DE8128631U1 - Damping washer - Google Patents

Description

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Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr. 81, D-8 Munich 81

For the present application, priority is given to Japanese application No. 1980-137489 filed on September 30, 1980 claimed.

The invention relates to a damping disk, which is used in connection with a friction clutch, in particular for land vehicles. In a damping disc of this type, there is an intermediate plate between each a radial flange of a hub splined to an output shaft and two side plates, namely a clutch plate and a holding plate. A first one that works with a low frictional force or a low one A friction element having frictional resistance is between the hub flange and each intermediate plate second working with a large frictional force or having a large frictional resistance friction element between each side plate and the adjacent intermediate plate arranged. With this arrangement, there will be a small torque transferred, whereby the relative torsion angle between the hub flange and the side plates is correspondingly small, -so Slippage arises at the top of the first-mentioned friction element and results in the generation of a small one Hysteresis torque. If the transmitted torque and thus the torsion angle increase, slip occurs on the friction surface of every second friction element and results in the generation of a large hysteresis torque. In this way, with damping discs with variable torque, noises can be detected in both the Effectively dampen or switch off the idle as well as the high load or high speed phase.

Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr. 81, D-8 Munich 81

In damping disks of this type, however, the strength of the radial flange has so far been due to large openings impaired, in which the intermediate plates holding together the web bolts and the Änschlagbolzen received connecting the side panels together. This makes it impossible to have large and long openings to be provided in the radial flange, in which there is space for correspondingly long torsion springs that would be able to absorb torque vibrations. As a result, this means that the desired absorption is not reached by torque vibrations.

The invention is therefore based on the object of a To provide damping washer of the type mentioned, which allows it, despite the necessary Receipt of the web bolts and stop bolts are large-volume and, in particular, are long in the circumferential direction Provide openings to accommodate torsion springs.

The object is achieved according to the invention by the subject matter of claim 1 solved.

Due to the special spatial arrangement of the recesses and the stay bolts and the stop bolts According to the invention, recesses are achieved in the circumferential direction to have much more space available for the introduction of openings in the radial flange. It succeeds, to distribute the forces occurring in such a way that one sees narrower material areas in the circumferential direction gets by. In this way, correspondingly long and / or more spring openings can be provided, whereby a

Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Siigcr, patent attorneys, Cosimastr. 81, D-8 Munich 81

correspondingly large corrosion angle with softer twisting characteristics what is obtained is the dampening absorption of vibrations during torque transmission benefits.

Further features and developments of the invention emerge from the subclaims in connection with the Embodiment shown in the drawing, to which particular reference is made and its following Description explains the invention in more detail.

It shows:

Fig. 1 is a sectional view of the damping disk according to the embodiment in connection with a clutch disc;

FIG. 2 is a partial sectional view showing another area of the exemplary embodiment according to FIG reproduces;

Fig. 3 is a side view from the direction of the arrows III-III in Fig. 1 of the embodiment, where sub-areas and individual components have been omitted;

FIG. 4 shows a schematic, enlarged partial view of a section of the radial flange according to FIG. 3;

Fig. 5 is a sectional view along the line V-V in Fig. 3;

6 is a diagram showing the relationship between torque and torsion angle;

Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr. 81, D-8 Munich 81

7 shows a schematic representation of a section of a radial flange of the previous type.

Fig.1 shows a hub 1 with internal teeth 2 for splinting onto an output shaft, not shown, and with a radial flange 3 on the peripheral surface = A pair of annular side plates 5 and 6 are arranged so that they form the radial flange 3 pick up between them. In the radially outer area of the side plate 5, damping plates 8 are provided with the aid of rivets 7 attached, which belong to a clutch plate. On both surfaces of the damping plates 8 are with With the aid of rivets 11, annular friction linings 10 are attached. The two side plates 5 and 6 are located radially on the outside Areas connected to each other with stop bolts 12. The side plate 5 is at its radially inner region provided with a bent cylindrical flange 14, which faces away from the radial flange 3 and is rotatable on the induction-hardened lateral surface of the hub 1 is held. The side plate 6, which is designed as a holding plate, has no such cylindrical flange on. With her, the inner edge around the outer surface of the hub 1 is kept spaced apart with a narrow gap.

An annular intermediate plate 16 is arranged between the radial flange 3 and each of the side plates 5 and 6. Between a radially inner area of the radial flange 3 and each of the two intermediate plates 16 is a first friction element 15 arranged. A second friction element 17 is located between each of the side plates 5 and 6 and the respectively adjacent intermediate plate 16. These friction elements 15 and 17 are as friction disks, wave springs or the like.

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Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Sliger, patent attorneys, Cosiraastr. 81, D-8 Munich 81

As can be seen in FIG. 2, there are radial central areas of the two intermediate plates 16 firmly connected to one another with the aid of web bolts 18. Press these stud bolts 18 the intermediate plates 16 against the second friction elements 17 so that each of these second friction elements 17 with large frictional force is applied or has a large frictional resistance. Because of this pressing force of the Web bolts 18 are the forces that act on each of the first friction elements 15, reduced accordingly, so that the frictional force that acts on each friction element 15 is kept small or the friction element 15 is a corresponding one has low frictional resistance. For this purpose, the surfaces of the first friction elements 15 be designed smoother and those of the second friction elements 17 rougher, which is the difference between the intended Frictional forces benefit.

As can be seen from Figure 1, a torsion spring 20, which is designed as a compressible helical spring, has a large diameter and a large spring wire thickness, while a further torsion spring 21, which is also designed as a compressible helical spring, has a small diameter and a small spring wire thickness . The torsion springs 20 and 21 extend with respect to their working direction substantially in the peripheral direction of the disk (with respect to the representation in Figure 1 perpendicular to the image plane), and in openings 24, 25 and 23 and 27, 28 and 26 incorporated in such a manner that they reach through the disks seen parallel to the disk axis and connect them to one another. For this purpose, the opening 23 arranged in the radial disk 3 are aligned with the openings 24 and 25 in the side plates 5 and 6 and receive the springs 20, while on the other hand the opening 26 provided in the radial flange 3 with those in the side plates 5 and 6 provided openings 27

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Dipl.-Ing. Otto Flügel, Dipl.-Ing, Manfred Siiger, patent attorneys, Cosimastr, 81, D-8 Munich 81

and 28 are aligned parallel to the disk axis and accommodate the smaller helical springs 22 (with regard to of the springs shown in Figure 1 corresponds to the aligned alignment of the transverse direction in the disk plane). The intermediate plates 16 are provided with openings through which the springs each take action.

From Figure 3 it can be seen that three large springs 20, two small springs 21 and a spring 22 are inserted into the disc, the spring 22 having a thinner wire diameter than the springs 21 have. One large spring 20 and one of the small springs 20 and 22 are shown in FIG Circumferential direction arranged one after the other and evenly distributed over the circumference, so that between the individual springs forms a constant distance. Outside each of the narrow springs 21 and 22 are three Arranged stop bolts 12 which protrude through recesses 30 formed in the radial flange 3. Included each recess 30 goes into the radially inwardly adjoining opening 26 for a spring 21 or into the Opening 31 for the spring 22 over. The recesses 30 are through an outer edge region 32 of the radial flange 3 bordered. Each intermediate plate 16 is provided with shallow indentations 40 within which the stop bolts 12 can be moved without attacking the washers. The web bolts 18 are each to the arranged adjacent to both end regions of the large springs 20; the disk accordingly has six web bolts 18. Each of the web bolts 18 extends through a recess 33 which is provided in the radial flange 3. Like Fig. 4

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Dipl, -Ing, Otto Flügel, Dipl.-Ing, Manfred Siigcr, Putenlanwiilte, Cosimastr. 81, D-8 Munich 81

can be seen, these recesses 33 are in the central area of the side edges 35 and 35 '(Figure 3) of the openings 23 formed. There are accordingly between each recess 33 and the inner and outer side edges 36 and 37 of each associated opening 23, flange areas 38 and 39 are created, each of which has radial lengths 1 and 1 '. The inner and outer edges 36 and 37 of each opening 23 are not provided with recesses. The ends of the springs 20 are dimensioned such that they rest on the areas 38 not covered by the recess and 39 are supported when a twisting operation, which will be explained later, occurs.

As can be seen from FIG. 5, between each stop bolt 12 and the adjacent two side edges 41 and 41 'of each recess 30 of the radial flange 3 there are spacings L1 and L'1 extending in the circumferential direction. These distances L1 and L ¹ I as well as further distances, which are described below, are set when the plates 5, 6 and 16 do not assume any rotational position with respect to the radial flange 3, as shown, the angle of rotation D (Fig. 6) so is zero degrees. The distance L1 corresponds to a maximum angle of rotation, ie 16 ° in FIG. 6 in the positive direction of torsion. The distance L ¹ I corresponds to the maximum angle of rotation 8 °, in the negative torsion direction. The distances L2 and L'2 are maintained between each web bolt 18 and the adjoining side edges 42 and 42 'of the recesses 33 in the radial flange 3. The distances L2 and L ¹ 2 correspond to the positive angle of rotation 12 ° and the negative angle of rotation 4 °, at which angles the second hysteresis torque H begins to occur. If the angle of rotation D is equal to zero degrees, both ends of the springs 20 and 21 are at the side edges 43 and 43 'or 44 and 44'

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Dipl.-Ing, Otlo Flügel, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr. 81, 0-8 Munich 81

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the openings in the side plates 5 and 6 are supported. Between the ends of the springs 20 and the side edges 35 and 35 'of the openings 23 in the Radialfansch 3 thereby distances L3 and L ¹ 3 occur. These distances L3 and L ¹ 3 correspond to a positive and a negative third angle of rotation 13 ° and 5 °. Between the ends of the springs 21 and the side edges 45 and 45 'of the openings 26 occur in the radial flange 3 distances L4 and L ¹ to 4, corresponding to a second positive torsion angle of 11 ° and a second negative torsion angle of 3 °. As can also be seen in FIG. 3, both ends of the spring 22 are supported by the side edges of the openings 31, 46 and 47 in the radial flange 3 and the two side plates 5 and 6. The side edges of the openings in the intermediate plates 16 are in contact with the ends of the springs 21 and 22, on the other hand, away from the ends of the springs 20 by distances corresponding to a twist angle of 1 (13 -12.5 -4) or more . This value of one degree is the torsional angle difference between the beginning of the third torsional phase by the springs 20 and the beginning of the second hysteresis torque H.

The mode of operation is as follows:

If in the operating position, as shown in Fig.1 to 5 and which corresponds to a torsion angle D of zero degrees, the clutch is actuated, so the friction linings are 10 pressed by a pressure plate, not shown, to the flywheel, not shown, of a prime mover, so a torque is applied to the side plates 5 and 6, causing the damping washer in direction of the arrow R in Fig.3 rotates. As long as the torque is low, the side plates are

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Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr. 81, D-8 Mi'-nchen 81

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th J and 6 via the second friction elements 17 without friction slip connected to the intermediate plates 16, while a friction slip on the surfaces of the first friction elements 15 occurs, so that a rotation of the side plates 5 and 6 relative to the radial flange 3 in the Direction of rotation R (Fig. 3) results. During this twisting movement, the weak spring 22 is driven by the in FIG recognizable left side of the opening 31 in the radial flange 3 on the one hand and through the right edges of the 3 openings 46 and 47 in the side plates 5 and 6 on the other hand pressed together. This way the torque is released from the side plates 5 and 6 are transmitted to the output shaft via the spring 22, the radial flange 3 and the hub 1. Though the feathers 20 and 21 perform the movement together with the side plates 5 and 6, they do not grip the side edges the openings 23 and 26 in the radial flange 3, which is why this torque is not via the springs 20 and 21 is transmitted. So there is only the weak spring 22 during this operating stage as a torque transmission spring is effective, the increase in torque T is a function of the torsion angle traversed D of the plates 5 and 6 are very small, as is the case with section a - b of the torque-angle-of-rotation characteristic curve X. can be seen in Fig.6. Furthermore, a small first hysteresis torque is generated by the friction slip of the friction elements 15 h is generated, as can also be seen in FIG. This operating stage extends up to a twist angle D of 11 °.

If the angle of rotation D exceeds 11 °, the Springs 21 moved over the distances L4 (Figure 5) and grip the side edges 45 of the openings 26 in the Radial flange 3 and begin to compress.

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Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr. 81, D-8 Munich 81 *

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This compression causes some of the torque from the side plates 5 and 6 to become the radial flange 3 transmitted via the springs 21. Since the torque is now transmitted via three springs 21 and 22, occurs in this operating phase an increase in the slope of the characteristic curve X, as shown in section b - d of Characteristic curve from Fig.6 can be seen. If the angle of rotation D reaches 12 °. so the web bolts 18 have the distances L2 (FIG. 5) and reach the side edges of the recesses 33 in the flange 3. After that attack (D - 12 °) the intermediate plates 16 are firmly in contact with the radial flange 3 in the direction of rotation, which is why now the side plates 5 and 6 are rotated relative to the intermediate plates 16 and the radial flange 3. this happens with frictional slip on the surfaces of the second friction elements 17, which require a high frictional force, which generates a large secondary hysteresis torque H in the area above the torque angle of 12 ° will. When the torsion angle has reached 13 °, the springs 20 have reached through the distances L3 (FIG. 5) and arrive at the side edges 35 of the openings 23 in the radial flange 3 to rest, so that now the compression the strong or hard springs 20 begins. In this way the torque is now from the side plates 5 and 5 are transmitted to the radial flange 3 via the springs 20. Since now all springs 20, 21 and 22 in this Operating phase are compressed and thus contribute to the transmission of the torque, the tendency of the grows Characteristic curve X in the area d - e in Fig. 6 accordingly.

As soon as the torsion angle D is 16 °, each stop bolt is located 12 on the side edges 41 of the associated recesses 30, whereby any further rotation between the plates is prevented.

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Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Siigcr, patent attorneys, Cosimastr. Sl, D-8 Munich 81

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If:, the torque T from its maximum value to 0 kgm falls, the torsion angle D decreases to zero degrees. During this reduction phase, the changes Inclination of the characteristic curve X twice at 13 ° and at 11 °, during the hysteresis torque changes once at 12 °. If the torque increases in the negative direction from 0 kgm, each element works in a similar way to described above; the angle of rotation increases up to 8 ° in the negative range. During this operating phase the slope of the characteristic curve X changes twice at 3 ° and at 5, while the hysteresis torque changes once changes at 4 °.

With this equipment according to the invention, the damping disk, as described in more detail above, and at the hysteresis torque changes, noises can be heard during idling and the high-load operating phase effectively avoid the machine.

The damping disk designed according to the invention has the particular advantage that the maximum torsion angle can be selected to be large and that the intermediate plates 16 are permanent, can be operated.

7 shows an older, not according to the invention trained Radial flange 50 which has a recess 55 through which a stop bolt 53 protrudes. The recess 55 is provided in the outer region of the plate and between two springs 51. In the inner edge area of the recess 55 another recess 57 is formed through which a web bolt 56 protrudes. The recess 55 and the recess 57 extend in the radial direction from the outer edge of the radial flange 50 to a

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Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr. 81, D-8 Munich 81

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Area near the inner edge of this flange 50.

In the formation of the flange according to Figure 7, it is essential to provide a spring seat part 58 of considerable length 1-j ι between the spring 51 and the recess 57 so that the radial flange 5o can permanently support the springs 51 and not from the elastic forces of the Springs 51 is deformed. For this reason, a large distance 13 is required between two adjacent springs 51, which is composed of the sum of the lengths 211 of the two spring seats 58 and the length l2 of the recess 57 in the circumferential direction (I3 = 21 ·] + I2). As a result, the length I4 of the spring 51 and a receiving opening can only be selected to be short, which has the disadvantage that the maximum angle of rotation becomes correspondingly small and torque vibration cannot be effectively absorbed. Since the distance I ₃ between two successive springs 51 must be chosen so long for the formation of the recess 57, only a few, for example three, recesses 57 and thus web bolts 56 can be provided in the disc. Because of this limited number of web bolts 56, for example three, the engagement between the intermediate plates and the radial flange 50 is limited to only three areas to which a correspondingly large partial pressure is applied. The intermediate plates can therefore be deformed, and the desired hysteresis torque characteristic may not be achieved. In contrast to this, in the case of the disc designed according to the invention - as can be seen in FIG the spring seating areas

Dipi.-lng, Otlo wing, Dipl.-Ing. Manfred Säger, patent attorneys, Cosimastr, 81, D-8 Munich 81

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39 is short. In other words, an area 60 is provided between the recess 33 and the opening 31 for the radial connection between the two spring seat areas 38 and 39, which area does not have to support the springs. For this reason, the length l _ß in the initial direction of the area 60 can be kept short, so that overall the length I ₅ between two openings 23 and 31 (26) is short. Conversely, the openings 23, 31 and 26 and thus the springs 30, 22 and 21 can be made correspondingly long, whereby the maximum of the torsion angle can be set correspondingly enlarged, so that the absorption of torque vibrations can take effect more effectively. Furthermore, since the web bolts 18 and the recesses 33 do not result in the distance I5 between the openings having to be selected larger, a corresponding number, for example six, web bolts 18 can be provided in the disk, as shown in FIG. In this way, the pressure exerted by the radial flange 3 via the web bolts 18 is distributed over a corresponding number of areas of the intermediate plates 16. As a result, the intermediate plates 16 are protected from deformation and the desired torque-hysteresis characteristic is achieved.

As can be seen in FIG. 4, the strength of the spring seat areas 38 and 39 is not impaired by the cutouts 30, since each cutout 30 is provided for a stop bolt 12 to reach through on the outer edge of the opening 31 and 26, respectively achieves that the distance I ₅ can be selected to be short and the maximum torsion angle large.

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Dipl.-Ing, Otto Flügel, Dipl.-Ing, Manfred Siigor, Patcntanwiiltc, Cosimastr. 81, D-8 Munich 81

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In another embodiment of the invention, two pairs of web bolts 18 can each be in the two side areas are provided by two openings in the radial flange 3, which are provided diametrically in the disc. Even each web bolt 18 could only be arranged next to one of the side edges of each corresponding opening be. It can also be made such spring arrangements that lead to the inclination of the Characteristic curve X changes only once. Finally, the outer edge regions 32 which can be seen from FIG Limit recesses 30 radially outward, can be omitted. Instead of those arranged distributed in the circumferential direction Springs 20, 21 or 22 can be pairs of coaxially arranged springs with on the one hand large and on the other hand, small diameter can be provided.

The invention has been described in a certain way down to the last detail on the basis of a preferred exemplary embodiment However, this disclosure of the preferred embodiment is to be understood to mean to understand that certain changes in design details, in the combination and arrangement of parts can be taken without departing from the inventive concept.

Dipl.-Ing. Otto Flügel, Dipl.-Ing. Manfred Säger, Patentanwiilte, Cosimastr, 81, D-8 Munich 81

Summary

A damping washer is described in connection with usable with a disc clutch and a radial hub flange, a pair of annular side plates and a pair of annular intermediate plates, the latter between the side plates and the radial flange are arranged and held together with the help of stud bolts, each in the central area the side edges of openings are used in the radial flange, which are used to accommodate springs. the The spacing of the respective web bolt from the side edge of the associated recess defines a torsion angle for a first hysteresis torque. The two side plates are through in radially outer areas Stop bolts connected, each of which reach through assigned recesses, which in the radially outer edge region of the flange are provided, the distance between each stop bolt and the side edges of the associated recess define the maximum possible angle of rotation. Due to the special spatial arrangements the recesses or recesses and the bolts passing through them can have a large maximum torsion angle and achieve permanent operation of the intermediate plates.

Claims (5)

Expectations 1. Damping washer for torque transmission between a driving and a driven shaft, especially in connection with a coupling, marked by a disc plate (3), by a pair connected to one another by means of web bolts (18) Intermediate plates (16) which are arranged coaxially to the disc plate (3) so as to receive them between them and Attack via a friction zone (15) of lower frictional resistance on the disk plate (3), by means of a pair Stop bolts (12) of interconnected side plates (5,6) which are coaxial with the other plates (3,16) these are arranged so as to accommodate them and act on the intermediate plates (16) via a friction zone (17) of higher frictional resistance, through in the disc plate (3) and the side plates (5,6) provided openings (23,24,25; 26,27,28) which in the direction ·! aligned parallel to the plate axis and in which the respective parallel openings penetrate and thus the disk plate with the side plates connecting springs (20,21,22) are used, which are attached in the circumferential direction of the plates directed opening edge regions (38,39) support, wherein between the opening edge regions (38,39) of the openings (23) of the disk plate (3) recesses (33) extending in the circumferential direction are formed, each of which has one of the web bolts (18) It> 1 I 1 I. t I I f ι I I I Il 1 · · It ti ti ti Ik Dipl.-lng. Otto Flügel, Dipl.-Ing, Manfred Siiyer, patent attorneys, Cosimastr, 81, D-8 Munich 81 ^{which has a distance (L2, L 1} 2) from the edge (42, 42) of the associated recess pointing in the circumferential direction, which corresponds to a torsion angle for a first hysteresis torque, and wherein in the edge region of the disk plate (3) recesses (30 ) are provided, each of which receives one of the stop bolts (12) which has distances (L1, L'1) from the edges (41, 41 ') of the respective associated recess which point in the circumferential direction and which correspond to the greatest torsion angle. 2. damping disc according to claim 1, characterized in that that the disc plate is designed as a radial flange (3) of a hub (1) which is keyed onto the driven shaft. 3. Damping disc according to claim 1 or 2, characterized in that some of the springs (20, 21) of the side edges (42.42 ", - 45.45 ') of the openings (23.26 ) are spaced apart in the flange (3) by distances (L3, L'3; L4, L ^I 4) which correspond to a torsion angle which is smaller than the maximum torsion angle. 4. damping disc according to one of the preceding claims, characterized in that that six springs '20, 21,22) are provided and six web bolts (18) are arranged at both ends of three springs (20) are. 5. damping disc according to one of the preceding claims, characterized in that the recesses (30) as a radial continuation of openings (26,31) for receiving springs (21,22) are formed in the disc plate (3).