JP6657080B2 - Multi-layer friction lining - Google Patents

Description

  The present invention relates to a multilayer friction lining comprising a carrier layer and a friction layer having a friction surface, and more particularly to a two-layer clutch lining. The invention further relates to a clutch disk with a drive disk, wherein a spring segment is fixed to the drive disk, to which the friction lining described above, in particular a two-layer clutch lining, is fixed. , Clutch disk.

  A multi-layer friction lining, in particular a two-layer clutch lining, known from WO 2007/121704 has a friction part forming a friction surface and a reinforcement part, the reinforcement part comprising a friction part. And has a higher burst rotation speed.

  It is an object of the present invention to increase the burst strength of a multilayer friction lining, in particular a two-layer clutch lining, comprising a carrier layer and a friction layer having a friction surface.

  This problem is solved in a multilayer friction lining, in particular a two-layer clutch lining, with a carrier layer and a friction layer having a friction surface, in which the carrier layer has at least one radial enlargement. You. The carrier layer and the friction layer are mainly in the form of a circular ring disk, preferably having a square cross section. The radial extension in the carrier layer may extend radially inward and / or radially outward. However, the radial enlargement is provided only on the carrier layer, not on the friction layer.

  In a preferred embodiment of the multilayer friction lining, the radial expansion of the carrier layer has a larger outer diameter than the friction layer. Due to the radial enlargement, the carrier layer extends radially outward beyond the friction layer.

  In another preferred embodiment of the multilayer friction lining, the radial extension of the carrier layer has a smaller inner diameter than the friction layer. Due to the radial expansion, the carrier layer extends radially inward beyond the friction layer.

  In another preferred embodiment of the multi-layer friction lining, the radial extension of the carrier layer is formed as an annular step. The concept of an annular step relates to a multilayer friction lining with a carrier layer and a friction layer.

  In another preferred embodiment of the multi-layer friction lining, the radial extension has approximately the same thickness as the carrier layer. The carrier layer and the friction layer are each in the form of a circular ring disk having a substantially preferably rectangular ring cross section. However, the carrier layer has a greater extension in the radial direction.

  In another preferred embodiment of the multi-layer friction lining, the radial extension has a somewhat smaller thickness compared to the carrier layer. With this configuration, it can be simply achieved that the pressure plate does not contact the carrier layer, in particular the radial enlargement of the carrier layer, when the friction layer is completely worn.

  In another preferred embodiment of the multi-layer friction lining, the carrier layer has a radial extension extending radially inward and a radial extension extending radially outward. With this configuration, the carrier layer expands with respect to the friction layer both radially outside and radially inside.

  The invention further relates to a clutch disc with a drive disc, in which a spring segment is fixed to the drive disc, on which the above-mentioned multilayer friction lining, in particular a two-layer clutch lining, is fixed. Have been. The drive disk functions to form a non-rotatable connection with a shaft, for example, a transmission shaft. The spring segments preferably function to preload the friction lining in the axial direction.

  In a preferred embodiment of the clutch disk, two multilayer friction linings as described above, in particular two two-layer clutch linings, are fixed to the spring segments. The spring segments preload both friction linings away from each other.

  In another preferred embodiment of the clutch disc, the two multilayer friction linings are formed symmetrically and contact the spring segments at their radial extensions. The symmetrical construction of the friction lining simplifies the manufacture and installation of the friction lining.

  Other advantages, features and details of the present invention are described below and different embodiments are described in detail below with reference to the drawings.

FIG. 2 is a cross-sectional view schematically showing a friction lining according to the invention with a radially inner enlargement. FIG. 2 is a cross-sectional view similar to FIG. 1, schematically illustrating a friction lining according to the invention with a radially outward enlargement. FIG. 3 is a cross-sectional view similar to FIGS. 1 and 2, schematically illustrating a friction lining according to the invention with a radially inner enlargement and a radially outer enlargement. FIG. 2 schematically shows a clutch disc with two friction linings corresponding to the friction lining shown in FIG. 1. FIG. 5 is a view showing a state in which a friction layer of the clutch disk shown in FIG. 4 has been worn. FIG. 6 is an enlarged view showing a region VI shown in FIG. 5.

  The present invention relates to adapting the lining geometry of a friction lining for the purpose of increasing the burst strength of the friction lining. The friction lining is mainly in the form of a circular ring having a square ring cross section.

  The friction lining has an inner diameter and an outer diameter. If the cross-sectional ratio between the outer and inner diameters of the friction lining is very small, in some cases, the desired burst strength is no longer provided.

  At very low cross-sectional ratios, the stresses generated in the friction lining may be so high as to cause undesirable bursts of the friction lining. As a result, the overall function of the clutch disk configured with the friction lining may be significantly impaired.

  According to an aspect of the invention, the dimensions of the friction layer remain the same. According to the invention, only the carrier layer is enlarged in order to increase the burst strength. The expansion of the carrier layer can take place radially inward and / or radially outward.

  In addition, steps or additional lining volumes are added axially to increase burst strength. This shoulder or additional lining volume serves to form a wear margin or a wear margin. The wear margin ensures that no catching or sticking of the pressure plate can occur.

  1 to 3 show three embodiments of the friction linings 1; 20; 30 schematically. The same reference numbers have been used to indicate the same or similar parts. Hereinafter, first, the common points of the friction linings 1; 20; 30 will be described, and then the differences of the friction linings 1; 20; 30 will be described.

  Each of the friction linings 1; 20; 30 has one carrier layer 3 and one friction layer 4. The side of the friction layer 4 opposite to the carrier layer 3 is a friction surface 5.

  The thickness of the carrier layer 3 is indicated by an arrow 6. The thickness of the friction layer 4 is indicated by an arrow 7. The thickness 7 of the friction layer 4 is also a possible wear layer thickness. Arrow 8 indicates the maximum possible wear, including all tolerances. The dash-dotted line 10 indicates the axis of rotation, the central axis or the longitudinal axis of the friction linings 1; 20;

  The inner and outer diameter of the friction surface 5 remains unchanged with respect to the conventional friction surface. According to an embodiment of the present invention, any structural space present radially inside the inner diameter of the friction surface 5 and / or radially outside the outer diameter is used for radially expanding the carrier layer 3. You.

  Thereby, at least one annular step is formed in the friction layer 4. The height or depth of this step, while encompassing all tolerances, is preferably greater than the required wear margin per friction lining. The annular step may be arranged radially inside and / or radially outside of the friction layer 4.

  In the friction lining 1 shown in FIG. 1, the carrier layer 3 has a radially enlarged portion 11. The radially enlarged portion 11 of the carrier layer 3 extends radially inward. The two-way arrow 12 shows how large the radial enlargement is relative to a conventional friction lining.

  The radial enlargement 11 has the same thickness or height as the carrier layer 3. The extension or dimension of the carrier layer 3 in the axial direction is called thickness or height. By axial is meant the direction in which the axis of rotation or longitudinal axis 10 extends, or the direction parallel to the axis of rotation or longitudinal axis 10.

  Arrow 13 indicates the inner diameter of the carrier layer 3 with the radial enlargement 11. Arrow 14 indicates the conventional inner diameter of carrier layer 3. The outer diameter of the friction lining 1 that does not change is indicated by the arrow 15. The friction layer 4 and the carrier layer 3 have the same outer diameter 15.

  In the friction lining 20 shown in FIG. 2, the radially enlarged portion 21 extends radially outward. Here, unlike FIG. 1, the inner diameter of the friction lining 20 remains unchanged. The resulting lining diameter in the carrier layer 3 is indicated by a double arrow 22.

  Arrow 23 indicates the outer diameter of friction layer 4, which corresponds to the outer diameter of a conventional carrier layer. The enlarged outer diameter of the carrier layer 3 with the radial enlargement 21 is indicated by the arrow 24.

  The friction lining 30 shown in FIG. 3 has an enlarged portion 31 extending radially inward and an enlarged portion 32 extending radially outward. The friction lining 30 is combined with the radially enlarged portion shown in FIGS. 1 and 2. The value obtained at the outer diameter of the carrier layer 3 is indicated by a two-way arrow 33.

  The outer diameter of the friction layer 4 is indicated by an arrow 34, which corresponds to the outer diameter of a conventional carrier layer. The enlarged outer diameter of the carrier layer 3 with the radial enlargement 32 is indicated by an arrow 35.

  The reduced inner diameter of the carrier layer 3 with the radial enlargement 31 is indicated by an arrow 36. The inner diameter of the friction layer 4 is indicated by an arrow 37, which corresponds to the inner diameter of a conventional carrier layer.

  4 to 6 schematically show the clutch disk 60 in a state where the clutch disk 60 is assembled together with the pressure plate 40. The clutch disc 60 has two friction linings 41, 42, also called friction lining halves. The friction lining 41 corresponds to the friction lining 1 shown in FIG. The friction lining 42 is symmetrical with respect to the friction lining 41 with respect to an axis of symmetry extending radially between the two friction linings 41, 42.

  The mounting state of the friction linings 41 and 42 will be described in detail below with respect to only the friction lining 1 in FIG. However, since the peripheral conditions for the friction linings 20, 30 in FIGS. 2 and 3 are equal, additional consideration of the friction linings 20, 30 in the installed state can be omitted.

  The two friction linings 41, 42 have in their carrier layers, respectively, a radially enlarged part 47, 48 extending radially inward. Arrows 43 indicate the thickness of the carrier layer. Arrow 44 indicates the thickness of the friction layer. The friction linings 41, 42 are non-rotatably connected by a spring segment 45 to a drive disk (Mitnehmerscheibe) 46.

  The spring segments 45 preload the friction linings 41, 42 in directions axially away from each other.

  Arrow 49 indicates the inner diameter of the friction layer of the friction lining or friction lining halves 41, 42. Arrow 50 indicates the reduced inner diameter of friction linings 41, 42 with radial enlargements 47, 48. The outer diameter of the friction linings 41, 42 is indicated by an arrow 51.

  FIG. 5 shows the friction lining 41 in a completely worn state. Arrow 54 indicates the wear thickness of the friction layer. Upon complete wear, the friction layer is almost completely worn.

  FIG. 6 is an enlarged view of the area VI shown in FIG. As can be seen from FIG. 6, when the friction layer of the friction lining 41 is completely worn, a slight gap 56 still remains between the pressure plate 40 and the radially enlarged portion 47. This ensures that the pressure plate 40 does not come into contact with the radial extension 47 of the carrier layer even during complete wear of the friction layer. As a result, undesired catching of the friction linings 41, 42 on the pressure plate 40 can be advantageously avoided.

DESCRIPTION OF SYMBOLS 1 Friction lining 3 Carrier layer 4 Friction layer 5 Friction surface 6 Arrow 7 Arrow 8 Arrow 10 Rotation axis 11 Radial expansion part 12 Bidirectional arrow 13 Arrow 14 Arrow 15 Arrow 20 Friction lining 21 Radial expansion part 22 Bidirectional arrow 23 Arrow 24 Arrow 30 Friction Lining 31 Radial Expansion 32 Radial Expansion 33 Bidirectional Arrow 34 Arrow 35 Arrow 36 Arrow 37 Arrow 40 Pressure Plate 41 Friction Lining 42 Friction Lining 43 Arrow 44 Arrow 45 Spring Segment 46 Drive Disc 47 Radial Expansion Part 48 Radial enlarged part 49 Arrow 50 Arrow 51 Arrow 54 Arrow 56 56 Interval 60 Clutch disc

Claims (7)

A multilayer friction lining (1; 20; 30; 41, 42) comprising a carrier layer (3) and a friction layer (4) having a friction surface (5),
Said carrier layer (3) has at least one radially enlarged part (11; 21; 31, 32; 47, 48);
It said radially enlarged portion thickness (11; 21; 31, 32 47, 48) is rather smaller than the thickness of the carrier layer (3),
Multilayer friction lining, characterized in that said radially enlarged portion (21) of said carrier layer (3) has a larger outer diameter than said friction layer (4) . The radial expansion of the carrier layer (3) (11; 47, 48), said has a smaller inner diameter than the friction layer (4), according to claim 1 Symbol placement multilayer friction lining. The radial expansion of the carrier layer (3) (11; 21; 31, 32; 47, 48) is formed as a stepped portion of the annular claim 1 or 2 multilayer friction lining according. It said carrier layer (3) is radially enlarged portion extending radially inwardly (31) and radially enlarged portion extending radially outward and a (32), Claims 1 to 3 A multilayer friction lining according to any one of the preceding claims. A clutch disc provided with a drive disc (46), wherein a spring segment drive disc (46) (45) is fixed to the spring segment (45), one of the Claims 1 to 4 1 A clutch disk, characterized in that the multilayer friction lining (1; 20; 30; 41, 42) according to the above item is fixed. Wherein the spring segments (45), two multi-layer friction lining according to any one of claims 1 to 4 (41, 42) is fixed, the clutch disc of claim 5, wherein. 7. The two-layer friction lining according to claim 6 , wherein the two friction linings are symmetrically formed and contact the spring segments at their radial extensions. Clutch disc.

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