JP2001193767A - Multi-disc brake device for axle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a multi-disc brake device for making the temperature rise of an intermediate brake ring, due to heat energy during braking, similar to that of brake rings at both ends. SOLUTION: A plurality of brake rings 31A, 31B, 31C are provided on the side of a fixed portion 10 and a plurality of brake discs 34 located one by one among the brake rings 31A, 31B, 31C are provided on the side of a rotating shaft 2. The intermediate brake ring 31B is formed thicker than the brake rings 31A, 31C at both ends. When a group of brake rings 31A, 31B, 31C are pressed against a group of brake discs 34 for required braking operation, the temperature rise of the intermediate brake ring 31B increasing in thickness and volume is made similar to that of the brake rings 31A, 31C at both ends, therefore causing uniform wear of facing portions 34a of the brake discs 34.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a multi-plate brake device for an axle employed in various vehicles such as a construction vehicle having a bucket device (working device) mounted on a front portion thereof.

[0002]

2. Description of the Related Art For example, in a large construction vehicle, a propeller shaft from a transmission (drive unit side) is linked to an input side (drive pinion gear) of a front axle or a rear axle. As such a conventional axle, a configuration shown in FIGS. 3 and 4 is provided.

[0003] That is, a differential 11 is provided in a differential body 10, and the differential 1 is
Reference numeral 1 denotes a differential case 12 and a passive ring gear 13 connected to the differential case 12.
And a pair of pinion gears 15 disposed in the differential case 12 and freely rotatably supported via a spider 14, and a pair of side gears 16 always meshing with the pinion gears 15. A pair of transmission shafts 2 that are rotatable on the same rotation axis 1 are linked to both side gears 16.

[0004] The differential body 10 is formed with an opening 17 on one surface in a direction perpendicular to the rotation axis 1, and the opening 17 can be closed by a pinion cage 18. Differential body 10
It is detachably connected to. The pinion cage 18 rotatably supports a pinion gear shaft 20 of a drive pinion gear 19 constantly meshed with the ring gear 13. A flange 21 is fixed to an outer end portion of the pinion gear shaft 20, and a propeller shaft can be connected to the flange 21.

[0005] On both left and right sides of the differential body 10, a recess 22 is formed around the rotation axis 1.
2 between the differential body (fixed portion) 10 side and the transmission shaft (rotary shaft) 2,
Is provided. That is, three (plural) brake rings 41A, 41B, 41C are provided in the recess 22.
Is provided in contact with the inner peripheral surface of the recess 22 so as to be slidable in the direction of the rotation axis 1.

The transmission shaft 2 has a hub disk 4
The hub disc 43 is fixed to the hub disc 43. Two (plural) brake discs 44 positioned one by one between the brake rings 41A, 41B, 41C are slidable in the direction of the rotation axis 1. It is provided in. Further recesses 22
Inside, a cylinder chamber 45 is formed in a concave shape. Inside the cylinder chamber 45, a piston 46 that can abut against the innermost brake rings 41A, 41B, 41C,
A spring 47 for urging the piston 46 in the backward direction is provided. Here, each brake ring 41A, 41
B and 41C have the same thickness t.

A reduction gear device 25 is disposed outside each of the multiple disc brake devices 40.
The transmission shaft 2 is connected to an axle shaft 26 via a link 5. According to the conventional axle as described above, the rotation of the propeller shaft is transmitted to the flange 21, the pinion gear shaft 20, the drive pinion gear 19, the ring gear 13, the differential case 12, and the transmission shaft 2, and thus via the reduction gear device 25. To the pair of axle shafts 26. And the cylinder chamber 45
The pressure is supplied to the piston 47 so that the piston 46 protrudes against the spring 47 so as to abut against the innermost brake ring 41C, and the brake rings 41A, 41B and 41C are brought into pressure contact with the brake disc 44 group. The desired braking action is performed by the operation of the plate brake device 40.

[0008]

However, according to the conventional structure described above, the friction surface of the brake disk 44 is made of a paper material or a rubber-based material, and is constantly in contact with the brake rings 41A, 41B, 41C during braking. are doing.
Therefore, since the middle (middle) brake ring 41B is sandwiched on both sides by the brake disc 44, that is, in a state similar to that sandwiched by the heat insulating material, it becomes difficult to dissipate heat and the braking ring 41B is formed. Thermal energy will be stored and the brake ring 4
Facing 44 of brake disc 44 in contact with 1B
There was an inconvenience that abrasion was accelerated only in a.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a multi-disc brake device capable of increasing the temperature of an intermediate brake ring by thermal energy during braking in the same manner as the brake rings at both ends. It was done.

[0010]

In order to achieve the above-mentioned object, a multi-plate brake device according to claim 1 of the present invention is provided.
A multiple-disc brake device in which a plurality of brake rings are provided on a fixed portion side and a plurality of brake disks disposed one by one between the brake rings on the rotation shaft side, wherein an intermediate brake ring has both ends. Characterized by being formed thicker with respect to the brake ring.

Therefore, according to the first aspect of the present invention, when the brake ring group is pressed against the brake disk group to perform the desired braking action, the intermediate brake ring has its thickness reduced by the thickness of the brake rings at both ends. By increasing the thickness and increasing the volume, the temperature rise due to the heat energy during braking can be made the same as the brake ring at both ends, so that the facing of the brake disc wears evenly at all parts become.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIG. In the embodiments of the present invention, the same or substantially the same components as those of the above-described conventional example (FIGS. 3 and 4) are denoted by the same reference numerals, and detailed description will be omitted. That is, in FIG. 1, 1 is a rotation axis, 2 is a transmission shaft, 10 is a differential body, 11 is a differential,
12 is a differential case, 22 is a recess, and 25 is a reduction gear device.

In the embodiment of the present invention, the multiple disc brake device 3 is provided between the differential body (fixed portion) 10 and both transmission shafts (rotating shafts) 2 by utilizing the recesses 22.
0 is provided. That is, three (plural) brake rings 31A, 31B, 31C are provided in the recess 22.
Is provided in contact with the inner peripheral surface of the recess 22 so as to be slidable in the direction of the rotation axis 1.

The transmission shaft 2 is provided with a hub disk 3.
3 are fixed, and two (a plurality of) brake disks 34 positioned one by one between the brake rings 31A, 31B, 31C are slidable in the direction of the rotation axis 1 on the hub disk 33. It is provided in. Further recesses 22
Inside the cylinder, a cylinder chamber 35 is formed in a concave shape. Inside the cylinder chamber 35, a piston 36 that can abut on the innermost brake ring 31C,
And a spring 37 for urging the spring in the backward direction.

Here, the brake rings 31A, 31B, 3
1C has the same inner diameter R, and the thickness T of the intermediate brake ring 31B is equal to the thickness of the brake ring 3 at both ends.
Thicker than the thickness t of 1A, 31C, that is, T> t
Specifically, T ≒ 2t is formed. The operation of the above embodiment will be described below.

The rotation of the propeller shaft is transmitted to a flange, a pinion gear shaft, a drive pinion gear, a ring gear, a differential case 12, and a transmission shaft 2, and is transmitted to a pair of axle shafts via a reduction gear device 25. Then, by supplying pressure to the cylinder chamber 35, the piston 36 is protruded against the spring 37 to abut on the innermost brake ring 31C, and the brake rings 31A, 31B, 31C are brought into contact with the brake disc 3.
The desired braking action is performed by the multiple disc brake device 30 by pressing against the fourth group.

At this time, the intermediate brake ring 31B is
By increasing the thickness T to the thickness t of the brake rings 31A and 31C at both ends and increasing the volume, the temperature rise due to the heat energy at the time of braking is the same as the brake rings 31A and 31C at both ends. As a result, the facing 34a of the brake disc 34 is uniformly worn at any portion.

The kinetic energy of the vehicle when decelerating by braking is absorbed by the brake disk 34 as heat energy. The heat energy per unit area of the brake disc 34 is He (J / c).
m ² ). Assuming that this heat energy is received in the opposed heat receiving volume per unit area of the frictionally applied brake rings 31A, 31B, 31C,
The temperature rise of A, 31B and 31C is represented by the following equation.

T = He / (VHs × γ × q) T: Temperature rise (K) He: Thermal energy (J / cm ² ) VHs: Steel heat receiving volume (cm ³ / cm ² ) γ: Iron density (g) / Cm ³ ) q: Specific heat of iron (J / g · K) Accordingly, as in the above-described embodiment, the inner diameters R and outer diameters of the brake rings 31A, 31B, 31C are the same,
By making the thickness T of the intermediate brake ring 31B nearly twice the thickness t of the brake rings 31A, 31C at both ends, the temperature rise of the brake rings 31A, 31B, 31C is made the same. Can be. Thus, in the brake disc 34, the wear of the facing 34a facing the intermediate brake ring 31B can be made the same as the wear of the facing facing the brake rings 31A and 31C at both ends.

Next, another embodiment of the present invention will be described with reference to FIG. That is, the brake rings 31A, 3
1B and 31C are the inner diameter r of the intermediate brake ring 31B.
Is smaller than the inner diameter R of the brake rings 31A and 31C at both ends, that is, r <R. The thickness T of the intermediate brake ring 31B is thicker than the thickness t of the brake rings 31A, 31C at both ends, that is, T> t, specifically, T ≒ 2t.

According to this alternative embodiment, the intermediate brake ring 31B also has an increased inner volume to increase the heat receiving volume, and improves the heat energy obtained by the brake ring 31B to the lubricating oil and the housing. are doing.
In the above embodiments, the intermediate brake ring 31
The thickness T of B is thicker than the thickness t of the brake rings 31A, 31C at both ends, that is, T ≒ 2t (about twice), but it is necessary to make it twice or nearly twice. There is no. That is, the intermediate brake ring 31B is made thicker than the brake rings 31A and 31C at both ends, and the temperature rise due to braking is made about the same or lower than the brake rings 31A and 31C at both ends (in some cases, compared to the brake rings 31A and 31C at the ends). May be slightly higher.) By doing so, the wear of the facing 34a of the brake disc 34 can be extended to the target time.

In each of the above-described embodiments, the type including three brake rings 31A, 31B, 31C and two brake disks 34 has been described. Even in the case of a combination of a plurality of different types, such as a type consisting of the above, uniform wear can be similarly achieved.

[0023]

According to the first aspect of the present invention, when the brake ring group is pressed against the brake disk group to perform the intended braking action, the thickness of the intermediate brake ring is reduced at both ends. By increasing the volume by increasing the thickness of the brake ring, the temperature rise due to thermal energy during braking can be made the same as with the brake rings at both ends, so that the facing of the brake disc is uniform at all parts Therefore, the wear can be extended to a target time.

[Brief description of the drawings]

FIG. 1 shows an example of an embodiment of the present invention and is a cross-sectional plan view of a main part of an axle multiple disc brake device.

FIG. 2 shows another embodiment of the present invention, and is a cross-sectional plan view of a main part of a multiple disc brake device for an axle.

FIG. 3 is a partially cutaway plan view of an axle, showing a conventional example.

FIG. 4 is a cross-sectional plan view of a main part of the multi-plate brake device for the axle.

[Explanation of symbols]

 REFERENCE SIGNS LIST 1 rotating shaft center 2 transmission shaft (rotating shaft) 10 differential body (fixed portion) 11 differential 22 recess 30 multiple disc brake device 31A end brake ring 31B intermediate brake ring 31C end brake ring 33 hub disk 34 brake disk 34a facing 36 Piston T Thickness of middle brake ring t Thickness of brake ring at end R Inner diameter of brake ring r Inner diameter of brake ring

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3J058 AA44 AA48 AA53 AA59 AA70 AA77 AA83 AA87 BA32 CB11 FA03 5H115 PA00 PG10 UI40

Claims (1)

[Claims] 1. A multi-plate brake device comprising: a plurality of brake rings provided on a fixed portion side; and a plurality of brake disks positioned one by one between the brake rings on a rotating shaft side. The brake ring of (1) is formed thicker than the brake rings at both ends.