KR20180053243A - Friction lining multi-plate for a multi-plate clutch or a multi-plate brake of a motor vehicle - Google Patents

Abstract

The present invention relates to a friction lining multi-plate (15) for a multi-plate clutch or a multi-plate brake of a vehicle having two shaft directional surfaces (16, 16′) with a ring disc shape. In the present invention, a friction lining (17) is provided on a shaft directional surface of one of two shaft directional surfaces (16, 16′) with the ring disc shape, and the friction lining (17) is provided with a groove (18) assembly through which oil can flow. The friction lining multi-plate (15) according to the present invention is characterized in that the assembly has a cell-shaped geometrical structure. In addition, the present invention relates to a corresponding multi-plate clutch and a corresponding multi-plate brake.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a multi-plate clutch or multi-

The present invention relates to a multi-plate clutch of a motor vehicle or a friction lining multi-plate for a multi-plate brake, and a corresponding multi-plate clutch and a corresponding multi-plate brake, according to the preamble of claim 1.

In the prior art, there are known multi-plate clutches and multi-plate brakes each including a plurality of annular frictional lining plates. In this case, usually, the first group is fixedly connected to rotate with the multi-plate carrier by the internally toothed multi-plate, while the second group is fixedly connected by the externally toothed multi- . At this time, the two groups can move relative to each other in the axial direction and can be connected in a frictional engagement manner. Such a friction lining multi-plate is typically constructed in the form of a layer with one support plate and one or more friction linings, for example made of steel, on which the friction lining is arranged on the annular surface of the support plate, In general, it is connected to the support plate in a non-disassembly manner. Friction lining often consists of fibrous materials made from paper-containing materials or carbon. Plates coated with friction lining on both sides as well as on one side are actually used. In the case of a multi-faced plate coated with one surface, since the friction lining of one multi-plate is in contact with the supporting plate of the other multi-plate, two adjacent multi-plates interact with each other. In the case of a double-sided coated multi-plate, one double-coated multi-plate is disposed between two neighboring uncoated multi-plates. In the shifting process of the multi-plate clutch or the braking process of the multi-plate brake, a very high frictional output which causes a strong temperature rise may occur in the multi-plate. To release the generated heat, a coolant or lubricant is usually provided which is suitable for the inlet of the multi-plate. For the most part, the cooling oil flow is supplied radially from the inner diameter of the multi-plate to the multi-plate, and the multi-plate packet is perfused through the milled or engraved grooves inside the friction lining. In this case, a number of different geometric shapes for the friction lining grooves are known. Here, for example, so-called waffle grooves, radial grooves and tangential grooves are referred to as basic patterns. It is often the case that various groove basic patterns are combined with each other.

In this connection, US 5,335,765 describes a wet running frictional lining multiple plate for an automatic transmission clutch, provided with two sets of grooves engraved inside the friction surface. The grooves of the two sets of grooves are distributed symmetrically around the friction surface. Each groove of the two set of grooves extends from the inner edge of the friction surface to the outer edge of the friction surface at an angle tilted backwardly obliquely in the radial direction with respect to the direction of rotation. The cooling oil for releasing heat flows into the groove from the inner diameter of the friction surface. In order to reach a rapid cooling oil flow from the inside to the outside, the inclination angle of the grooves of the second set of grooves is greater than the inclination angle of the grooves of the first set of grooves, in which case each second groove passes into the first groove, Extends from this point to the outer diameter of the friction surface. The first groove and the second groove meet each other near the inner diameter of the frictional surface and in this case the cooling oil inlet cross section which can be used for the perfusion of cooling oil flowing into the friction lining multi- Corresponds to the free cross-section of the first groove. The outlet section for the cooling oil corresponds to the sum of the free cross sections of the first and second grooves at the frictional surface outer diameter and is approximately two times greater than the size of the cooling oil inlet cross section. The ratio of the grooves to the friction lining surface is relatively small. Corresponding to the alignment of the two sets of grooves, the friction lining multi-plate has a preferred rotation direction and can be used only along the one rotation direction without a functional loss.

DE 44 32 624 C1 discloses a friction lock for a converter lockup clutch of a torque converter with a plurality of grooves or grooves for the flow of cooling oil, mounted on an axially displaceable piston Lining is known and these grooves or grooves extend over a radially outer edge of the friction lining and an angle defined in the circumferential direction from the radially inner edge by a radial spacing that is automatically changed with respect to the axis of rotation of the friction lining do. In this case, each of the grooves or grooves is arranged such that the radial components of the grooves or grooves are arranged in opposition to the radial components prior to the change, one or more of their extensions Change direction. At the periphery, only a small number of inlets are distributed in the outer diameter of the friction lining, and there are only a few outlets in the inner diameter of the friction linings. At this time, the inlet and outlet of the groove proceed perpendicular to the rotational direction. In the course of travel of each groove from the radial outer side to the radially inner side of the friction lining, a pocket for temporarily storing cooling oil is disposed in the groove cross section. Correspondingly, within the groove travel path, the groove cross section is expanded in a section manner, and then narrows again in another groove travel path. The inlet cross section and the outlet cross section of the individual grooves are the same. With such a groove formation, it is necessary to reach as much uniform cooling of the friction lining surface as possible without requiring a relatively large cooling oil flow.

However, the known friction lining multi-plate is associated with disadvantages in that a target collision between the amount of cooling oil flow through the groove and the cooling oil staying time in the groove is not ideally calculated. As a result, the cooling oil may flow too quickly into the multi-plate, resulting in the failure of sufficient heat to escape from the multi-plate into the cooling oil, or as the cooling oil stays between the multiple plates for too long, And then heated. Another disadvantage of the geometry of the grooves, which are mostly used, is that the oil flow in the circumferential direction is not symmetrical. This means that the cooling oil will reach a different perfusion path depending on the inflow point in the inner diameter of the multi-plate, thereby causing it to encounter different flow resistances, and this situation can lead to uneven cooling of the multi- It causes.

An object of the present invention is to provide an improved friction lining multi-plate for multi-plate clutches or multi-plate brakes.

The above object is solved by a friction lining multi-plate for a multi-plate clutch or multi-plate brake according to claim 1 of the present invention. The preferred embodiments and improvements of the present invention are evident from the dependent claims.

The present invention relates to a multi-plate clutch or multi-plate brake friction lining multi-plate for automobiles having two axial faces in the form of annular discs, in which case friction occurs on at least one of the two axial faces of the annular disc- A lining is provided, wherein the friction lining has a groove assembly through which the oil can be perfused. The friction lining multi-plate according to the present invention is characterized in that the assembly has a geometry in the form of a cell.

Advantages arising from these characteristics are that the cooling oil or lubricating oil used for cooling or lubrication of the friction lining multi-plate according to the present invention, regardless of the inflow point into the groove and through the groove, Regardless, it always meets a uniform flow resistance. Thereby, on the one hand, the cooling oil or the lubricating oil does not sufficiently absorb the heat by passing too quickly through the grooves, so that no area in the friction lining multi-plate which can cause the superheating of the corresponding area of the friction lining multi-plate occurs . On the other hand, there is no point in the friction lining multiplate where the cooling oil or lubricant is too slow to penetrate the groove to absorb too much heat, which can cause overheating exceeding the permissible limit temperature of the cooling oil or lubricant . In other words, by the geometry of the cell geometry, a uniform and sufficient cooling over all areas of the friction lining plates can be ensured, in which case the cooling oil or lubricating oil is not particularly heated to exceed its permissible limit temperature Nor destroyed by this. Another advantage is the fact that the material stresses of the friction lining multi-plate due to temperature can be avoided by ensuring a uniform temperature across all areas of the friction lining multi-plate.

The term "cell-shaped geometry" is understood in the sense of the present invention to mean that a certain number of grooves each form a single geometric cell. This cell is the basic pattern that constitutes the groove assembly that spans the friction lining. Such a cell or such a basic pattern is arranged several times side by side to make a "cell-like geometry" according to the invention. In other words, you can think of a stamp as a printed pattern as a cell or a basic pattern. This print pattern is placed several times side by side to create a "cell-like geometry" in accordance with the present invention.

Preferably, the outer or inner plates of the multi-plate clutch or multi-plate brakes may likewise be treated as frictional lining plates.

According to a preferred embodiment of the present invention, it has been proposed that the cell geometry is formed as a hexagonal geometry. In other words, the cell geometry in this case consists of a hexagonal basic pattern that is repeatedly placed side by side several times. The hexagonal corners are formed by grooves. The hexagonal geometry is the structure with the best ratio of area enclosed to the circumference of all the basic patterns that can be placed side by side. Since the circumferential length is formed by the grooves, the axial surface of the friction lining multi-plate can be cooled with as few or as few grooves as possible. This simplifies the manufacture of such friction lining plates and thus reduces costs. At the same time, it is ensured that excessive flow resistance to the cooling oil or lubricating oil does not occur, since there are no sharp edges in the flow channel with an angle exceeding 60 degrees.

Such a hexagonal geometry is generally known as a "honeycomb" or honeycomb geometry.

According to another preferred embodiment of the present invention, it is proposed that the cell-shaped geometry is formed as an octagonal geometry. In the octagonal geometry, the axial faces of the friction lining plates are covered by a plurality of octagons arranged side by side, in which case the faces between the octagonal edges and the octagons are formed by the grooves. Since the octagons can be arranged side by side on one side without gaps, a change in the groove width is repeatedly generated in each cell. Such a change in the groove width can reduce the flow velocity of the cooling oil or lubricant passing through the groove again.

This allows for, for example, the use of relatively low viscosity cooling oil or lubricating oil or, generally, to extend the residence time of the cooling oil or lubricating oil in the groove and thereby enable higher heat release to the cooling oil or lubricating oil , The perfusion rate can be reduced as intended using an octagonal geometry.

According to another preferred embodiment of the present invention, it is proposed that the geometry of the cell shape is formed as a circular geometry. Similar to the octagonal geometry, one side can be completely covered using a circle of circular geometry. Thus, even in the circular geometry, there is a variation in the groove width which may cause a decrease in the perfusion rate. In circular geometry, the edges of the circles or the faces between the circles are formed by the grooves.

According to another preferred embodiment of the present invention, it is proposed that a cell-shaped geometric structure is formed such that the groove connects the radially inner surface of the friction lining multi-plate with the radially outer surface of the friction lining multi-plate. Thereby, the cooling oil or the lubricating oil can be selectively transferred from the radially inner surface of the friction lining multi-plate to the radially outer surface of the friction lining multi-plate, or vice versa. More specifically, individual cells are arranged side by side so that cooling oil or lubricant can continue to flow from the grooves of one cell to the grooves of neighboring cells. In this case, the cooling oil or the lubricating oil is guided along the groove along the axial surface, so that the axial surface can be uniformly cooled as a result.

Preferably, it has been proposed that the friction lining multi-plate begin to flow from its radially inner diameter to the radially outer diameter. In this embodiment, the centrifugal force supports the transporting effect on the cooling oil or the lubricating oil, whereby the advantage is that the pump with a relatively high output and high cost can be omitted. Furthermore, after the heated cooling oil or lubricant is discharged from the grooves, centrifugation is carried out while forming droplets, so that particularly effective cooling is exhibited because relatively small individual droplets have a relatively large surface per volume.

According to another preferred embodiment of the present invention, it has been proposed that the friction lining is divided by further split grooves. The split grooves divide the friction lining into two or more individual friction lining segments that are not connected to each other, i. E. This embodiment demonstrates the advantage that there is less friction lining produced as waste in the manufacturing aspect because the total amount of friction lining for the axial face needs to be present as a separate member in order to manufacture an individual friction lining segment And the relatively smaller retaining members of the friction lining can still be used.

Preferably, it has been proposed that the grooves be engraved inside the friction lining, grinded or milled. These three manufacturability proved equally rapid, inexpensive, and sufficiently accurate.

Furthermore, it can be said that the split grooves are preferably gaps in the friction lining, that is to say that the split grooves are formed between the individual friction lining segments that are produced solely by the absence of any friction lining, .

The invention also relates to a multi-plate clutch comprising one or more friction lining plates according to the invention. From this, the advantages already mentioned with respect to the friction lining multi-plate according to the invention also appear for the multi-plate clutch according to the invention.

Finally, the invention also relates to a multi-plate brake comprising one or more friction lining plates according to the invention. From this, the advantages already mentioned with respect to the friction lining multi-plate according to the invention also appear for the multi-plate brakes according to the invention.

The present invention is described below by way of example with reference to the embodiments shown in the respective figures.
Figure 1 illustrates, schematically and schematically, a friction lining multi-plate having a groove geometry known in the prior art,
Figure 2 illustrates, illustratively and schematically, one possible embodiment of a friction lining multi-plate according to the present invention,
Figure 3 illustrates, illustratively and schematically, another possible embodiment of a friction lining multi-plate according to the present invention,
Figure 4 illustrates, illustratively and schematically, another possible embodiment of a friction lining multi-plate according to the present invention,
5 illustrates an exemplary and schematic view of another possible embodiment of a friction lining multi-plate according to the present invention.

The same objects, functional units and equivalent components are designated with the same reference numerals throughout the drawings. These objects, functional units, and equivalents are embodied in the same manner with respect to their technical features, unless expressly or implicitly indicated otherwise herein.

1 shows an exemplary and schematic view of friction lining multiple plates 1 to 15 having a groove geometry known in the prior art. Fig. 1 (a) shows a friction lining multiple plate 1 without any grooves in the friction lining. Because of this, since the friction lining has the maximum surface, corresponding maximum friction effect also appears. However, the friction lining diaphragm 1 suffers from the risk of overheating even in a short period of frictional action. Fig. 1 (b) shows a friction lining multiple plate 2 having radial grooves. By virtue of the radial grooves having a tendency to rapidly outflow the cooling oil, the cooling effect of the cooling oil is consequently not completely extinguished, and the friction lining multi-plate 2 quickly overheats. The friction lining multi-plate 3 of FIG. 1C with a cross-shaped groove has only slightly improved with respect to the radial groove of FIG. Even though the cruciform grooves no longer face the radial direction of centrifugal force as a whole, the cooling oil quickly crosses the cruciform grooves to enable maximum cooling output. The cruciform grooves also have the additional disadvantage that the cooling oil causes uneven cooling of the friction lining plates by passing the cruciform grooves at different speeds according to their inlet points into the cruciform grooves. This situation causes material stress. The cross-shaped grooves aligned along the direction of action of the centrifugal force are relatively quickly perfused than the cross-shaped grooves aligned away from the direction of action of the centrifugal force. 1 (d) shows a friction lining multi-plate 4 having group parallel grooves. The reference to the radial groove of the friction lining multi-plate 2 of Fig. 1 (b) also applies substantially to the group parallel grooves of the friction lining multi-plate 4. The friction lining multi-plate 5 having a cross-bag type groove in Fig. 1 (e) has a cross-sectional shape in which the cross-sectional groove of the friction lining multi- Characteristic or cooling characteristic. Fig. 1 (f) shows a friction lining multi-plate 6 having a spiral grooved groove. Such a spiral grooved groove causes rapid overheating of the cooling oil due to difficulty in the perfusion of the cooling oil, and in some cases even quickly causing overheating to exceed the limit temperature of the cooling oil, The cooling effect is lost. 1 (g) shows a friction lining multi-plate 7 having waffle grooves. Such waffle grooves are substantially associated with the same disadvantages as the crisscross grooves of the friction lining multi-plate 3 shown in Fig. 1c, and in this case additionally, the fact that the cooling introduced into the waffle- By allowing a plurality of possible branches to be selected after the oil has flowed into the particular groove, the period of time in which the cooling oil stays within the waffle-shaped groove extends locally to such an extent that the cooling oil is heated beyond its limit temperature It is possible. Such hazards are particularly present in the region of the friction lining having grooves that are not aligned along the direction of action of the centrifugal force. In Fig. 1 (h), a friction lining multi-plate 8 having so-called sunburst type grooves can be seen. Such a sunburst-type groove tends to be over-rapidly perfused by the cooling oil, so that the cooling oil can not perform its own complete cooling function. Fig. 1 i shows a friction lining multi-plate 9 with a few annular grooves and an additional pressure relief bore. This causes uneven cooling of the friction lining multi-plate 9. In Fig. 1J, a friction lining multi-plate 10 having a multi-segment radial groove can be seen. As a multi-segment radial groove, a groove formed by the engagement of a plurality of individual friction lining members in the region of the friction lining multi-plate 10 in which no friction lining is provided is dealt with. Therefore, such multi-segment radial grooves always have a groove depth corresponding to the lining thickness of the friction lining. The small size of such grooves presents the advantage that only a relatively small number of friction linings are produced as waste. Because the radial grooves typically have a relatively large groove depth and likewise a relatively large groove width, the cooling oil typically flows through the radial groove too quickly to enable effective cooling. The friction lining multi-plate 11 of Fig. 1 has a multi-segment hook type groove. In this case too, since the multi-segment grooves are handled, the multi-segment hook-shaped grooves have a groove depth corresponding to the lining thickness. Due to the sharp edges within the multi-segment hook-shaped grooves, there is a high risk that the cooling oil will stay in the multi-segment hook-shaped grooves for too long to be heated beyond their limit temperature. This also applies to the friction lining multi-plate 12 having the multi-segment bottleneck grooves shown in Fig. 1. The friction lining multi-plate 13 of FIG. 1 shows a multi-segment cross-shaped groove. For multi-segment cross-shaped grooves, the previously mentioned discussion of the cross-shaped grooves of the friction lining multi-plate 3 of Figure 1, c, is applied in a more acute form because multi-segment cross- This is because it is deeper and wider than the groove.

Fig. 2 illustrates one possible embodiment of a friction lining multi-plate 15 according to the present invention for multi-plate brakes or multi-plate clutches of an automobile having two axial faces 16, 16 'in the form of an annular disc, . According to the example, the friction lining multi-plate 15 is formed as an external multi-plate 15. At least one axial face of the two axial faces 16, 16 'of the annular disc shape is provided with a friction lining 17 having a groove 18 assembly through which oil can flow on its side . In this case, since the groove 18 assembly in which the oil can be perfused has a geometry of a cell shape formed as a hexagonal geometry, the cooling oil does not have to stay in the groove for too long to overheat, on the one hand The situation is warranted and on the other hand a situation is ensured in which the cooling oil does not have to go through the groove too quickly to prevent heat absorption acting by the cooling oil. Also, depending on the geometry of the cell shape, the same flow resistance occurs in all regions of the friction lining multi-plate 15, and consequently, uneven cooling of the friction lining multi-plate 15 is avoided. As can be further seen in the enlarged cross-sectional view of FIG. 2, the grooves 18 have the same width everywhere, consequently clogging of the cooling oil and, in some cases, swirl formation are avoided in the grooves. At this time, the cooling oil is preferably subjected to the grooved path shown by the arrows, in which case none of the corners flowing through the cooling oil have an angle exceeding 60 degrees. Thereby, too, only a small flow resistance appears.

3 shows an illustrative and schematic view of another possible embodiment of a friction lining multi-plate 15 according to the present invention for a multi-plate brake or multi-plate clutch of an automobile. The friction lining multi-plate 15 of FIG. 3 differs from the friction lining multi-plate 15 of FIG. 2 in that a cell-shaped geometric structure, which is formed as a circular geometry by way of example, is formed. Such a formation increases the flow resistance to the cooling oil due to the variation of the groove width of the groove 18. Thus, the friction lining multi-plate 15 of Fig. 3 is particularly suitable for use with cooling oils of low viscosity, or for multi-plate clutches or multi-plate brakes with very high rpm causing high centrifugal forces, .

Fig. 4 exemplarily and schematically shows another possible embodiment of a friction lining multi-plate 15 according to the present invention for a multi-plate brake or multi-plate clutch of an automobile. The friction lining multi-plate 15 of Fig. 4 differs from the friction lining multi-plate 15 of Fig. 2 in that a cell-like geometry is formed in this case as an octagonal geometry. Similar to the circular geometry of the friction lining multi-plate 15 shown in FIG. 3, the octagonal geometry also causes variations in the groove width of the grooves 18, thereby increasing the flow resistance to the cooling oil. Accordingly, the friction lining multi-plate 15 of Fig. 4 is likewise suitable for cooling oil of particularly low viscosity or for multi-plate clutches or multi-plate brakes which are operated, for example, at very high rotational speeds, A high centrifugal force acting on the oil appears.

Fig. 5 exemplarily and schematically shows another possible embodiment of a friction lining multi-plate 15 according to the invention for multi-plate brakes or multi-plate clutches of an automobile. The friction lining multi-plate 15 of FIG. 5 differs from the embodiment of FIG. 2 in that the friction lining 17 is divided by an additional split groove 19. This leads to a more rapid perfusion of the cooling oil in the region of the friction lining multi-plate 15 with the split grooves 19, but thus advantageously makes the production of the friction lining multi-plate 15 shown in the figure, This is because the friction lining is produced as waste.

1: Friction lining multi-plate
2: Friction lining multi-plate
3: Friction lining multi-plate
4: Friction lining multi-plate
5: Friction lining multi-plate
6: Friction lining multi-plate
7: Friction lining multi-plate
8: Friction lining multi-plate
9: Friction lining multi-plate
10: Friction lining multi-plate
11: Friction lining multi-plate
12: Friction lining multi-plate
13: Friction lining multi-plate
15: Friction lining multi-plate
16, 16 ': an axial face of an annular disc shape
17: Friction lining
18: Groove
19: split groove

Claims (8)

A multi-plate clutch or multi-plate brake friction lining multiplate (15) for an automobile having two axial surfaces (16, 16 ') in the form of annular discs, characterized in that the two axial surfaces (16, 16' Wherein the friction lining (17) is provided with a groove (18) assembly through which the oil can flow, wherein the friction lining (17)
Characterized in that the groove assembly has a geometry in the form of a cell. The method according to claim 1,
Wherein the cell-shaped geometry is formed as a hexagonal geometry. The method according to claim 1,
Wherein the cell-shaped geometry is formed as an octagonal geometry. The method according to claim 1,
Wherein the cell-shaped geometric structure is formed as a circular geometric structure. The method according to any one of claims 1 to 4,
The cell-shaped geometry is characterized in that the groove (18) is formed to connect the radially inner surface of the friction lining multi-plate (15) with the radially outer surface of the friction lining multi- . The method according to any one of claims 1 to 5,
Characterized in that the friction lining (17) is divided by an additional split groove (19). A multi-plate clutch comprising one or more friction lining multipoles (15) according to at least one of the claims 1 to 6. A multi-plate brake comprising one or more friction lining multipoles (15) according to at least one of the claims 1 to 6.

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