JPH0728414Y2 - Friction plate - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Object of the Invention] (Field of Industrial Application) The present invention relates to a friction plate of a multi-plate clutch.

(Prior Art) USP3896684 discloses a differential limiting clutch for a differential device. Generally, in a multi-disc clutch, a large number of friction plates are alternately arranged and subjected to a pressing force, so that it is difficult for lubricating oil to enter the surface of the friction plates. If the lubricating oil is insufficient, heat, seizure, damage, or vibration and noise due to intermittent slip (stick slip) are likely to occur. Therefore, in the above conventional example, as shown in FIG.
A large number of concentric shallow grooves 103 are provided on the surface of the. However, although this shallow groove has an effect of evenly holding the lubricating oil on the surface, it holds only a small amount of the lubricating oil, and does not replace the new lubricating oil. Therefore, the above problems may occur especially when transmitting a large torque. In addition, there is also one in which radial oil grooves are provided on the surface of the friction plate as shown in USP 3,648,545. In this case, the lubricating oil is scattered by the centrifugal force, so that the amount of the lubricating oil held is small and there is no action to take in new lubricating oil.

(Problems to be solved by the invention) Therefore, the invention is a friction plate of a multi-plate clutch,
An object is to provide a friction plate whose surface is always lubricated with sufficient lubricating oil.

[Structure of the Invention] (Means for Solving the Problem) A friction plate of the present invention is one and the other friction plates of a multi-plate clutch that engages one and the other members that rotate relative to each other.
While bending under the fastening force, undulations formed in radial directions opposite to each other so as to form continuous concave and convex portions in the circumferential cross-sectional area are provided respectively, and between adjacent undulations, one of It is characterized in that the volume of the facing portion formed between the concave portion and the other concave portion is changed by relative rotation and bending.

(Operation) The amount of flexure of the swell increases or decreases due to fluctuations in the fastening force of the multi-plate clutch, and the volume between one concave portion and the other concave portion changes, causing a pumping action at various places. By this pump action, lubricating oil is sucked into and discharged from the recess. In this way, the recess becomes a reservoir of lubricating oil, and the lubricating oil is constantly replaced. Further, with the relative rotation of the friction plate, the respective convex portions pass over the other concave portion while changing their contact points, and are supplied with lubricating oil. The engaging force of the multi-plate clutch is uniformly dispersed by the spring action of the undulation and the surface pressure becomes constant, so that noise and vibration at the time of engagement, or stick slip is prevented.

(Embodiment) An embodiment will be described with reference to FIGS. 1 to 3. The multi-plate clutch using this embodiment is used as the differential limiting means of the differential device shown in FIG. Hereinafter, the left and right directions are the left and right directions in FIG.

First, the differential device will be described with reference to FIG. This device is arranged on the drive side axle of the vehicle.

A ring gear (not shown) is fixed to the flange portion 3 of the differential case 1, and the differential case 1 is rotationally driven by the driving force from the engine via the ring gear. A pair of pressure rings 5 and 7 are engaged with the differential case 1 so as to rotate integrally and slidably in the axial direction. Four pinion shafts 9 are arranged between the rings 5 and 7. The shaft 9 is fixed (constantly formed) radially to the ring-shaped boss 11 at equal intervals around the boss 11. A cam portion 13 is formed between the tip of the shaft 9 and the opposing portion of the rings 5 and 7 to give left and right cam forces to the rings 5 and 7, respectively, when they try to rotate relative to each other. Pinion gears 15 are rotatably supported on the shafts 9, respectively. A pair of side gears 17, 19 meshes with the gear 15 from the left and right. A left axle 21 is spline-connected to the left side gear 17, and a right axle 23 is axially slidably connected to the right side gear 19.

Therefore, the driving force from the engine is the differential case 1, the pressure rings 5, 7, the pinion shaft 9, the pinion gear 1
5, transmitted through the side gears 17, 19 and the axles 21, 23, and differentially distributed to the left and right wheels by the rotation of the pinion gear 15.

Between the differential case 1 and the pressure rings 5, 7, there are arranged multi-plate clutches 25, 27 which connect the differential case 1 and the side gears 17, 19 and serve as differential limiting means. The outer and inner friction plates 29 and 31 of the clutches 25 and 27 are alternately arranged. The outer friction plate 29 is located inside the casing 1 and the inner friction plate 31 is located outside the left and right side gears 17 and 19. Each is connected by a lug so as to be movable in the axial direction. The multi-plate clutches 25 and 27 are pressed and fastened via the pressure rings 5 and 7 by the cam force of the cam 13 and the backward force of the side gears 17 and 19 due to the engagement with the pinion gear 15.

Therefore, while traveling, the multi-plate clutches 25, 27 are always engaged with a certain amount of force due to the above-mentioned force due to the drive resistance of the wheels, and the differential between the left and right wheels is limited. The property is improved. Further, even if the driving resistances of the left and right wheels differ, for example, when driving on a rough road or turning, a large driving force is transmitted to the wheel side having a large driving resistance due to the differential limiting force, so that the running performance and the turning performance are improved. Is improved.

As shown in FIG. 1, the outer friction plate 29 is provided with a lug portion 33 for connection with the casing 1 on the outer circumference, and as shown in FIG. 2, the inner friction plate 31 is formed with the side gear 17 on the inner circumference. A lug portion 35 is provided for connection with the terminals 19, 19. Each friction plate 2
As shown in the respective drawings (b), reference numerals 9 and 31 are convex portions 37 and 39 and concave portions 41 and 43.
Has undulations 45, 47, which in turn include these undulations 45, 47
47, as shown in each of the drawings (a), the friction plate 29 is clockwise toward the outside, and the friction plate 31 is counterclockwise toward the outside. Thus, the directions of these undulations 45, 47 are opposite to each other, and the convex portions 37, 39 do not overlap the concave portions 41, 43.

When the fastening force is changed in size, the volume of the recesses 41, 43 increases or decreases due to the bending of the swells 45, 47, and the pump action sucks the lubricating oil into the recesses 41, 43 and the sucked lubricating oil is always Replace with new lubricating oil. Further, the one convex portion 37, 39 always changes its contact point with the relative rotation of the friction plates 29, 31 and passes over the other concave portion 41, 43 to be supplied with lubricating oil. In this way, the entire surfaces of the friction plates 29, 31 are always lubricated and cooled by the new lubricating oil, and the opposing friction surfaces do not have edges so that no oil film breakage occurs.
Further, due to the spring action of the undulations 45 and 47, the pressing force is evenly distributed to all the friction plates 29 and 31, and the surface pressure becomes constant, so that stick slip is prevented. Further, for example, even if a large pressing force is suddenly applied, this spring action alleviates shock, vibration, noise, etc. at the time of fastening.

The undulation size (cycle and height) may be different between the friction plate on one side and the friction plate on the other side, unlike the embodiment. For example, one undulation may be small and the friction plate may be substantially a flat plate.

Further, it goes without saying that the friction plate of the present invention can be used not only for the differential limiting means but also for a single multi-plate clutch.

[Advantage of the Invention] As described above, when the friction plate of the present invention is used, the surface thereof is always lubricated with sufficient lubricating oil, stick-slip is prevented in the multi-plate clutch, and vibration and noise at the time of engagement are small.

[Brief description of drawings]

FIG. 1 and FIG. 2 relate to one embodiment, respectively. (A) is a plan view, (b) is an enlarged sectional view taken along line AA of (a), (c) is a side view, and FIG. Sectional view of apparatus using this embodiment,
FIG. 4 is a plan view of a conventional example. 29,31 …… Friction plate, 37,39 …… Convex portion 41,43 …… Recessed portion, 45,47 …… Waviness

Claims (1)

[Scope of utility model registration request] 1. A friction plate of one and the other of a multi-plate clutch that engages with one and the other of the members that rotate relative to each other, is bent by receiving a fastening force, and is continuous in a circumferential sectional area. The undulations that are formed in opposite radial directions are formed on each of the ridges, and the volume of the facing portion between the adjacent ridges and between the one ridge and the other ridge is relatively rotated and bent. A friction plate characterized by being changed by.