JPS6010907Y2 - Drive axle transmission support device for traveling work vehicles - Google Patents

Description

[Detailed description of the invention] The present invention relates to a drive axle transmission support device for a traveling work vehicle.
To enable a drive axle to be freely disassembled and assembled without disassembling an axle case, and to facilitate the replacement of an oil seal attached to an end of an axle case.

A brake device is provided on the differential output shaft, a planetary transmission is provided between the differential output shaft and the drive axle on the extension line of this shaft, the drive axle is wrapped in an axle case, and the drive axle is mounted so as to be relatively rotatable. The technology of making the drive axle freely insertable and detachable in the axial direction from the planetary carrier was developed in 1983.
The applicant has proposed this in Publication No.-45725.

However, in this prior art, since the planetary gear is not supported from both sides in the axial direction, there is a risk of it falling over when the axle is pulled out, so the planetary carrier must be supported by a large-capacity bearing.

The present invention solves this problem.

Hereinafter, specific examples of the present invention will be described in detail with reference to the drawings.

In FIG. 1, reference numeral 1 denotes a transmission case that serves as the body of a traveling work vehicle such as a tractor, and a differential device 2 driven by a speed change transmission device (not shown) is built into the case 1.

3 is a brake device, which is provided on each of the differential output shafts 4.

Reference numeral 5 designates a planetary transmission device, which is shown in the form of a gear in the figure, and is provided between the differential output shaft 4 and the drive axle 6 provided on the axis extension line of each output shaft 4. This is the final reduction gear.

7 is a brake case, 8 is an axle case, and 9 is a drive axle, which is usually a rear wheel and is detachable from the axle 6.

Referring to FIGS. 2 and below, reference numeral 10 denotes a bearing case, which is fastened to the side wall of the transmission case 1 with a plurality of bolts 11, and holds the differential device 2 so as to be relatively rotatable.

The differential output shaft 4 extends outward from the side wall 1a of the mission case 1, and has an engaging protrusion 12 in the middle.
A gear 13 serving as a solar transmission body is engraved on the outside.

14 is a brake disc, which is the engagement protrusion 1 of the differential output shaft 4
2 in the circumferential direction, but movable in the axial direction, and in the figure, two sheets are held at intervals.

Of course, the number of discs 14 may be one or two or more.

A plurality of bolts 15 are installed on the side wall 1a of the transmission case 1, and the base portions 8a of the brake case 7 and the axle case 8 are screwed together with a nut 16.

Of course, for this attachment, the bolt 15 does not have to be a stud as shown in the figure, and may be a bolt with a head screwed into the side wall 1a, but preferably a stud.

The brake case 7 is seated on the side wall 1a, but at this time,
A seal is not used between the seats, but an oil-tight structure is achieved by fitting the outer peripheral surface 17a of the flange 17 of the bearing case 10 and providing an O-ring 18 as an oil seal between the outer peripheral surface 17a and the outer peripheral surface 17a.

A plurality of support protrusions 20 for a cam plate 19 are formed on the flange 17 of the bearing case 10 on a radial line centered on the differential output shaft 4, and the cam plate 19 is fitted to these protrusions so as to be relatively rotatable.

Cam surfaces 21 are formed on the mission case 1 side of the cam plate 19 at equal intervals in the circumferential direction, and balls 22 are in contact with the cam surfaces 21, and the balls 22 can be freely transferred to the ball holes 23 of the flange 17. It is stored.

In addition, in order to avoid direct contact between the balls 22 and the side wall 1a of the transmission case 1 and the formation of impressions, the balls 22 are
A plate body 24 made of resin, metal, etc. is interposed between the side wall 1a and the side wall 1a.

An engaging portion 25 projects from a portion of the outer periphery of the cam plate 19, and a cam lever 26 engages with this engaging portion 25.

The cam lever 26 is fitted and fixed to a cam lever shaft 27, and the lever shaft 27 is mounted on a bag-shaped holding portion 28 projecting from the lower part of the brake case 7 so that both ends of the shaft can freely rotate around the axis. 29 is the bearing metal, 30.3
Reference numeral 1 indicates an O-ring, and reference numeral 32 indicates a thrust collar. A cam lever 33 is fitted onto the outside of the case 7 of the cam lever shaft 27, and a brake rod 34 is pivotally attached to the cam lever 33.

An annular pressure receiving surface 35 is formed on the brake case 7 in correspondence with the thrust applying means consisting of the cam surface 21 and the ball 22.
This pressure receiving surface 35 is the inner surface of the annular wall 36.

Reference numeral 37 denotes an annular brake plate, which is interposed between the pressure receiving surface 35, the brake disc 14, and the adjacent brake discs 14, respectively.

The drive axle 6 has a mounting flange 38 at its outer end, to which the disc of the wheel 9 is removably mounted with bolts or the like.

Further, the axle 6 has a spline portion 39 formed at its inner end, and is held relatively rotatably by two ball bearings 40 and 41 located at an axially inner corner with respect to the axle case 8. , 41 inner race is nut 42 and retaining ring 43
′ prevents thrust movement toward each other in the direction.

Note that the inner race of the bearing 41 is firmly fitted to the shaft 6.

The axle case 8 has a rectangular cross section as shown in FIG. 2, and the left side of the line A-A in FIG.
The area to the right of line A is shown in a transverse plane.

Reference numeral 43 denotes a bearing restraining case for the bearing 40, which can be attached and detached using a plurality of fastening bolts 44 to restrain the outer race of the bearing 40 on the outer end surface of the axle case 8. An O-ring 45 is interposed therebetween, and an oil seal 46 is interposed between the bearing restraining case 43 and the axle 6.

The planetary transmission 5 has a cylindrical boss 48 of its planetary carrier 47.
is held by a spline portion 39 of the axle 6, and the axle 6 can be pulled out from the boss 48 in an axially outward direction.

A plurality of planetary transmission support shafts 49 are fixed to the planetary carrier 47 in parallel with the axle 6, and each support shaft 49 has a metal 5
0, a gear 51 as a planetary transmission body is pivotally supported for relative rotation.

Note that an oil hole 49a is formed in the support shaft 49 to lubricate the metal 50.

Reference numeral 52 denotes a planetary ring body, which is an internal gear in the embodiment, and is held between the inner end surface of the axle case 8 and the outer end surface of the brake case 7 while annularly surrounding the axis of the differential output shaft 4. In the embodiment, they are attached together by bolts 15.

Note that each planetary transmission body 51 engages with the planetary ring body 52, and each planetary transmission body 51 engages with the sun transmission body 13.

Further, in the embodiment, a gear type is shown as the planetary reduction transmission device 5, but it may be a roller type.

However, it preferably follows a gear pattern.

Each of the planetary transmission bodies 51 includes an annular wall 36 of the brake case 7 and an annular wall 5 formed inside the inner end of the axle case 8.
3, and is held in a pinched manner.

Note that 54 indicates a pair of O-rings in the planetary transmission body 51.

According to the embodiment of the present invention configured as described above, the power from the differential device 2 is transmitted to the pair of left and right differential output shafts 4, and is transmitted to the rear axle via the planetary gear transmission 5 under the required reduction ratio. 6, and the rear wheels 9 are rolled.

Furthermore, when a brake pedal or the like outside the area is depressed, the cam plate 19 is held by the protrusion 20 and moves in the braking direction via the thrust applying means consisting of the ball 22 etc., pressing the brake disc 14 etc. against the pressure receiving surface 35. Each differential output shaft 4 can be braked independently or simultaneously.

The heat generated by braking of the brake device 3 and the lubrication of the planetary transmission device 5 are generated by the gear oil in the transmission case 1 flowing into the brake case 7 and the axle case 8 or by applying lubricating oil to the brake case 7 and the axle case 8. This lubricating oil is prevented from leaking by storing the lubricating oil by the O-rings 18, 30, 31, and 54, and leaking from the outer end of the axle case 8 is prevented by the O-ring 45 and the oil seal 46.

Therefore, oil seals 46 and 01J due to long-term use.
The replacement of the ring 45 and the reassembly after replacement are performed as follows.

First, after removing the wheel 9 from the wheel 6 and loosening the bolts 44 that fasten the axle case 8 and the bearing holding case 43,
The axle 6 is pulled out to the left in FIG. 2 using a tool or the like.

Since the inner end of the axle 6 is joined to the cylindrical boss portion 48 of the planet carrier 47 by a spline 39, the axle 6 is connected to the bearings 40, 41 and the bearing restraining case 43, as shown in FIG.
At the same time, it becomes possible to completely pull it out from the axle case 8.

After pulling out in this manner, the bearing restraining case 43 is moved in the axial direction, making it easier to replace the oil seal 46 and the O-ring 45.

Furthermore, when the axle 6 is pulled out as shown in FIG. 4, it is necessary to support the planetary transmission 5 and maintain the posture of the cylindrical boss portion 48 during reassembly.

This is because the transmission device 5 is supported by inserting the spline portion 39 of the axle 6 into the cylindrical boss portion 48, and if the axle 6 is pulled out, the support is lost.

However, in the embodiment of the present invention, both end surfaces of the planetary transmission body 51 are sandwiched between the annular wall 53 of the axle case 8 and the annular wall 36 of the brake case 7, and these sandwiching points are indicated by the reference numerals in FIG. Since this is done in each transmission body 51 as shown in a, the position of the cylindrical boss portion 48 of the planetary carrier 47 does not change even if the axle 6 is pulled out.

Further, even if each transmission body 51 is held between the walls 36 and 53, since the clamping portion is a sliding surface, each transmission body 51
There will be no hindrance to the transfer.

After replacing the O-ring 45 and oil seal 46, insert the entire axle 6 shown in FIG. Since the position of the cylindrical boss portion 48 has not changed as described above, this assembly is extremely easy, and all that is required is to retighten the fastening bolt 44 and attach the wheel 9 to the axle 6.

The present invention includes a brake device on the differential output shaft, a planetary transmission between the differential output shaft and the drive axle on the extension line of this shaft, the drive axle is wrapped in an axle case, and is mounted to be relatively rotatable. The drive axle is held in a planet carrier of a planetary transmission so that it can be freely inserted into and removed from the planetary carrier in the axial direction, and both outer peripheral sides of the plurality of planetary transmission bodies attached to the planetary carrier are connected to the axle case and the brake. A drive axle transmission support for a traveling work vehicle, characterized in that the drive axle transmission support is supported between facing walls of a case so as not to be axially movable, and each of the planetary transmission bodies is further supported by a solar transmission body on a differential output shaft. Since it is related to a device, it has the following advantages.

In addition to the basic effect of simply pulling out the axle from the axle case without disassembling the axle case when replacing oil seals, etc., even if the axle is pulled out, the planetary carrier does not allow the planetary power Since it is supported between the case and the facing wall of the brake case, it is possible to maintain the posture.

Therefore, there is no need to adopt a complicated structure in which the bearing is fitted onto the planetary carrier and supported by the axle case.

[Brief explanation of the drawing]

The drawings show an example of the implementation of the present invention, and FIG. 1 shows a general outline of the overall structure.
3 is an explanatory cross-sectional view taken along line 3-3 in FIG. 2, and FIG. 4 is a cross-sectional view when the axle is pulled out. 3...brake device, 4...differential output shaft, 5...planetary transmission, 6...axle, 7...brake case , 8... Axle case, 9...--- Axle, 36. Annular wall of curved brake case, 39. Spline part of curved axle, 47.
... Planetary carrier, 48. Curved, cylindrical boss, 51.
... Planetary transmission body, 53 ... Annular wall of the axle case.

Claims (1)

[Scope of utility model registration request] A brake device is provided on the differential output shaft, a planetary transmission is provided between the differential output shaft and a drive axle on the extension line of this shaft, the drive axle is wrapped in an axle case, and is mounted so as to be relatively rotatable; The drive axle is held so that it can be inserted into and removed from the planetary carrier of the planetary transmission device in the axial direction. 1. A drive axle transmission support device for a traveling work vehicle, characterized in that the planetary transmissions are supported immovably in the axial direction between them, and each of the planetary transmissions is supported by a sun transmission on a differential output shaft.