CN216942523U

CN216942523U - Heavy drive axle and tractor

Info

Publication number: CN216942523U
Application number: CN202220426687.5U
Authority: CN
Inventors: 朱昊; 贾强; 付帅; 吕平; 赵青; 王学龙; 刘庆勇
Original assignee: Weichai Lovol Heavy Industry Co Ltd
Current assignee: Weichai Lovol Intelligent Agricultural Technology Co Ltd
Priority date: 2022-03-01
Filing date: 2022-03-01
Publication date: 2022-07-12
Anticipated expiration: 2032-03-01

Abstract

The utility model relates to a heavy drive axle and a tractor, which relate to the field of agricultural machinery, wherein one ends of two steering oil cylinders are respectively hinged with the middle parts of two steering knuckles, the other ends of the two steering oil cylinders are respectively hinged with a drive axle housing, each wheel-side speed reducer comprises a gear ring, at least four planet wheels and a planet carrier, the gear ring is fixedly connected with the other ends of the steering knuckles, the number of the planet wheels is at least four, the at least four planet wheels are uniformly distributed in the gear ring along the circumferential direction of the gear ring and are meshed with the gear ring, the at least four planet wheels are also rotatably connected with the planet carrier, and the planet carrier is rotatably connected with the other ends of the steering knuckles. The beneficial effects are that: when the steering is performed, the two steering cylinders work simultaneously to drive the two steering knuckles to rotate. The steering power is sufficient, and the steering device is suitable for heavy equipment. The bearing capacity of the hub reduction gear is increased by increasing the number of the planet gears, the size of the hub reduction gear is not required to be increased, and the structure is compact and convenient for mounting tires.

Description

Heavy drive axle and tractor

Technical Field

The utility model relates to the field of agricultural machinery, in particular to a heavy drive axle and a tractor.

Background

The tractor mainly uses the front steering transaxle to realize turning to with preceding driving function, and most tractor front drive axle bearing capacity is lower at present, and the reliability is general, generally is used for 300 horsepower below, and the complete machine weight is below 15 tons. And the front axle mostly adopts a single steering oil cylinder to realize steering, and when the front axle is applied to heavy equipment, the steering power is insufficient.

In prior art, when bearing capacity is not enough, can usually be through the size of increase hub reduction gear ring gear and planet wheel with increase intensity, but strengthen according to above-mentioned scheme back and although intensity satisfies, overall dimension is too big, leads to the front wheel construction bolt circle of distribution too big, and installation tire is difficult, can't install two front wheels even.

SUMMERY OF THE UTILITY MODEL

The utility model aims to solve the technical problem of how to improve the bearing capacity and the steering capacity of a drive axle.

The technical scheme for solving the technical problems is as follows: a heavy drive axle comprises a drive axle shell, two steering knuckles, two wheel reducers and two steering oil cylinders, wherein two ends of the drive axle shell are respectively hinged with one ends of the two steering knuckles, the other ends of the steering knuckles are in one-to-one correspondence with the wheel reducers and are connected with the wheel reducers, one ends of the two steering oil cylinders are respectively hinged with the middle parts of the two steering knuckles, the other ends of the two steering oil cylinders are hinged with the drive axle shell,

every the hub reduction gear includes ring gear, planet wheel and planet carrier, the ring gear with the other end fixed connection of knuckle, the planet wheel is at least four, at least four the planet wheel is followed the circumference evenly distributed of ring gear is in the ring gear and rather than the meshing, at least four the planet wheel still with the planet carrier rotates and is connected, the planet carrier with the other end of knuckle rotates and is connected.

The utility model has the beneficial effects that: when the steering device is used for steering, the two steering oil cylinders work simultaneously to drive the two steering knuckles to rotate synchronously. The steering power is sufficient, and the steering device is suitable for heavy equipment. In addition, the bearing capacity of the hub reduction gear is increased by increasing the number of the planet gears, the size of the hub reduction gear is not required to be increased, and the hub reduction gear is compact in structure and convenient for mounting tires.

On the basis of the technical scheme, the utility model can be further improved as follows.

Further, each hub reduction gear comprises four planet wheels.

Furthermore, the heavy-duty drive axle further comprises a tie rod, and two ends of the tie rod are respectively hinged with the middle parts of the two steering knuckles.

The beneficial effect of adopting the further scheme is that: the tie rod balances the steering force of the steering cylinders on two sides and restrains the turning angles of the two steering knuckles at the same time, so that the two steering knuckles synchronously rotate.

Further, the tie rod can be telescopically adjusted and positioned.

The beneficial effect of adopting the further scheme is that: the length of the transverse pull rod is adjustable, and the installation and adjustment are facilitated.

Furthermore, the heavy-duty drive axle further comprises two universal half shafts, one ends of the two universal half shafts are respectively in transmission connection with the planet wheels of the wheel-side speed reducer, and the other end of each universal half shaft is used for power input.

Furthermore, heavy transaxle still includes differential mechanism, differential mechanism includes differential mechanism casing, differential gear shaft, differential planetary bevel gear and differential half-axis bevel gear, the rotatable installation of differential mechanism casing in the transaxle housing is internal, the differential gear shaft with differential mechanism casing fixed connection, the differential gear shaft is the cross axle and has four axle heads, differential planetary bevel gear is four, four differential planetary bevel gear is rotatable cover respectively four axle heads of differential gear shaft, two differential half-axis bevel gear is located respectively the both sides of differential gear shaft, and every differential half-axis bevel gear simultaneously with four differential planetary bevel gear meshes, two the other end of universal half-axis respectively with two of differential mechanism differential half-axis bevel gear fixed connection.

Furthermore, the heavy-duty drive axle further comprises a power input shaft, one end of the power input shaft is used for power input, the other end of the power input shaft can rotatably extend into the drive axle shell, a power input gear is fixed on the drive axle shell, a differential bevel gear is fixed on the outer side of the differential shell, and the power input gear is meshed with the differential bevel gear.

Furthermore, each universal half shaft comprises a transmission half shaft, a universal joint and a sun wheel shaft, wherein one end of each sun wheel shaft is provided with a meshing section, the meshing section is in transmission connection with the corresponding planet wheel of the hub reduction gear, the other end of each sun wheel shaft is connected with one end of the transmission half shaft through the universal joint, and the other end of the transmission half shaft is used for power input.

The beneficial effect of adopting the further scheme is that: the universal joint is correspondingly positioned in the steering joint, the universal joint enables power to be transmitted to the sun wheel shaft from the transmission half shaft, and the sun wheel shaft can rotate along with the rotation of the steering joint.

The utility model also provides a tractor comprising the heavy drive axle.

Drawings

FIG. 1 is a block diagram of a heavy drive axle of the present invention;

FIG. 2 is an enlarged partial view of the differential of the present invention;

FIG. 3 is an enlarged fragmentary view of the wheel hub reduction assembly of the present invention;

FIG. 4 is a cross-sectional view A-A of the wheel reduction drive of FIG. 3.

In the drawings, the components represented by the respective reference numerals are listed below:

1. a power input shaft; 2. a power input gear; 3. a differential bevel gear; 4. a drive half shaft; 5. a differential housing; 6. differential half-shaft bevel gears; 7. differential planetary bevel gears; 8. a differential gear shaft; 9. a universal joint; 10. a knuckle; 11. a sun gear shaft; 12. a ring gear; 13. a planet wheel; 14. a planet carrier; 15. a steering cylinder; 16. a tie rod; 17. a transaxle housing.

Detailed Description

The principles and features of this invention are described below in conjunction with the following drawings, which are set forth by way of illustration only and are not intended to limit the scope of the utility model.

In the present embodiment, the terms "front" and "rear" refer to "front" and "rear" in the traveling direction of the heavy-duty transaxle in use, and may also refer to "front" and "rear" in the traveling direction of the vehicle on which the heavy-duty transaxle is mounted.

As shown in fig. 1 to 4, the heavy drive axle of this embodiment includes a drive axle housing 17, two steering knuckles 10, two wheel reducers, two ends of the drive axle housing 17 are respectively hinged to one end of the two steering knuckles 10, the other ends of the steering knuckles 10 are connected to the wheel reducers in a one-to-one correspondence manner, and further includes two steering cylinders 15, one end of each of the two steering cylinders 15 is hinged to a middle portion of each of the two steering knuckles 10, the other end of each of the two steering cylinders 15 is hinged to the drive axle housing 17,

every the hub reduction gear includes ring gear 12, planet wheel 13 and planet carrier 14, ring gear 12 with the other end fixed connection of knuckle 10, planet wheel 13 is at least four, at least four planet wheel 13 is followed the circumference evenly distributed of ring gear 12 is in the ring gear 12 and with its meshing, at least four planet wheel 13 still with planet carrier 14 rotates and is connected, planet carrier 14 with the other end of knuckle 10 rotates and is connected.

During steering, the two steering cylinders 15 work simultaneously to drive the two steering knuckles 10 to rotate synchronously. The steering power is sufficient, and the steering device is suitable for heavy equipment. In addition, the bearing capacity of the hub reduction gear is increased by increasing the number of the planet wheels 13, the size of the hub reduction gear does not need to be increased, and the structure is compact and convenient for mounting tires.

Wherein, the heavy drive axle can be a front drive axle or a rear drive axle. In most vehicles, a front drive axle is used for driving and steering, and the heavy drive axle of the present embodiment is set as the front drive axle. It is not excluded that the heavy drive axle of the present embodiment may also be applied to some special vehicles and used as a rear drive axle.

As for the operation mode of the two steering cylinders 15, specifically, as shown in fig. 1, when the two steering cylinders 15 are disposed on the same side (front side or rear side) of the transaxle housing 17, when steering, one steering cylinder 15 is extended and the other steering cylinder 15 is shortened, so that both the two knuckles 10 are turned left or right. When the two steering cylinders 15 are respectively provided on both sides (one on the front side and the other on the rear side) of the transaxle case 17, the two steering cylinders 15 are simultaneously extended or shortened at the time of steering, so that both the two knuckles 10 are turned leftward or rightward.

Specifically, as shown in fig. 4, the planet gear 13 is rotatably connected with the planet carrier 14 through a bearing, and the planet gear 13 can rotate around its axis. As shown in fig. 3, the carrier 14 is rotatably connected to the other end of the knuckle 10 via a bearing.

On the basis of any one of the above schemes, each hub reduction gear comprises four planet wheels 13. The four-planet wheel hub reduction gear is used in the embodiment, and the problem that the conventional three-planet cantilever hub reduction bearing capacity is insufficient is solved

On the basis of any scheme, the heavy-duty drive axle further comprises a tie rod 16, and two ends of the tie rod 16 are respectively hinged with the middle parts of the two steering knuckles 10.

The tie rod 16 balances the steering force of the steering cylinders 15 on two sides, and simultaneously restrains the turning angles of the two steering knuckles 10, so that the two steering knuckles 10 synchronously rotate.

On the basis of any one of the above schemes, the cross pull rod 16 can be telescopically adjusted and positioned.

The tie rod 16 is adjustable in length, facilitating installation and adjustment.

Specifically, the tie rod 16 includes an adjusting screw, a first half rod and a second half rod, two ends of the adjusting screw have thread sections with opposite spiral directions, and two ends of the adjusting screw are respectively in threaded connection with one end of the first half rod and one end of the second half rod, and the other end of the first half rod and the other end of the second half rod are respectively hinged to the two steering knuckles 10. The overall length of the track rod 16 can be adjusted by turning the adjustment screw. The length of the track rod 16 is constant during use of the heavy drive axle.

On the basis of any scheme, the heavy-duty drive axle further comprises two universal half shafts, one ends of the two universal half shafts are in transmission connection with the planet wheels 13 of the two hub reduction gears respectively, and the other end of each universal half shaft is used for power input.

Specifically, one end of each universal half shaft is coaxially arranged with the corresponding gear ring 12, and is simultaneously in meshed transmission with all the planet wheels 13 of the corresponding hub reduction gear.

On the basis of any scheme, the heavy-duty drive axle further comprises a differential mechanism, wherein the differential mechanism comprises a differential mechanism shell 5, differential gear shafts 8, differential planetary bevel gears 7 and differential half-axle bevel gears 6, the differential case 5 is rotatably mounted in the drive axle case 17, the differential gear shaft 8 is fixedly connected with the differential case 5, the differential gear shaft 8 is a cross shaft and has four shaft ends, the differential bevel gear 7 is four, the four differential bevel gear 7 are respectively rotatably sleeved at the four shaft ends of the differential gear shaft 8, the two differential half-shaft bevel gears 6 are respectively positioned at two sides of the differential gear shaft 8, and each differential half-shaft bevel gear 6 is simultaneously meshed with four differential planetary bevel gears 7, and the other ends of the two universal half shafts are respectively fixedly connected with the two differential half-shaft bevel gears 6 of the differential mechanism.

Specifically, the differential case 5 is rotatably mounted in the drive axle case 17 through a bearing, and a rotation shaft of the differential case 5 is perpendicular to a plane where the differential gear shaft 8 is located. The differential planetary bevel gear 7 is rotatably sleeved on the differential gear shaft 8 through a bearing. The two differential half shaft bevel gears 6 are coaxially arranged and are positioned on two sides of the differential gear shaft 8, the axis of the differential half shaft bevel gear 6 is superposed with the rotating shaft of the differential case 5, and the axis of the differential half shaft bevel gear 6 is perpendicular to the plane where the differential gear shaft 8 is positioned.

Specifically, the differential gear shaft 8 is cross-shaped, two adjacent shaft ends are perpendicular to each other, and two differential planetary bevel gears 7 arranged on the two opposite shaft ends are symmetrical about the cross-shaped intersection of the differential gear shaft 8.

On the basis of any scheme, the heavy-duty drive axle further comprises a power input shaft 1, one end of the power input shaft 1 is used for power input, the other end of the power input shaft can rotatably extend into the drive axle housing 17 and is fixedly provided with a power input gear 2, a differential bevel gear 3 is fixedly arranged on the outer side of the differential housing 5, and the power input gear 2 is meshed with the differential bevel gear 3.

The power input shaft 1 is connected with the drive axle shell 17 through a bearing, and the power input gear 2 is fixedly connected with the power input shaft 1 or integrally formed. The power input gear 2 and the differential bevel gear 3 can be gears in any form, preferably both bevel gears, and the axis of the power input gear 2 is perpendicular to the axis of the differential bevel gear 3.

On the basis of any scheme, each universal half shaft comprises a transmission half shaft 4, a universal joint 9 and a sun gear shaft 11, one end of each sun gear shaft 11 is provided with a meshing section, the meshing section is in transmission connection with a planetary gear 13 of the corresponding wheel-side speed reducer, the other end of each sun gear shaft 11 is connected with one end of the transmission half shaft 4 through the universal joint 9, and the other end of each transmission half shaft 4 is used for power input.

The universal joint 9 is correspondingly positioned in the steering knuckle 10, the universal joint 9 enables power to be transmitted from the transmission half shaft 4 to the sun gear shaft 11, and the sun gear shaft 11 can rotate along with the rotation of the steering knuckle 10.

The transmission process of the heavy drive axle is as follows:

power is input by the power input shaft 1 and is transmitted to the differential bevel gear 3 and the differential shell 5 through meshing of the power input gear. The differential case 5 drives a differential planetary bevel gear 7 through an internal differential gear shaft 8, power is distributed to two differential half-shaft bevel gears 6, the differential half-shaft bevel gears 6 are transmitted into a wheel-side speed reducer through a transmission half shaft 4, a universal joint 9 and a sun gear shaft 11, the sun gear shaft 11 is meshed with a plurality of planetary gears 13 in the wheel-side speed reducer for transmission, and the planetary gears 13 are meshed with a gear ring 12 and rotate along the gear ring 12. After the power is decelerated by the planetary deceleration structure, the power is finally output to the driving wheel by the planet carrier 14.

The utility model also provides a tractor comprising the heavy drive axle.

In the description of the present invention, it should be noted that the terms "front", "rear", "left", "right", "inner", "outer", "circumferential", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplification of description, but do not indicate or imply that the referred device or element must have a specific orientation, be configured in a specific orientation, and operate, and thus, should not be construed as limiting the present invention.

In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the utility model. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples and features of different embodiments or examples described in this specification can be combined and combined by one skilled in the art without contradiction.

In the description of the present invention, it should be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "connected," and "connected" are to be construed broadly, e.g., as meaning either a fixed connection, a removable connection, or an integral connection; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.

The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the utility model, and any modifications, equivalents, improvements and the like that fall within the spirit and principle of the present invention are intended to be included therein.

Claims

1. A heavy drive axle comprises a drive axle shell (17), two steering knuckles (10) and two wheel-side reducers, wherein two ends of the drive axle shell (17) are respectively hinged with one ends of the two steering knuckles (10), the other ends of the steering knuckles (10) are in one-to-one correspondence with the wheel-side reducers and are connected with the wheel-side reducers, the heavy drive axle is characterized by further comprising two steering oil cylinders (15), one ends of the two steering oil cylinders (15) are respectively hinged with the middle parts of the two steering knuckles (10), the other ends of the two steering oil cylinders (15) are hinged with the drive axle shell (17),

every the hub reduction gear includes ring gear (12), planet wheel (13) and planet carrier (14), ring gear (12) with the other end fixed connection of knuckle (10), planet wheel (13) are four at least, four at least planet wheel (13) are followed the circumference evenly distributed of ring gear (12) is in ring gear (12) and mesh with it, four at least planet wheel (13) still with planet carrier (14) rotate to be connected, planet carrier (14) with the other end of knuckle (10) rotates to be connected.

2. A heavy drive axle according to claim 1, characterized in that each said wheel reduction comprises four said planet wheels (13).

3. The heavy drive axle according to claim 1, further comprising a tie rod (16), wherein both ends of the tie rod (16) are respectively hinged to the middle portions of the two steering knuckles (10).

4. A heavy drive axle according to claim 3, characterized in that the track rod (16) is telescopically adjustable and positionable.

5. A heavy drive axle according to any one of claims 1-4, characterized in that it further comprises two universal half-shafts, one end of each of which is in driving connection with a respective planet wheel (13) of the two hub reduction gears, and the other end of each of which is used for power input.

6. A heavy drive axle according to claim 5, characterized in that the heavy drive axle further comprises a differential mechanism, the differential mechanism comprises a differential mechanism housing (5), differential gear shafts (8), differential bevel planet gears (7) and differential half-shaft bevel gears (6), the differential mechanism housing (5) is rotatably mounted in the drive axle housing (17), the differential gear shafts (8) are fixedly connected with the differential mechanism housing (5), the differential gear shafts (8) are cross shafts and have four shaft ends, the differential bevel planet gears (7) are four, the four differential bevel planet gears (7) are respectively rotatably sleeved at the four shaft ends of the differential gear shafts (8), two differential half-shaft bevel gears (6) are respectively positioned at two sides of the differential gear shafts (8), and each differential bevel gear half-shaft (6) is simultaneously meshed with the four differential bevel planet gears (7), the other ends of the two universal half shafts are respectively and fixedly connected with the two differential half shaft bevel gears (6) of the differential mechanism.

7. A heavy drive axle according to claim 6, characterized in that the heavy drive axle further comprises a power input shaft (1), one end of the power input shaft (1) is used for power input, the other end of the power input shaft rotatably extends into the drive axle housing (17) and is fixed with a power input gear (2), a differential bevel gear (3) is fixed on the outer side of the differential housing (5), and the power input gear (2) is meshed with the differential bevel gear (3).

8. A heavy drive axle according to claim 5, characterized in that each of the half-axle universal joints comprises a half-axle drive shaft (4), a universal joint (9) and a sun-axle shaft (11), one end of the sun-axle shaft (11) has a meshing section, the meshing section is in driving connection with the planet wheels (13) of the corresponding wheel reduction gear, the other end of the sun-axle shaft (11) is connected with one end of the half-axle drive shaft (4) through the universal joint (9), and the other end of the half-axle drive shaft (4) is used for power input.

9. A tractor comprising a heavy drive axle according to any one of claims 1 to 8.