KR20010051997A - Annular friction-clutch facing for a multi-disk clutch - Google Patents

Abstract

PURPOSE: An annular friction-clutch facing is provided to remove excessive lubricating agents formed on the facing by using grooves. CONSTITUTION: An annular friction-clutch facing(30) for a multi-disk clutch(10) includes an inner edge(32) and an outer edge(34) defining a width(w) of the facing(30). The facing(30) further includes a first group of grooves(136) formed on the facing(30) and having a first cross-sectional area. Each groove of the first group(136) has a first opening(38) at the outer edge(34) and a second opening(40) at the inner edge(32) remote from the first opening(38) and is adapted to direct lubricating agents across the width(w) over a substantial area of the facing(30). The facing(30) further includes a second group of grooves(42) formed on the facing(30) and having a second cross-sectional area smaller than the first cross-sectional area. The second group of grooves(42) includes first and second sets of grooves(44,46), respectively. The grooves of the first set(44) are disposed in intersecting relationship with the grooves of the second set(46). The second group of grooves(42) is adapted to remove excess of the lubricating agents on the facing(30).

Description

Circular friction clutch contact surface of multi-disc clutch {ANNULAR FRICTION-CLUTCH FACING FOR A MULTI-DISK CLUTCH}

The present invention relates to a multi-disk device. More particularly, the present invention relates to a frictional contact surface of a multi-disk device with improved lubrication properties.

Multi-disk friction devices are widely used in clutch or brake assemblies, such as in land vehicles. In general, such a vehicle can be divided into three main parts, a power generation unit such as an internal combustion engine, a power transmission unit and a wheel, and the power transmission unit typically refers to a transmission. Torque and speed generated by the engine are converted into power required for the movement of the vehicle in the transmission.

Such a transmission may include one or more gear sets including an intermediate plate gear or an inner sun gear supported by a carrier and an outer ring gear, and a gear ratio of the gear set. It consists of several elements for conversion. The multi-disc pack clutch is a friction device installed as a holding device in such a transmission or a differential, and can be widely used as a braking engine for various land vehicles such as wet brakes.

Such a multi-disk pack-clutch or brake assembly includes a plurality of ring-shaped disks and has a clutch subassembly. The subassembly comprises a set of friction disks which intersect with each other and are fixedly actuated to the hub and a set of plates arranged to be torsionally fixed and actuated to the disk carrier. Typically the clutch or brake assembly also includes a piston. As part of the gear set is used, such as in a particular gear range, the piston is operated so that the plate and the friction disk can be in relatively contact with each other. The plates are operated in a mutual gearing manner, and the friction disc is also operated in a mutual gearing manner. The sets are mutually replaceable in the axial direction and can be contacted or separated in pairs. In the "open pack" mode, the plate and the friction disc rotate without parallax. In some applications it is known to have several multi-disk friction devices that are connected to other drive connections via transmissions or differentials to provide various gear ratios or brake portions in operation.

In general, conventional multi-disc clutches or multi-disc brakes have discs connected to each other, i.e., discs integrally formed of a friction material. Such a device is shown in German patent 31 49 880 C2, German patent 35 32 759 C1, and German patent 31 18 565 A1.

Each friction disk includes a carrier plate made of steel or the like. The carrier plate comprises a friction surface on at least one circular surface. In general, the friction surface includes a fiber material made of paper or paper-like material. In general, the plate surface has a smooth structure. Thus, the contact surface of the cross-connected plate and the friction disk is covered with the friction surface. International patent WO 97/32678 discloses a special plate-face structure made of steel for improving the coefficient of friction between the friction disc and the plate.

When the friction device is activated, the kinetic energy is converted into thermal energy, and a considerable amount of heat is generated. If the friction surface wears or tears or is too hot to release heat, it can burn and damage the friction surface and reduce the operating efficiency of the clutch or brake. Moreover, the service life of a multi-disc clutch or similar device needs to be long. For example, during the service life of the clutch, the disks are in contact with each other innumerably and are subjected to large axial forces, thus providing a large surface pressure to each disk. Despite these needs, the process of power transmission remains unchanged, and each disk has a long service life. Defects in one or more disks will lead to failure of the entire device. And replacing a defective disk with a new one is not very easy. Therefore, it is of optimal economic importance to prolong the service life of the discs while maintaining the process of power transmission.

As a result, in the power transmission described above, the lubrication of each element plays a very important role. In particular, the lubricating oil must be reliably delivered throughout the contact surface of the discs. To that end, lubricating oil is generally applied to the friction surface. The high temperature is maintained to the extent possible limited by the lubricating oil.

In the prior art, the friction surface has a structural arrangement similar to a sponge with pores to hold a certain amount of oil. Retention oil is provided to the friction surface during clutch operation.

Many sources of failure of discs having such or other structures have been found, such as inadequate lubrication and inadequate characteristics of overfriction and friction linings.

Therefore, in the technical field related to power transmission, in particular multi-disk friction devices such as clutches and brakes, there is a need for a technology that can prolong the service life, in particular in the "open pack" mode, and prevent the disc from breaking. will be. The present invention organizes the disks so that lubrication is optimized, so that they transmit torque in an improved manner.

The present invention seeks to overcome the disadvantages of the circular friction clutch contact surface of such a conventional friction disk clutch. The contact surface includes an inner edge and an outer edge that determine its width. The contact surface also includes a first group of grooves formed in the contact surface and having a first intersection area. Each first group of grooves has a first opening at the outer edge and a second opening at the inner edge spaced from the first opening and across the width at a substantial area of the contact surface 30. Supply lubrication means directly. The facing also includes a second group of grooves formed in the contact surface and having a second crossing area smaller than the first crossing area. The second group of grooves includes first and second sets of grooves. The first set of grooves are arranged to intersect with the second set of grooves. The grooves of the second group act to remove excess lubrication means from the contact surface.

Thus, one advantage of the present invention is the supply of excess lubricating oil to the frictional contact surface.

Another advantage of the present invention is that the grooves release the heat generated by the friction device in the "closed pack" operating mode.

Another advantage of the present invention is that the grooves improve the friction characteristics of the multi-disk friction device.

Another advantage of the present invention is that the relatively large flow of lubricating oil in the grooves can improve the dissipation of frictional heat in the clutch, thereby extending the operating life of the disc.

Another advantage of the present invention is that the grooves apply lubricating oil all over the friction surface to every corner at all speeds during operation of the disks.

Another advantage of the present invention is that the grooves act to form a film with lubricating oil.

Another advantage of the present invention is that the energy density can be significantly improved to reduce the size of the disks or increase the friction with disks of the same size while maintaining the same frictional operation.

Another advantage of the present invention is that the flow of lubricating oil in the grooves does not prevent the absorption of the rod by the contact of the disks and therefore no time delay occurs.

Another advantage of the present invention

In conclusion, the circular friction-clutch contact surface of the multi-disc clutch according to the present invention as described above operates more effectively than the conventional contact surface, and the manufacturing cost is reduced.

1 is a schematic cross-sectional view of a multi-disk friction device according to the present invention;

2a is a plan view of a contact surface according to the invention, showing grooves of the first and second groups formed in the contact surface according to a preferred embodiment;

2B is a plan view of a contact surface according to the present invention showing first and second groups of grooves formed in the contact surface according to another preferred embodiment;

2c is a plan view of a contact surface according to the present invention showing the first and second groups of grooves formed in the contact surface according to another preferred embodiment;

3 is an enlarged plan view of a contact surface according to the present invention, showing grooves of the first and second groups formed in the contact surface according to the preferred embodiment of FIG.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

As shown in FIG. 1, the present invention relates to a friction device 10 of a clutch or brake engine, and is mainly used in connection with a transmission, a differential, or a brake structure. For example, but not by way of limitation, although not shown in the accompanying drawings, a transmission engine generally comprises an input shaft which works in conjunction with a basic power engine such as an internal combustion engine. In particular, a transmission engine used in automobiles further includes an output shaft interlocked with the wheel through a power transmission unit such as a drive shaft and a differential shaft, and at least one of the output shaft and the output shaft. A plurality of gear sets is installed. That is, the transmission engine includes the input shaft, the output shaft, and the gear set.

The gearset is equipped with several additional elements for changing the transmission gear ratio. To that end the transmission engine typically comprises at least one friction device 10. However, it is recognized as a conventional technique in the related art of the present invention that the transmission engine may be provided with several friction devices for power interruption and supply of the gear set when converting the gear ratio. Although described above in connection with an automobile, one of ordinary skill in the art may recognize that the present invention may be applied to a transmission, a differential, and a brake structure of an industrial device other than the automobile. Thus, the term "clutch" as used below is to be considered a concept that includes clutches or brakes used in all types of transmissions, differentials and brake systems.

As shown in the figure, the friction device (or clutch assembly 10) is composed of a drive part 12 and a driven part 14. The drive unit 12 includes a drive shaft 16. 1 shows that the drive shaft 16 is firmly connected to a disc carrier 18 that rotates around the axis “A” of the drive shaft 16, which will be described in detail below. Similarly, driven portion 14 includes driven hub 26. The driven hub 26 includes a spline 20 extending axially and located at the circular edge of the hub 26. The plurality of circular external drive disks 22 are splined or otherwise mounted at part 24 for axial movement relative to the disk carrier 18, thus making it possible to rotate around the axis “A” (24). Supported in the part. The plurality of circular internal driven disks 28 are splined or otherwise installed and operated by spline 20 so as to be able to rotate about axis " B ". Thus, as is well known in the art, the outer drive disks 22 and the inner driven disks 28 are intersected with each other and when the clutch is in the "Open Pack" mode as in the prior art. They rotate with time difference.

Each disk 22, 28 includes a working surface having a predetermined thickness, which can be in contact with the working surface of the adjacent disks 22, 28 so as to transmit torque to the adjacent disks 22, 28. have. The operating surface has a surface for frictional contact with a similar surface of an adjacent disk, which will be described in more detail below. In the preferred embodiment each disk 22, 28 is made of metal.

More specifically, the operating surfaces of the disks 22 and 28 include circular friction-clutch contact surfaces indicated at 30 in FIGS. 2A, 2B, 2C and 3, which are shown in FIGS. 2A, 2B, 2C and 3. Are denoted by like reference numerals, and some of them are displayed in increments of 100 to indicate similar structures. In a preferred embodiment, the friction-clutch contact surface 30 is made of a paper like material. Each contact surface 30 engages in contact with the operating surfaces of adjacent disks 22 and 28. In the operating mode, the working surface is applied with lubricating means such as oil to form an oil film (not shown).

According to the invention, each contact surface 30 comprises an inner edge 32 and an outer edge 34 which determine the width w. The contact surface 30 is formed with a first group of grooves 36 comprising a first cross section. Each groove 36 of the first group has a first opening 38 at the outer edge 34 and a second opening 40 at the inner edge 32 away from the first opening 38. . The grooves 36 of the first group also supply lubrication means across the width w to the corresponding areas of the contact surface 30. The contact surface 30 further comprises a second group of grooves 42 comprising a second cross section less than the first cross section. The second group of grooves 42 is composed of a first set of grooves 44 and a second set of grooves 46. The first set of grooves 44 are formed to intersect with the second set of grooves 46. These second groups of grooves 42 are for removing excess lubrication means of the contact surface 30.

The first group of grooves 36 may be formed to have many orientations, such as radial or secant. In the preferred embodiment shown in FIGS. 2A and 3, the first group of grooves 36 extend radially across the width w so that each of the first group of grooves 36 is defined as the diameter of the contact surface. D ₁ ) with a continuous angle of change. For example, one groove 36 is shown to extend at an angle of 40 degrees with respect to the diameter D ₁ of the contact surface 30 in FIG. 2A, and is shown to extend at an angle of 30 degrees in FIG. 3. The angle with respect to the diameter D ₁ of each other groove 36 varies. As shown in FIG. 3, the grooves 36 of the first group may be arranged to have a constant distance from the other grooves 36 of the first group. For example, the first grooves 36 are arranged at intervals of 10 degrees with respect to the diameter D ₂ line of the contact surface 30. Three other grooves 36 extend radially across the width w at 23 degrees, 34 degrees and 45 degrees relative to the diameter D ₂ .

In another preferred embodiment shown in FIG. 2B, the first group of grooves 136 are arranged at equal intervals with respect to the adjacent grooves 136 and extend exactly across the width w of the contact surface 30. In this way, the grooves 136 are formed to have a shape similar to the curve of the pump blades. Curves of the grooves 136 are formed along the direction of rotation of the contact surface 30. In the embodiment of FIG. 2B the direction of rotation of the contact surface 30 is counterclockwise.

However, in another preferred embodiment shown in FIG. 2C, the first predetermined portion of grooves 236 of the first group extend in exactly one direction across width w and are spaced at equal intervals with respect to adjacent grooves 248. Grooves 248 of the group and a second predetermined subgroup of grooves 250 extending in the exact opposite direction to the grooves 248 across the width w and disposed at the same increment for adjacent grooves 250. ). In the present embodiment, the grooves 248 and 250 are disposed independently of the direction of rotation of the contact surface 30.

Each of these preferred embodiments also has a second group of grooves 42 which in turn comprise first and second sets of grooves 44, 46. The first set of grooves 44 are arranged parallel to each other, extend radially across the width w, and are arranged at an orthogonal or 90 degree angle with respect to the second set of grooves 46. In other words, the second group of grooves 42 are formed in a mesh or lattice shape. It can also be called a "grid pattern". In this case it is necessary that the lubricating oil applied to the contact surface 30 be formed as flat as possible so that no significant hydrodynamic lubricating film is formed during the contact of the disks 22 and 28. However, one of ordinary skill in the art would think that the first set of grooves 44 may deviate from the radial extension line across the width w and may cross at an angle with the second set of grooves 46. There will be. The first and second sets of grooves 44, 46 are formed not too deep relative to the contact surface 30. In addition, the adjacent first group of grooves 36, 136, 236 are arranged to have a first placement interval with each other, and the adjacent second group of grooves 42 have a second distance smaller than the distance between the grooves 36 of the first group. It is arranged to have a spacing interval.

The first group of grooves 36, 136, 236 and the second group of grooves 42 have a variety of sizes and shapes. For example, the first group of grooves 36, 136, 236 may be deeply formed in the contact surface 30, and may form sharp edges in the contact surface 30. In a preferred embodiment the depth at the contact surface 30 is determined, wherein the grooves 36, 136, 236 of the first group are formed to have a depth deeper than the depth at which the grooves 42 of the second group are formed. In particular, the first group of grooves 36, 136, 236 may have twice the depth of the second group of grooves 42. However, one of ordinary skill in the art would appreciate that the depth of the grooves 36, 136, 236 can be any multiple of the depth of the grooves 42. In another preferred embodiment, the first group of grooves 36, 136, 236 are formed entirely through the depth of the contact surface 30.

The second group of grooves 42 have a second predetermined width, and the first group of grooves 36, 136, 236 have a first predetermined width that is significantly greater than the second predetermined width. In particular, the first group of grooves 36, 136, 236 may be twice as wide as the second group of grooves 42. However, one of ordinary skill in the art would appreciate that the width of the grooves 36, 136, 236 can be larger by any multiple of the width of the grooves 42. Moreover, the number of grooves 42 of the second group is greater than the number of grooves 36, 136, 236 of the first group. The grooves are formed in at least one and preferably all contact surfaces 30 for the storage of lubrication means. Those skilled in the art will appreciate that the present invention described may be formed on one or both adjacent surfaces of adjacent disks 22 and 28.

The structure of the contact surface 30 may be formed by applying or removing a material, including mechanical means. It is also possible to obtain the desired structure of the grooves by non-mechanical means. The contact surface 30 may be laser treated.

The combination of the grooves 36 and 42 of the first and second groups is optimal when operating. The first group of grooves 36, 136, 236 are arranged in such a way that the pumping effect is generated. The first group of grooves 36, 136, 236 also have a relatively large cross section so that a large amount of lubrication means can be delivered. Thus, the lubricating oil is effectively circulated by the grooves of the first group, so that the lubricating oil is applied to the entire surface of the disks 22, 28. The second group of grooves 42 act to remove excess lubricating oil, thus reducing the hydrodynamic effect of causing the contact surface 30 to float in the oil film. The grooves 36, 136, 236, 42 supply residual lubricant to the contact surfaces 30 of the disks 22, 28 and ensure that unlubricated operation does not occur on the contact surfaces between the inner disks 22, 28.

As a result, the grooves 36, 136, 236, 42 improve the frictional characteristics of the contact surface 30, so that the power absorption is constant while the disks 22, 28 move with the friction coefficient. In addition, the grooves 36, 136, 236, 42 in the contact surface 30 described above form an oil flow, in particular, to keep oil in a limited area of the discs 22, 28 so that the friction device 10 is deactivated. The heat generated is released.

More specifically, the grooves 36, 136, 236, 42 dissipate heat generated in the "closed pack" operating mode, thus improving the friction characteristics of the friction device 10. The relatively large flow of lubricating oil in the grooves 36, 136, 236, 42 improves the cooling of frictional heat in the clutch 10, thus extending the operating life of the disks 22, 28. The grooves 36, 136, 236, 42 also apply lubricating oil up to every corner of the discs 22, 28 to apply the entire contact surface 30 with the lubricating oil at all speeds during operation of the discs 22, 28. The grooves 36, 136, 236, 42 operate to form a film by lubricating oil. The energy density increases considerably, ie the size of the disks 22, 28 can be reduced while maintaining the same frictional operation, or the frictional operation can be increased while maintaining the size of the disks 22, 28. The flow of lubricating oil in the grooves 36, 136, 236, 42 does not block the absorption of the rod by the contact of the disks 22, 28.

The contact surface 30 of the present invention can operate effectively compared to the conventional contact surface, manufacturing cost can be reduced.

The present invention has been described above technically. In the above description, the terms are intended to be used as essential semantics of descriptive words rather than as restrictive. The present invention is not limited to the above embodiments and modifications may be made without departing from the basic principles of the present invention. Accordingly, the present invention may be modified in various ways within the scope of the following claims.

Claims (20)

An inner edge 32 and an outer edge 34 determining the width w of the contact surface 30; Formed in the contact surface 30 and having a first intersecting area, each having a first opening 38 at the outer edge 34 and a distance at the first opening 38 at the inner edge 32. A first group of grooves (136, 236) having a dull second opening (40) and directly supplying lubrication means across the width (w) to a substantial area of the contact surface (30); Formed in the contact surface 30, having a second crossing area smaller than the first crossing area, and consisting of first and second sets of grooves 44 and 46 so that the first set of grooves 44 A second group of grooves (42) arranged to intersect two sets of grooves (46) and operative to remove excess lubrication means at the contact surface (30); Circular friction-clutch contact surface 30 of the multi-disc clutch 10, characterized in that consisting of. 2. The groove of claim 1, wherein the grooves 36 of the first group extend radially across the width w such that each of the grooves 36 of the first group has a diameter D ₁ of the contact surface 30. Circular friction-clutch contact surface 30 of a multi-disc clutch 10, characterized by having a continuously varying angle. The method of claim 1, wherein the grooves 136 of the first group are arranged at equal intervals with respect to the adjacent grooves 136, characterized in that it extends exactly across the width (w) of the contact surface (30) Circular friction-clutch contact surface 30 of the multi-disc clutch 10. 2. The first predetermined subgroup of grooves of claim 1, wherein the first group of grooves 236 extend in exactly one direction across the width w and are spaced at equal intervals with respect to adjacent grooves 248. 248; The second predetermined subgroup grooves 250 extending in the exact opposite direction to the first predetermined subgroup grooves 248 and arranged at equal intervals with respect to the adjacent grooves 250. Circular friction-clutch contact surface 30 of the multi-disc clutch 10. 2. Circular friction-clutch contact surface (30) according to claim 1, characterized in that the first set of grooves (44) are arranged parallel to each other. 2. The circular friction-clutch contact surface (30) of claim 1, wherein the first set of grooves (44) extend radially across the width (w). 2. The circular friction-clutch contact surface 30 of claim 1, wherein the first set of grooves 44 are arranged to be orthogonal to the second set of grooves 46. . 2. The method of claim 1, wherein adjacent grooves 136 and 236 of the first group are arranged at a first placement interval, and adjacent grooves 42 of the second group are arranged at a second placement interval smaller than the first placement interval. Circular friction-clutch contact surface 30 of the multi-disc clutch 10. 2. The contact surface (30) of claim 1, wherein the contact surface (30) determines depth, and the first group of grooves (136, 236) and the second group of grooves (42) are formed by the depth, wherein the first group of grooves ( 136, 236 is formed to a deeper degree than the second group of grooves 42, the circular friction-clutch contact surface 30 of the multi-disc clutch 10. 10. The circular friction-of the multi-disc clutch 10 according to claim 9, characterized in that the depth of the grooves 136, 236 of the first group is formed to have a double depth with respect to the grooves 42 of the second group. Clutch contact surface 30. 10. Circular friction-clutch contact surface (30) according to claim 9, characterized in that the first group of grooves (136,236) are formed entirely along the depth of the contact surface (30). 2. The multi-function multiplier of claim 1, wherein the second group of grooves 42 have a second predetermined width and the first group of grooves 136, 236 have a first predetermined width that is significantly greater than the second predetermined width. The circular friction-clutch contact surface 30 of the disc clutch 10. 13. The circular friction-clutch contact surface of the multi-disc clutch 10 according to claim 12, wherein the width of the grooves 136, 236 of the first group is doubled the width of the grooves 42 of the second group. 30. 2. The circular friction-clutch contact surface (30) of claim 1, wherein the number of grooves (42) of the second group is greater than the number of grooves (136,236) of the first group. ). A drive member 12 comprising a plurality of drive disks 22 supported for rotation, and a drive member 14 comprising a plurality of driven disks 28 supported for rotation, said drive And the driven disks 22, 28 intersect each other such that each drive disk 22 is adjacent to the driven disk 28, providing selective frictional contact and the drive and driven members 12, 14. Can move closer and further away from each other to transfer torque between them, Each of the drive and driven disks 22, 28 includes a circular contact surface 30 arranged to frictionally contact the circular contact surface 30 of one of the adjacent disks 22, 28, wherein At least one of the circular contact surfaces 30 of the adjacent disks 22, 28 has an inner edge 32 and an outer edge 34 that determine the width w of the contact surface 30 and the contact surface 30. The first group of grooves 136 and 236 formed in the cross section and the second group of grooves 136 and 236 formed in the contact surface 30 and having a relatively narrow cross section compared to the first group of grooves 136 and 236. And 42, wherein the first group of grooves 136, 236 have a first opening 38 in the outer edge 34 and a first opening 38 in the inner edge 32. A second opening 40 at a distance and directly supply a lubrication means across the width w to a substantial area of the contact surface 30, the grooves 42 of the second group being the first and the first It consists of two sets of grooves 44, 46 so that the first set of grooves 44 intersect each other with the second set of grooves 46. Multi-disc friction device, characterized in that it is arranged to lock and to act to remove excess lubrication means from the contact surface (30). 16. The groove (36) of claim 15 wherein the grooves (36) of the first group extend radially across the width (w) such that each groove (36) of the first group has a diameter D ₁ of the contact surface (30). Multi-disc friction device 10, characterized in that it has a continuously varying angle. The method of claim 15, wherein the grooves 136 of the first group are disposed at equal intervals with respect to the adjacent grooves 136, and extend precisely across the width w of the contact surface 30. Multi-Disc Friction Device (10). 16. The first predetermined subgroup of grooves of claim 15, wherein the first group of grooves 236 extend in exactly one direction across the width w and are spaced at equal intervals with respect to adjacent grooves 248. 248; The second predetermined subgroup grooves 250 extending in the exact opposite direction to the first predetermined subgroup grooves 248 and arranged at equal intervals with respect to the adjacent grooves 250. Multi-disk friction device (10). 16. The multi-disk friction device (10) according to claim 15, wherein the first set of grooves (44) are arranged parallel to each other. 16. Multi-disc friction device (10) according to claim 15, characterized in that the first set of grooves (44) extend radially across the width (w).