CN211852715U - Integral double HST planetary differential steering gearbox - Google Patents
Integral double HST planetary differential steering gearbox Download PDFInfo
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- CN211852715U CN211852715U CN202020456770.8U CN202020456770U CN211852715U CN 211852715 U CN211852715 U CN 211852715U CN 202020456770 U CN202020456770 U CN 202020456770U CN 211852715 U CN211852715 U CN 211852715U
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Abstract
The utility model discloses an integral two HST planet differential steering gearboxes, including power take off mechanism, walking drive mechanism, steering drive mechanism, walking drive mechanism including walking HST, selector shaft, walking brake axle, sun axle, install hydraulic pressure walking gear on the walking HST, be equipped with on the selector shaft with hydraulic pressure walking gear meshing's hydraulic pressure gear, mechanical grade driven gear, fast and slow grade driving gear, install first and second gear shift sliding sleeve on the selector shaft, be fixed with walking input gear on the walking brake axle and with fast and slow grade driven gear of fast and slow grade driving gear meshing, the centre of sun axle is equipped with walking driven gear, the both sides correspondence of sun axle is equipped with planet differential mechanism, walking input gear drives the rotation of walking driven gear. After adopting above-mentioned structure, have simple structure compactness, small, light in weight, stable performance is reliable, transmission efficiency is high, excellent in use effect's advantage.
Description
Technical Field
The utility model relates to the technical field of agricultural machinery, especially an integral two HST planet differential steering gearboxes that use on agricultural machinery.
Background
China is a large population country and is also a large agricultural country, with the rapid development of national economy, the input of the country to agricultural and agricultural machinery subsidies is continuously increased, the original working pattern is fundamentally changed, modern agricultural machinery products are accepted by vast farmers, the labor intensity of the farmers is greatly reduced, and the production efficiency is greatly improved. However, the technical level of the current agricultural machinery is not mature enough, and a plurality of problems are exposed in sequence in the use process, for example, a crawler tractor is mainly embodied on a planetary differential steering gearbox, and a walking system of the adopted gearbox has two schemes, one scheme is that mechanical gear speed change is adopted, the crawler tractor has the advantages of small loss and high transmission efficiency, and the crawler tractor has the problems of few gears, large step difference and poor linearity and also needs to be provided with a reverse gear structure; the other is to adopt hydraulic gear speed change, its advantage is that can realize the stepless speed change, the speed change is gentle, the stability is good, its problem that exists is that the loss is big, the transmission efficiency is low; because an integral gearbox which has mechanical gear speed change and hydraulic gear speed change and can realize a planetary differential steering function does not exist at present, the gearbox can only meet one scheme, and the differential steering function cannot be realized on a planetary differential mechanism; if the differential steering function is realized, the box body is divided into a left part and a right part, and meanwhile, a part with the differential steering function needs to be added, so that the structure is complex, the requirement on the machining precision of the part is high, and the whole weight of the mechanism is heavy. In order to solve the above problems, many manufacturers and technicians develop and research the solution, but no reasonable solution is available to solve the above problems.
Disclosure of Invention
For overcoming the above-mentioned problem that prior art exists, the utility model aims at providing a simple structure is compact, small, light in weight, dependable and stable performance, high, the excellent in use effect's of transmission efficiency integral two HST planet differential turns to gearbox.
The utility model provides a technical scheme that above-mentioned technical problem adopted, it is including installing power take off mechanism, walking drive mechanism, the steering gear on the box, walking drive mechanism including fix on the box and the walking HST who is connected with power take off mechanism, set up selector shaft, walking brake axle, the sun axle on the box, install hydraulic pressure walking gear on walking HST's the output shaft, be equipped with on the selector shaft with hydraulic pressure walking gear meshing and rotatable hydraulic pressure gear, the mechanical gear driven gear that drives by power take off mechanism, rotatable fast-gear driving gear and slow-gear driving gear, install first gear shift sliding sleeve on the selector shaft between hydraulic pressure gear and mechanical gear driven gear, install second gear shift sliding sleeve on the selector shaft between fast-gear driving gear and slow-gear driving gear, be fixed with walking input gear on the walking brake shaft, And the traveling driven gear is arranged in the middle of the sun shaft, the planetary differential mechanisms are correspondingly arranged on two sides of the sun shaft, and the traveling input gear drives the traveling driven gear to rotate.
The utility model further adopts the technical proposal that the steering transmission mechanism comprises a steering HST fixed on the box body and connected with the power output mechanism, a steering primary gear capable of rotating relative to the shift shaft, a steering secondary gear capable of rotating relative to the walking brake shaft and a steering brake shaft arranged on the box body, wherein the steering primary gear is provided with a steering primary driven gear, the steering secondary gear is provided with a steering secondary driven gear, the steering brake shaft is provided with a steering tertiary gear, a steering input gear and a rotatable first inert wheel, the output shaft of the steering HST is provided with a hydraulic steering gear, the steering primary gear is meshed with the hydraulic steering gear, the steering secondary gear is meshed with the steering primary driven gear, the steering tertiary gear is meshed with the steering secondary driven gear, the first inert wheel is meshed with the walking input gear, the walking driven gear is meshed with the first inert wheel, the steering input gear is matched with the planetary differential mechanism.
In a further proposal of the utility model, the power output mechanism comprises a power input shaft, a power output driven shaft, a transmission shaft and a power output shaft which are arranged on the box body, the power input shaft is provided with a first driving gear, a second driving gear and a driving bevel gear, the power output driven shaft is provided with a first driven gear and a second driven gear which can rotate, and a power output meshing sleeve is arranged on a power output driven shaft between the first driven gear and the second driven gear, the first driven gear and the second driven gear are meshed with the corresponding first driving gear and the second driving gear, a driven bevel gear meshed with the driving bevel gear and a mechanical gear driving gear meshed with the mechanical gear driven gear are fixed on the transmission shaft, one end of the transmission shaft is connected with an input shaft of the steering HST, the other end of the transmission shaft is connected with an input shaft of the walking HST, and the power output shaft is connected with the power output driven shaft through a connecting shaft.
The utility model discloses a further scheme, planet differential mechanism include planet carrier, planet wheel, tooth cover, be equipped with ring gear and outer ring gear on the tooth cover, the tooth cover rotationally sets up on the sun axle, the planet wheel rotationally sets up on the planet carrier through planet wheel axle, the inboard and the sun axle meshing of planet wheel, the outside of planet wheel meshes with the ring gear of tooth cover.
The utility model discloses a further scheme, the box on be equipped with rotatable idler shaft, the last two second idlers that are equipped with of idler shaft turns to input gear and wherein one side planet differential mechanism's the outer ring gear meshing of tooth cover and simultaneously with one of them second idler meshing, the outer ring gear meshing of tooth cover of another second idler and corresponding opposite side planet differential mechanism.
The utility model discloses a further scheme, the both sides correspondence of box is equipped with the travel drive mechanism, travel drive mechanism including connecting drive driving gear, drive driven gear, semi-axis, the drive wheel on corresponding planet carrier, the semi-axis rotationally sets up on the box, drive driven gear install on the semi-axis and with the meshing of drive driving gear, the output at the semi-axis is installed to the drive wheel.
The utility model discloses a further scheme, the box on be fixed with the walking stopper of being connected with the walking brake axle, be fixed with the steering brake who is connected with the steering brake axle on the box.
After adopting above-mentioned structure, compare with prior art and have following advantage: firstly, the power output mechanism can provide high-low two-gear power output for a trailer through gear transmission and gear shifting, and simultaneously provides three paths of power output for a walking HST, a mechanical gear driving gear and a steering HST, wherein the HST is a hydraulic stepless speed changer for short, and stepless speed change is realized through the HST; the traveling HST can provide 4-gear power of high-speed forward, low-speed forward, high-speed backward and low-speed backward for the traveling driving mechanism through the traveling transmission mechanism; the mechanical gear driving gear can provide 2 gears of power for the walking driving mechanism to work forward and climb the speed through the walking transmission mechanism; the steering HST provides steering power for the walking driving mechanism through the steering transmission mechanism; hydraulic transmission and mechanical transmission can be selected according to different working condition requirements to realize forward or backward movement, so that the working stability and the transmission efficiency are improved; by adopting the three paths of power output, a reverse gear transmission mechanism can be omitted, the transmission mechanism of the gearbox is simplified, and the assembly property, the adaptability and the reliability of the gearbox are improved. Secondly, a planetary differential mechanism is adopted to obtain a larger reduction transmission ratio and a steering function, so that the reduction stage number of the gearbox is reduced, and the weight of the gearbox is reduced; the planetary differential mechanism is decelerated and moved from the last stage to the penultimate stage, so that the stress borne by the planetary differential mechanism is reduced, and the structural weight of the planetary mechanism can be reduced; the rotating speeds of the sun shaft and the gear sleeve of the planetary differential mechanism can be effectively controlled through the traveling driving mechanism and the steering transmission mechanism, and the two half shafts can obtain the rotating speeds with controllable directions, so that the gearbox can realize a linear traveling function, a variable-diameter steering function and an in-situ steering function. And thirdly, rotating shafts of the gear reduction mechanisms of the walking driving mechanism and the steering transmission mechanism are combined, so that the using number of the rotating shafts and bearings is reduced, the structure of the gearbox is simplified, the weight of the gearbox is reduced, and the production cost is reduced.
Drawings
Fig. 1 is a schematic view of the structure of the present invention.
Fig. 2 is a schematic perspective view of the present invention.
Fig. 3 is a schematic diagram of the principle of the matching structure of the present invention.
Fig. 4 is a schematic cross-sectional view taken along line a-a of fig. 1 according to the present invention.
Fig. 5 is a schematic cross-sectional view of B-B of fig. 2 according to the present invention.
Fig. 6 is a schematic cross-sectional view of C-C of fig. 2 according to the present invention.
Wherein 1 a first driving gear, 2 a power input shaft, 3 a second driving gear, 4 a driving bevel gear, 5 a driven bevel gear, 6 a steering HST, 7 a hydraulic steering gear, 8 a slow gear driving gear, 9 a steering primary gear, 10 a steering primary driven gear, 11 a steering secondary gear, 12 a secondary driven gear, 13 a slow gear driven gear, 14 a steering tertiary gear, 15 a steering brake, 16 a steering brake shaft, 17 a planetary differential mechanism, 18 a driving gear, 19 a sun shaft, 20 a walking driven gear, 21 a half shaft, 22 a driving wheel, 23 a driving driven gear, 24 a second idle gear, 25 an idle gear shaft, 26 a first driven gear, 27 a power output meshing sleeve, 28 a second driven gear, 29 a power output driven shaft, 30 a transmission shaft, 31 a mechanical gear driving gear, 32 a walking HST, 33 a hydraulic walking gear, 34 a hydraulic gear, 35 a gear shaft, 36 a first shift sleeve, 37 mechanical gear driven gears, 38 second shift sliding sleeves, 39 traveling brakes, 40 fast gear driving gears, 41 traveling brake shafts, 42 fast gear driven gears, 43 traveling input gears, 44 steering input gears, 45 first idle gears, 46 connecting shafts, 47 traveling driving mechanisms, 48 power output shafts, 49 planet carriers, 50 planet gears and 51 gear sleeves.
Detailed Description
Fig. 1 to 6 show that the present invention relates to a specific embodiment of an integrated dual HST planetary differential steering transmission, which comprises a power output mechanism, a traveling transmission mechanism and a steering transmission mechanism mounted on a casing, wherein the traveling transmission mechanism comprises a traveling HST32 fixed on the casing and connected with the power output mechanism, a shift shaft 35, a traveling brake shaft 41 and a sun shaft 19 arranged on the casing, a hydraulic traveling gear 33 is mounted on an output shaft of the traveling HST32, a hydraulic gear 34 rotatable and meshed with the hydraulic traveling gear 33, a mechanical gear driven gear 37 driven by the power output mechanism, a rotatable fast gear driving gear 40 and a slow gear driving gear 8 are arranged on the shift shaft 35 arranged between the hydraulic gear 34 and the mechanical gear driven gear 37, a first shift sliding sleeve 36 is mounted on the shift shaft 35 arranged between the fast gear driving gear 40 and the slow gear driving gear 8, a second shift sliding sleeve 38 is mounted on the shift shaft 35 arranged between the fast gear driving gear 40 and the slow gear driving gear 8, a travel input gear 43, and a fast driven gear 42 and a slow driven gear 13 engaged with the fast drive gear 40 and the slow drive gear 8 are fixed to the travel brake shaft 41, a travel driven gear 20 is provided in the middle of the sun shaft 19, planetary differential mechanisms 17 are provided on both sides of the sun shaft 19, and the travel input gear 43 rotates the travel driven gear 20.
In order to realize the steering transmission conveniently, the steering transmission mechanism comprises a steering HST6 fixed on the box body and connected with the power output mechanism, a steering primary gear 9 capable of rotating relative to the shift shaft 35, a steering secondary gear 11 capable of rotating relative to the walking brake shaft 41, and a steering brake shaft 16 arranged on the box body, wherein the steering primary gear 9 is provided with a steering primary driven gear 10, the steering secondary gear 11 is provided with a steering secondary driven gear 12, the steering brake shaft 16 is provided with a steering tertiary gear 14, a steering input gear 44 and a rotatable first idler 45, a hydraulic steering gear 7 is arranged on the output shaft of the steering HST6, the steering primary gear 9 is meshed with the hydraulic steering gear 7, the steering secondary gear 11 is meshed with the steering primary driven gear 10, the steering tertiary gear 14 is meshed with the steering secondary driven gear 12, and the first idler 45 is meshed with the walking input gear 43, the traveling driven gear 20 is engaged with a first idler gear 45, and the steering input gear 44 is engaged with a planetary differential mechanism.
In order to ensure power output, the power output mechanism comprises a power input shaft 2, a power output driven shaft 29, a transmission shaft 30 and a power output shaft 48 which are arranged on a box body, wherein a first driving gear 1, a second driving gear 3 and a driving bevel gear 4 are arranged on the power input shaft 2, a rotatable first driven gear 26 and a rotatable second driven gear 28 are arranged on the power output driven shaft 29, a power output meshing sleeve 27 is arranged on the power output driven shaft 29 between the first driven gear 26 and the second driven gear 28, the first driven gear 26 and the second driven gear 28 are meshed with the corresponding first driving gear 1 and the second driving gear 3, a driven bevel gear 5 meshed with the driving bevel gear 4 and a mechanical gear driving gear 31 meshed with the mechanical gear driven gear 37 are fixed on the transmission shaft 30, one end of the transmission shaft 30 is connected with an input shaft of a steering HST6, the other end is connected with an input shaft of the walking HST32, and the power output shaft 48 is connected with the power output driven shaft 29 through a connecting shaft 46.
In order to realize differential steering, the planetary differential mechanism 17 comprises a planet carrier 49, planet wheels 50 and a gear sleeve 51, wherein the gear sleeve 51 is provided with an inner gear ring and an outer gear ring, the gear sleeve 51 is rotatably arranged on the sun shaft 19, the planet wheels 50 are rotatably arranged on the planet carrier 49 through planet wheel shafts, the inner sides of the planet wheels 50 are meshed with the sun shaft 19, and the outer sides of the planet wheels 50 are meshed with the inner gear ring of the gear sleeve 51. The box body is provided with a rotatable idler shaft 25, the idler shaft 25 is provided with two second idler gears 24, the steering input gear 44 is meshed with an outer gear ring of a gear sleeve 51 of the planetary differential mechanism on one side and simultaneously meshed with one second idler gear 24, and the other second idler gear 24 is meshed with an outer gear ring of a gear sleeve 51 of the corresponding planetary differential mechanism on the other side.
In order to realize the traveling driving, two sides of the box body are correspondingly provided with traveling driving mechanisms 47, each traveling driving mechanism 47 comprises a driving gear 18, a driving driven gear 23, a half shaft 21 and a driving wheel 22, the driving gear 18, the driving driven gear 23, the half shaft 21 and the driving wheel 22 are connected to a corresponding planet carrier 49, the half shaft 21 is rotatably arranged on the box body, the driving driven gear 23 is installed on the half shaft 21 and meshed with the driving gear 18, and the driving wheel 22 is installed at the output end of.
To achieve braking, a traveling brake 39 connected to a traveling brake shaft 41 is fixed to the case, and a steering brake 15 connected to a steering brake shaft 16 is fixed to the case.
The working principle of the utility model is as follows: the power machine transmits power to a first driving gear 1, a second driving gear 3 and a driving bevel gear 4 through a power input shaft 2.
The first driving gear 1 drives the first driven gear 26 or the second driving gear 3 drives the second driven gear 28, then the power is transmitted to the power output driven shaft 29 through the power output meshing sleeve 27, and the power output driven shaft 29 enables the power output shaft 48 to obtain 2-gear power through the connecting shaft 47.
The driving bevel gear 4 drives the driven bevel gear 5 to change the power transmission direction, the driven bevel gear 5 drives the transmission shaft 30, and the transmission shaft 30 outputs three paths of power: one path is transmitted to a walking HST32 to drive a hydraulic walking gear 33; one path is transmitted to the mechanical gear driving gear 31; one path is transmitted to a steering HST6, which drives a hydraulic steering gear 7.
The hydraulic traveling gear 33 drives the hydraulic gear 34 or the mechanical driving gear 31 drives the mechanical driven gear 37, and then the power is transmitted to the shift shaft 35 through the first shift sliding sleeve 36, and the shift shaft 35 transmits the power to the fast driving gear 40 or the slow driving gear 8 through the second shift sliding sleeve 38. The power is transmitted to the fast-gear driving gear 40 through the hydraulic walking gear 33, and two-gear output power of high-speed forward and high-speed backward is obtained; the power is transmitted to the slow-gear driving gear 8 through the hydraulic walking gear 33, and two-gear output power of low-speed forward and low-speed backward is obtained; the power is transmitted to the fast gear driving gear 40 through the mechanical gear driving gear 31 to obtain the working forward gear output power; the power is transmitted to the slow gear driving gear 8 through the mechanical gear driving gear 31, and the output power of the forward gear is obtained.
The fast gear driving gear 40 drives the fast gear driven gear 42 or the slow gear driving gear 8 drives the slow gear driven gear 13, and then drives the traveling brake shaft 41, and the traveling brake shaft 41 drives the traveling input gear 43. The walking input gear 43 drives the walking input gear 18 through the first idler gear 45, the walking input gear 18 drives the sun shaft 19, and the sun shaft 19 obtains a rotating speed nTaiwan (Chinese character of 'tai')The sun shaft 19 is provided with two sun shaft gears.
The steering primary gear 9 and the steering primary driven gear 10 are connected gears, and the steering secondary gear 11 and the steering secondary driven gear 12 are connected gears. The hydraulic steering gear 7 drives a steering primary gear 9, and then the steering primary driven gear 10 drives the steeringThe steering secondary driven gear 12 drives the steering tertiary gear 14 to the secondary gear 11, and drives the steering brake shaft 16 to which the steering tertiary gear 14 belongs, and the steering brake shaft 16 drives the steering input gear 44. One path of the steering input gear 44 drives an outer gear ring of a gear sleeve 51 of a planetary differential mechanism 17, so that the gear sleeve 51 of the planetary differential mechanism 17 obtains a rotating speed nGear ring 1. Meanwhile, the other path of the steering input gear 44 drives the second idle gear 24, and then the second idle gear 24 drives the outer gear ring of the gear sleeve 51 of the other planetary differential mechanism 17, so that the gear sleeve 51 of the other planetary differential mechanism 17 obtains the same rotation speed nGear ring 1Rotating speed n with same size and opposite directionGear ring 2。
When two gear sleeves 51 rotate at a speed nGear ring 1And nGear ring 2When the number is 0, the two planetary carriers 49 are driven by the sun gear on the sun shaft 19, and the two planetary carriers 49 further drive the left and right driving gears 18, so that the left and right driving gears 18 obtain the same rotation speed and the same direction. Then the left and right driving gears 18 respectively drive the left and right driving driven gears 23, and the left and right driving driven gears 23 respectively drive the driving wheel 22 through the half shaft 21, so that the left and right driving wheels 22 obtain the same rotating speed and the same direction, and the machine can run linearly.
When two gear sleeves 51 rotate at a speed nGear ring 1、nGear ring 2And sun shaft 19 speed nTaiwan (Chinese character of 'tai')When the rotation speed difference is not 0, the two planet carriers 49 are driven by the combined action of the sun shaft gear and the inner gear ring of the gear sleeve 51, and the two planet carriers 49 respectively drive the left driving gear 18 and the right driving gear 18, so that the left driving gear 18 and the right driving gear 18 obtain a variable rotation speed difference. Then the left and right driving gears 18 respectively drive the left and right driving driven gears 23, and the left and right driving driven gears 23 respectively drive the driving wheel 22 through the half shaft 21, so that the left and right driving wheels 22 obtain a variable speed difference, and the machine can perform a turning action with a variable turning radius.
When the sun shaft 19 rotates at a speed nTaiwan (Chinese character of 'tai')When the value is 0, the two planet carriers 49 are driven by the inner gear ring of the gear sleeve 51, and the two planet carriers 49 respectively drive the left driving part and the right driving partThe gear 18 makes the left and right driving gears 18 have the same rotation speed and opposite rotation speed. Then the left and right driving gears 18 respectively drive the left and right driving driven gears 23, and the left and right driving driven gears 23 respectively drive the driving wheel 22 through the half shaft 21, so that the left and right driving wheels 22 also obtain the same rotating speed and opposite rotating speed, and the machine tool can perform the pivot steering action.
Because the planetary differential mechanism 17 has two power input ends, two braking points are required to be disconnected in a power breaking mode to ensure safety, wherein the walking brake 39 at one end of the walking brake shaft 41 can be used as a common brake, the steering brake 15 at one end of the steering brake shaft 16 can be used as a differential lock, and after the differential lock is locked, the implement cannot be steered, so that the linearity of the implement during working and traveling can be ensured.
The above description is only the specific embodiment of the present invention, and is not intended to limit the present invention in any form, and the present invention does not depart from the technical solution of the present invention, and the made simple modification, equivalent change or modification all fall into the protection scope of the present invention.
Claims (7)
1. The utility model provides an integral two HST planet differential steering gear box, is including installing power take off mechanism, walking drive mechanism, the steering drive mechanism on the box, characterized by: the traveling transmission mechanism comprises a traveling HST (32) which is fixed on the box body and connected with the power output mechanism, a gear shifting shaft (35) arranged on the box body, a traveling brake shaft (41) and a sun shaft (19), a hydraulic traveling gear (33) is installed on an output shaft of the traveling HST (32), a hydraulic gear (34) which is meshed with the hydraulic traveling gear (33) and can rotate is arranged on the gear shifting shaft (35), a mechanical gear driven gear (37) driven by the power output mechanism, a rotatable fast gear driving gear (40) and a slow gear driving gear (8), a first gear shifting sliding sleeve (36) is installed on the gear shifting shaft (35) between the hydraulic gear (34) and the mechanical gear driven gear (37), a second gear shifting sliding sleeve (38) is installed on the gear shifting shaft (35) between the fast gear driving gear (40) and the slow gear driving gear (8), a traveling input gear (43) and a traveling brake shaft (41) are fixed, And a fast driven gear (42) and a slow driven gear (13) meshed with the fast driving gear (40) and the slow driving gear (8), a walking driven gear (20) is arranged in the middle of the sun shaft (19), planetary differential mechanisms (17) are correspondingly arranged on two sides of the sun shaft (19), and a walking input gear (43) drives the walking driven gear (20) to rotate.
2. The integrated dual HST planetary differential steering gearbox of claim 1, wherein: the steering transmission mechanism comprises a steering HST (6) which is fixed on the box body and connected with the power output mechanism, a steering primary gear (9) which can rotate relative to a shift shaft (35), a steering secondary gear (11) which can rotate relative to a walking brake shaft (41), and a steering brake shaft (16) which is arranged on the box body, wherein a steering primary driven gear (10) is arranged on the steering primary gear (9), a steering secondary driven gear (12) is arranged on the steering secondary gear (11), a steering tertiary gear (14), a steering input gear (44) and a rotatable first idler wheel (45) are arranged on the steering brake shaft (16), a hydraulic steering gear (7) is arranged on an output shaft of the steering HST (6), the steering primary gear (9) is meshed with the hydraulic steering gear (7), and the steering secondary gear (11) is meshed with the steering primary driven gear (10), the steering third-stage gear (14) is meshed with the steering second-stage driven gear (12), the first idler gear (45) is meshed with the walking input gear (43), the walking driven gear (20) is meshed with the first idler gear (45), and the steering input gear (44) is matched with the planetary differential mechanism.
3. An integral dual HST planetary differential steering gearbox according to claim 1 or 2, characterised in that: the power output mechanism comprises a power input shaft (2), a power output driven shaft (29), a transmission shaft (30) and a power output shaft (48) which are arranged on a box body, wherein a first driving gear (1), a second driving gear (3) and a driving bevel gear (4) are arranged on the power input shaft (2), a rotatable first driven gear (26) and a rotatable second driven gear (28) are arranged on the power output driven shaft (29), a power output meshing sleeve (27) is arranged on the power output driven shaft (29) between the first driven gear (26) and the second driven gear (28), the first driven gear (26) and the second driven gear (28) are meshed with the corresponding first driving gear (1) and the second driving gear (3), a driven bevel gear (5) meshed with the driving bevel gear (4) and a mechanical gear driving gear (31) meshed with a mechanical gear driven gear (37) are fixed on the transmission shaft (30), one end of the transmission shaft (30) is connected with an input shaft of the steering HST (6), the other end of the transmission shaft is connected with an input shaft of the walking HST (32), and the power output shaft (48) is connected with the power output driven shaft (29) through a connecting shaft (46).
4. The integrated dual HST planetary differential steering gearbox of claim 3, wherein: the planetary differential mechanism (17) comprises a planet carrier (49), a planet wheel (50) and a gear sleeve (51), wherein the gear sleeve (51) is provided with an inner gear ring and an outer gear ring, the gear sleeve (51) is rotatably arranged on a sun shaft (19), the planet wheel (50) is rotatably arranged on the planet carrier (49) through a planet wheel shaft, the inner side of the planet wheel (50) is meshed with the sun shaft (19), and the outer side of the planet wheel (50) is meshed with the inner gear ring of the gear sleeve (51).
5. The integrated dual HST planetary differential steering gearbox of claim 4, wherein: the box body is provided with a rotatable idler shaft (25), the idler shaft (25) is provided with two second idler gears (24), the steering input gear (44) is meshed with an outer gear ring of a gear sleeve (51) of the planetary differential mechanism on one side and simultaneously meshed with one of the second idler gears (24), and the other second idler gear (24) is meshed with an outer gear ring of the gear sleeve (51) of the planetary differential mechanism on the other side correspondingly.
6. The integrated dual HST planetary differential steering gearbox of claim 5, wherein: the two sides of the box body are correspondingly provided with walking driving mechanisms (47), each walking driving mechanism (47) comprises a driving gear (18), a driving driven gear (23), a half shaft (21) and a driving wheel (22) which are connected onto a corresponding planet carrier (49), the half shaft (21) is rotatably arranged on the box body, the driving driven gear (23) is arranged on the half shaft (21) and meshed with the driving gear (18), and the driving wheel (22) is arranged at the output end of the half shaft (21).
7. The integrated dual HST planetary differential steering gearbox of claim 6, wherein: a walking brake (39) connected with a walking brake shaft (41) is fixed on the box body, and a steering brake (15) connected with a steering brake shaft (16) is fixed on the box body.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020456770.8U CN211852715U (en) | 2020-04-01 | 2020-04-01 | Integral double HST planetary differential steering gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020456770.8U CN211852715U (en) | 2020-04-01 | 2020-04-01 | Integral double HST planetary differential steering gearbox |
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| Publication Number | Publication Date |
|---|---|
| CN211852715U true CN211852715U (en) | 2020-11-03 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202020456770.8U Withdrawn - After Issue CN211852715U (en) | 2020-04-01 | 2020-04-01 | Integral double HST planetary differential steering gearbox |
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| CN (1) | CN211852715U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111271427A (en) * | 2020-04-01 | 2020-06-12 | 浙江四方集团公司 | Integral double HST planetary differential steering gearbox |
-
2020
- 2020-04-01 CN CN202020456770.8U patent/CN211852715U/en not_active Withdrawn - After Issue
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111271427A (en) * | 2020-04-01 | 2020-06-12 | 浙江四方集团公司 | Integral double HST planetary differential steering gearbox |
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