Multi-plate clutch with reduced imbalance

Abstract

multi-plate clutch (1) comprising a clutch basket (2) with a plurality of alternately arranged outer plates (3, 4, 5, 6) and inner plates (7, 8, 9), where Each outer plate (3, 4, 5, 6) has at least one weight (23, 24, 25, 26) to compensate for a total imbalance (17) resulting from individual imbalances (13, 14, 15, 16) of the plates (3, 4, 5, 6) that occurs during operation of the multi-plate clutch (1), wherein each outer plate (3, 4, 5, 6) has areas (11) projecting into basket openings (10) of the clutch basket (2) and wherein a weight (23, 24, 25, 26) is arranged on at least one of the areas (11), wherein the outer plates (3, 4, 5, 6) are arranged in the clutch basket (2) such that the weights (23, 24, 25, 26) are radially distributed in a longitudinal direction (z) of the multi-plate clutch (1). are arranged offset from each other, wherein, with a number X of outer slats (3, 4, 5, 6), the weights (23, 24, 25, 26) are arranged radially offset from each other at an angle of 360° / X.

Description

The invention relates to a multi-plate clutch.

[0001] Multi-plate clutches have long been known in the art. A multi-plate clutch, or friction-plate clutch, is a machine component. Its distinguishing feature compared to other clutch systems is the parallel arrangement of outer and inner plates with friction linings. The same contact pressure acts on all friction pairs.

[0002] Multi-plate clutches can be engaged under load. They are widely used because they are compact and inexpensive. They are usually oil-immersed and are used predominantly in automatic transmissions, in highly loaded main or starting clutches, or in limited-slip differentials. In construction machinery, multi-plate clutches are also used as service and parking brakes.

[0003] As state of the art, reference is made, for example, to DE 100 05 838 A1 and DE 10 2008 041 368 A1.

[0004] A disadvantage of the current technology is that the loose connection of the outer plates in the clutch basket creates an imbalance, which can accumulate randomly if multiple plates are used. The plates are designed to be rotationally symmetrical according to the current state of the art, and the resulting imbalance is accepted. In dual clutches, the imbalance of the open clutch is added, although any flank centering is not relevant due to the load-free nature of the clutch.

[0005] The technical task is therefore to overcome the disadvantages of the state of the art.

[0006] The object is achieved according to the invention in particular by a multi-plate clutch having a clutch basket with a plurality of alternately arranged outer plates and inner plates, wherein at least one weight is arranged on each outer plate or on each inner plate to compensate for a total imbalance resulting from individual imbalances of the plates that occurs during operation of the multi-plate clutch.

[0007] By providing weights that are specifically oriented, the lamellae can be brought into a radially defined position such that the individual imbalances of the individual lamellae are just compensated. The weights are preferably intended as additional masses.

[0008] Preferably, the weights should be designed in such a way that any imbalance due to the additional mass is always greater than any tolerance-related imbalance due to the system's play, masses, and component tolerances. This allows a defined imbalance position to be achieved for each lamella.

[0009] Preferably, the total imbalance of the outer plates results from different radial individual imbalances of the outer plates in the plate cage. The total imbalance is preferably understood as a total imbalance. The weights are oriented in such a way that the total imbalance is minimized. Particularly preferably, an individual imbalance of a plate results from the product of the displacement of the plate and the mass of the plate. The mass of the plate is composed of the dead weight of the plate and the weight arranged on the plate.

[0010] Preferably, a first outer lamella has a first weight, a second outer lamella has a second weight, a third outer lamella has a third weight, etc.

[0011] Preferably, a first inner plate has a first weight, a second inner plate has a second weight, a third inner plate has a third weight, etc.

[0012] The multi-plate clutch is preferably a multi-disk clutch. The outer plate is preferably a clutch plate, in particular a steel plate. The inner plate is preferably an output plate, in particular a friction plate.

[0013] Particularly preferably, at least one recess or bore can be introduced into the lamellae instead of the weights. By providing specifically oriented recesses or bores, the lamellae can be brought into a radially defined position such that the individual imbalances of the individual lamellae just compensate for each other.

[0014] In an embodiment according to the invention, each outer plate has regions projecting into basket openings of the clutch basket, wherein a weight is arranged on at least one of the regions.

[0015] This makes it easy to attach the weights to the outer slats.

[0016] In an embodiment according to the invention, the outer plates are arranged in the clutch basket in such a way that the weights are arranged radially offset from one another in a longitudinal direction of the multi-plate clutch.

[0017] In this way, the weights are oriented in the clutch basket in such a way that the total imbalance is minimized.

[0018] In an embodiment according to the invention, with a number of X outer slats, the weights are arranged radially offset from one another at an angle of 360° / X.

[0019] This shows us a way to arrange the weights in a structured manner on the outer slats.

[0020] In a further embodiment of the invention, each inner lamella has at least one region in which a weight is arranged.

[0021] This makes it easy to attach the weights to the inner slats.

[0022] In a further embodiment according to the invention, the inner plates are arranged in the clutch basket in such a way that the weights are arranged radially offset from one another in a longitudinal direction of the multi-plate clutch.

[0023] In this way, an alternative is presented to orient the weights in such a way that the total unbalance is minimized.

[0024] In a further embodiment of the invention, with a number of X inner plates, the weights are arranged radially offset from one another at an angle of 360° / X.

[0025] This shows us a way to arrange the weights in a structured manner on the inner slats.

[0026] In a further embodiment of the invention, the weights are applied by means of a punching process or are designed as balancing rivets.

[0027] This makes it easy to attach the weights to the slats.

[0028] In a further embodiment of the invention, a product of the factors [mass of the weight] x [distance from a center of gravity of the weight to a rotational axis (z) of the outer disk] is greater than a sum of the summands [static unbalance of the outer disk] + [dynamic unbalance of the outer disk].

[0029] In this way, the weights are oriented in such a way that the total unbalance is minimized.

[0030] In a further embodiment according to the invention, the static imbalance results from an inherent imbalance of the outer plate and the dynamic imbalance results from a product of the mass of the outer plate and the existing play between the outer surface of the outer plate and the inner surface of the clutch basket.

[0031] The invention will now be illustrated by way of example with the aid of figures. They show: Fig. 1 a schematic longitudinal section through a known multi-disk clutch, Fig. 2 a schematic cross section AA through a portion of the multi-disk clutch from Fig. 1, Fig. 3 a graph with a resulting total imbalance of the outer plates of the multi-plate clutch from Fig. 1, Fig. 4 a schematic longitudinal section through the multi-disk clutch according to the invention, Fig. 5 a schematic cross section BB through a portion of the multi-disk clutch from Fig. 4, Fig. 6 a graph with a reduced total unbalance of the outer plates of the multi-plate clutch from Fig. 4 and Fig. 7 shows a further schematic cross section BB through a partial area of ​​the multi-disk clutch from Fig. 4.

[0032] Fig. Figure 1 shows a schematic longitudinal section through a known multi-plate clutch 50. The multi-plate clutch 50 has a clutch basket 2 with a plurality of alternately arranged outer plates 3, 4, 5, 6 and inner plates 7, 8, 9. Four outer plates 3, 4, 5, 6 and three inner plates 7, 8, 9 are shown.

[0033] Due to the loose connection of the outer plates 3, 4, 5, 6 in the clutch basket 2, a total unbalance 17 is created, which can be added randomly with several outer plates 3, 4, 5, 6, as in Fig. 3, showing a possible clearance 19. The total imbalance 17 results from the individual imbalances of the outer plates 3, 4, 5, 6. The outer plates 3, 4, 5, 6 are designed rotationally symmetrically.

[0034] An individual imbalance 13, 14, 15, 16 of an outer plate 3, 4, 5, 6 results from the product of the displacement 13, 14, 15, 16 of the outer plate 3, 4, 5, 6 and the mass of the outer plate 3, 4, 5, 6. The mass of the outer plate 3, 4, 5, 6 corresponds to the dead weight of the outer plate 3, 4, 5, 6. The resulting total unbalance 17 is accepted. In the case of double clutches, an unbalance of the respective open clutch is added, whereby any flank centering does not take into account here due to the lack of load.

[0035] Each outer plate 3, 4, 5, 6 has areas 11 projecting into the basket openings 10 of the clutch basket 2. The clutch basket prevents a displacement of the outer plates 3, 4, 5, 6 that exceeds the geometry of the clutch basket 2. A displacement of the outer plate 3 is Fig. 2 shown.

[0036] Fig. 4 shows a schematic longitudinal section through the multi-plate clutch 1 according to the invention. The multi-plate clutch 1 has a clutch basket 2 with a plurality of alternately arranged outer plates 3, 4, 5, 6 and inner plates 7, 8, 9. Four outer plates 3, 4, 5, 6 and three inner plates 7, 8, 9 are shown. A weight 23, 24, 25, 26 is arranged on each outer plate 3, 4, 5, 6. A first weight 23 is arranged on a first outer plate 3, a second weight 24 is arranged on a second outer plate 4, a third weight 25 is arranged on a third outer plate 5, and a fourth weight 26 is arranged on a fourth outer plate 6.

[0037] Each outer plate 3, 4, 5, 6 has regions 11 projecting into basket openings 10 of the clutch basket 2. A weight 23, 24, 25, 26 is arranged on one of the regions 11 of each outer plate 3, 4, 5, 6.

[0038] The outer plates 3, 4, 5, 6 are arranged in the clutch basket 2 such that the weights 23, 24, 25, 26 are radially offset from one another in a longitudinal direction z of the multi-plate clutch 1. The weights 23, 24, 25, 26 are radially offset from one another by 90°. The weights 23, 24, 25, 26 are oriented such that the total imbalance 17 is minimized or compensated for.

[0039] The weights 23, 24, 25, 26 are attached by means of a punching process or are designed as balancing rivets.

[0040] The weights 23, 24, 25, 26 serve to compensate for a total unbalance 17 that occurs during operation of the multi-disk clutch 1. The total unbalance 17 that occurs results from the individual unbalances 13, 14, 15, 16 of the outer plates 3, 4, 5, 6 in the plate cage 2, according to Fig. 6, where a possible play 19 is shown. A single imbalance 13, 14, 15, 16 of an outer plate 3, 4, 5, 6 results from the product of the displacement 13, 14, 15, 16 of the outer plate 3, 4, 5, 6 and the mass of the outer plate 3, 4, 5, 6. The mass of the outer plate 3, 4, 5, 6 is composed of the dead weight of the outer plate 3, 4, 5, 6 and the weight 23, 24, 25, 26 arranged on the outer plate 3, 4, 5, 6. A displacement of the outer plate 3 is in Fig. 5. Since the individual unbalances 13, 14, 15, 16 of the outer plates 3, 4, 5, 6 are all oriented in opposite directions, a compensated total unbalance 17 is established, which is equal to zero.

[0041] Fig. 7 shows a further schematic cross section BB through a partial area of ​​the multi-disk clutch 1 from Fig. 4.

[0042] As already mentioned, the weights are oriented to minimize the total unbalance. The weights are designed in such a way that the unbalance due to the additional mass is always greater than the tolerance-related unbalance due to the clearances, masses, and component tolerances in the system. In this way, a defined unbalance position is achieved for each lamination.

[0043] A product of the factors [mass of weight 23] x [distance 20 from a center of gravity of weight 23 to the axis of rotation z of outer plate 3] is greater than a sum of the summands [static unbalance of outer plate 3] + [dynamic unbalance of outer plate 3].

[0044] The dynamic imbalance results from a product of the mass of the outer plate 3 and the existing clearance 19 between the outer surface of the outer plate 3 and the inner surface of the clutch basket 2. List of reference symbols 1 multi-plate clutch 2 clutch basket 3 outer slats 4 outer slats 5 outer slat 6 outer slats 7 inner lamella 8 inner lamella 9 inner lamella 10 Basket opening 11 Area 13 Single unbalance 14 Single unbalance 15 Single unbalance 16 single unbalance 17 Total unbalance 19 game 20 radius 23 Weight 24 Weight 25 weight 26 Weight 50 multi-plate clutch x axis y axis z axis

Claims

[1] Multi-plate clutch (1) comprising a clutch basket (2) with a plurality of alternately arranged outer plates (3, 4, 5, 6) and inner plates (7, 8, 9), where at least one weight (23, 24, 25, 26) is arranged on each outer plate (3, 4, 5, 6) to compensate for a total imbalance (17) arising during operation of the multi-plate clutch (1) and resulting from individual imbalances (13, 14, 15, 16) of the plates (3, 4, 5, 6), wherein each outer plate (3, 4, 5, 6) has regions (11) projecting into basket openings (10) of the clutch basket (2) and wherein a weight (23, 24, 25, 26) is arranged on at least one of the regions (11), wherein the outer plates (3, 4, 5, 6) are arranged in the clutch basket (2) in such a way that the weights (23, 24, 25, 26) in a longitudinal direction (z) of the multi-plate clutch (1) are arranged radially offset from one another, wherein with a number of X outer plates (3, 4, 5, 6) the weights (23, 24, 25, 26) are arranged radially offset from one another at an angle of 360° / X. [2] Multi-plate clutch (1) according to one of the preceding claims, wherein the weights (23, 24, 25, 26) are applied by means of a punching process or are designed as balancing rivets. [3] Multi-plate clutch (1) according to one of the preceding claims, wherein a product of the factors [mass of the weight (23, 24, 25, 26)] x [distance (20) from a center of gravity of the weight (23, 24, 25, 26) to a rotational axis (z) of the outer plate (3, 4, 5, 6)] is greater than a sum of the summands [static imbalance of the outer plate (3, 4, 5, 6)] + [dynamic imbalance of the outer plate (3, 4, 5, 6)]. [4] Multi-plate clutch (1) according to claim 3, wherein the static imbalance results from an inherent imbalance of the outer plate (3, 4, 5, 6) and the dynamic imbalance results from a product of the mass of the outer plate (3, 4, 5, 6) and the existing play (19) between the outer surface of the outer plate (3, 4, 5, 6) and the inner surface of the clutch basket (2).

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