheel shaft 19, and a through hole with the diameter larger than that of the sun wheel shaft 19 is formed in the planet carrier shaft 14.
The F-range II gear 28 meshing with the F-range I gear 15 and the R-range II gear 30 meshing with the R-range idle gear 33 are connected to the power output shaft 31 via the directional clutch 29.
The L-range clutch 6, the H-range clutch 7, the M-L range clutch 25, and the M-H range clutch 26 in the present embodiment are wet clutches. The directional clutch 29 is a double-engageable mesh clutch or a double-directional wet clutch, and a double-directional wet clutch is used in this embodiment.
The gearbox of this embodiment comprises the following steps when in use:
1. Preparation before starting: the L-stage clutch 6, the H-stage clutch 7 and the M-H stage clutch 26 are disengaged, the M-L stage clutch 25 is engaged, and the directional clutch 29 is engaged on the left side and disengaged on the right side.
2. Starting the tractor: the pump displacement of the pump control hydraulic motor 22 is set to be maximum in the reverse direction, then the engine is started, and the power input shaft 1 is driven to rotate, at the moment, the rotating speed of the motor shaft 23 is maximum, the rotating speed of the power output shaft 31 is zero, and the tractor is in a static state; slowly engaging the L-section clutch 6, gradually increasing the rotating speed of the power output shaft 31 from zero to the lowest stable rotating speed, and finishing the starting of the tractor.
3. l-section stepless speed regulation: the pump displacement of the pump control hydraulic motor 22 is gradually adjusted in the forward direction, the rotating speed of the power output shaft 31 is gradually increased, and the tractor is gradually accelerated; when the pump displacement of the pump-controlled hydraulic motor 22 reaches the positive maximum, the tractor reaches the maximum speed in the L-section.
4. switching the L section to the H section: after the L section is accelerated, the L section clutch 6 and the M-L gear clutch 25 are separated, the H section clutch 7 and the M-H gear clutch 26 are engaged, meanwhile, the pump displacement of the pump control hydraulic motor 22 is rapidly adjusted to the H section theoretical section shifting point displacement in the reverse direction, and the H section transmission ratio of the gearbox under the displacement is equal to the L section transmission ratio before the section shifting. After that, the gearbox is switched to the H section for operation.
5. H-section stepless speed regulation: the pump displacement of the pump control hydraulic motor 22 is gradually adjusted in the forward direction, the rotating speed of the power output shaft 31 is gradually increased, and the tractor continues to accelerate; when the pump displacement of the pump-controlled hydraulic motor 22 reaches a positive maximum, the tractor reaches a maximum speed in section H.
6. The reverse running working condition of the tractor is as follows: the direction clutch 29 is engaged on the right side and disengaged on the left side, and the rest is completely identical to the operation in the forward running.
Of course, the above description is not limited to the above examples, and technical features of the present invention that are not described in the present application may be implemented by or using the prior art, and are not described herein again; the above embodiments and drawings are only used for illustrating the technical solutions of the present invention and are not intended to limit the present invention, and the present invention has been described in detail with reference to the preferred embodiments, and those skilled in the art should understand that changes, modifications, additions or substitutions made by those skilled in the art within the spirit of the present invention should also belong to the protection scope of the claims of the present invention.
Claims (5)
1. The utility model provides a 2 section formula cunning rubs hydraulic pressure reposition of redundant personnel buncher which characterized in that: the hydraulic pump comprises a power input shaft (1), a pump control hydraulic motor (22), a confluence planetary row (32) and a power output shaft (31), wherein a pump shaft I gear (2), an L section I gear (3) and an H section I gear (4) are fixedly arranged on the power input shaft (1) in sequence;
a pump shaft II gear (20) meshed with the pump shaft I gear (2) is fixedly arranged on a pump shaft (21) of the pump control hydraulic motor (22), a motor shaft L-I gear (24) is connected to a motor shaft (23) of the pump control hydraulic motor (22) through an M-L gear clutch (25), and a motor shaft H-I gear (27) is connected to the motor shaft through an M-H gear clutch (26);
The confluence planet row (32) comprises a sun gear (12) and a gear ring (10) which are coaxially arranged, and a planet gear (11) which is positioned between the sun gear (12) and the gear ring (10) and is simultaneously meshed with the sun gear (12) and the gear ring (10), wherein a gear ring shaft (9) fixedly connected with the gear ring is connected with an H-section II gear (8) meshed with an H-section I gear (4) through an H-section clutch (7), and is connected with an L-section II gear (5) meshed with an L-section I gear (3) through an L-section clutch (6); a sun wheel shaft (19) fixedly connected with the sun wheel (12) is fixedly provided with a motor shaft L-II gear (17) meshed with a motor shaft L-I gear (24) and a motor shaft H-II gear (18) meshed with a motor shaft H-I gear (27); an F-gear I gear (15) and an R-gear I gear (16) are fixedly arranged on a planet carrier shaft (14) fixedly connected with a planet carrier (13) provided with a planet wheel, the R-gear I gear (16) is in meshed connection with an R-gear idle wheel (33), and a gear ring shaft (9), a sun wheel shaft (19) and the planet carrier shaft (14) are coaxial;
And the power output shaft (31) is connected with an F-gear II gear (28) meshed with the F-gear I gear (15) and an R-gear II gear (30) meshed with the R-gear idle gear (33) through a directional clutch (29).
2. The 2-stage slipping friction starting hydraulic split-flow continuously variable transmission according to claim 1, characterized in that: the planet carrier shaft (14) is sleeved on the sun wheel shaft (19).
3. The 2-stage slipping friction starting hydraulic split-flow continuously variable transmission according to claim 1, characterized in that: the pump-controlled hydraulic motor (22) is an integrated pump-controlled hydraulic motor.
4. the 2-stage slipping friction starting hydraulic split-flow continuously variable transmission according to claim 1, characterized in that: the L-section clutch (6), the H-section clutch (7), the M-L gear clutch (25) and the M-H gear clutch (26) are wet clutches.
5. The 2-stage slipping friction starting hydraulic split continuously variable transmission according to claim 1 or 4, characterized in that: the directional clutch (29) is a double-direction engageable intermeshing clutch or a double-direction wet clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920609434.XU CN209781609U (en) | 2019-04-30 | 2019-04-30 | 2-stage type friction starting hydraulic shunting stepless gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920609434.XU CN209781609U (en) | 2019-04-30 | 2019-04-30 | 2-stage type friction starting hydraulic shunting stepless gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN209781609U true CN209781609U (en) | 2019-12-13 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920609434.XU Expired - Fee Related CN209781609U (en) | 2019-04-30 | 2019-04-30 | 2-stage type friction starting hydraulic shunting stepless gearbox |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN209781609U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113124127A (en) * | 2021-04-20 | 2021-07-16 | 中国石油大学(华东) | Multi-mode hydraulic mechanical stepless speed change device for grain harvester |
-
2019
- 2019-04-30 CN CN201920609434.XU patent/CN209781609U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113124127A (en) * | 2021-04-20 | 2021-07-16 | 中国石油大学(华东) | Multi-mode hydraulic mechanical stepless speed change device for grain harvester |
| CN113124127B (en) * | 2021-04-20 | 2022-05-24 | 中国石油大学(华东) | Multi-mode hydraulic mechanical stepless speed change device for grain harvester |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20191213 Termination date: 20210430 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |