JPS60211127A - Torsional damper - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a torsional damping device, particularly for a clutch plate in a motor vehicle, comprising two components arranged to rotate with respect to each other within a defined range of relative angular movement. one coaxial member comprising a hub flange, the other coaxial member comprising two guide rings, one on each side of the hub flange; Resilient means are disposed circumferentially between the members, said hub flange and each said guide ring are provided with openings adapted to receive said resilient means, and friction means are provided between said coaxial members. a torsional damping device arranged axially, said friction means consisting of a pressure ring inserted between said hub 7 flange and a guide ring of @i, said pressure ring being provided with an annular friction surface on each side thereof; Regarding.

Torsional damping devices of this type are usually integrated into the clutch plates, especially clutch plates of motor vehicles.

In the early versions of conventional torsional damping devices, the hub flange was combined with a hub that was constrained to rotate with the driven shaft (e.g., the main shaft of an automobile gear box), while a plurality of guides One of the rings houses a facing stationary carrier, which is adapted to be coupled to the drive shaft of the motor vehicle upon engagement of the clutch. In another version of the conventional torsional damping device, the hub 7 rank has a facing carrier fixed thereto, while a plurality of guide rings are associated with the hub.

An effect of the various friction means operating between two coaxial parts of the torsional damping device is that hysteresis effects are introduced into the operating characteristics of the torsional damping device. That is, for a given value of relative angular movement between coaxial members of a torsional damping device, the value of the torque transmitted from one of the coaxial members to the other as that relative angular displacement is increasing; If the target angular displacement is decreasing, a difference in torque value will be introduced between the outer torque value and the target angular displacement.

In addition, the various friction means described above have the effect that the friction obtained between the coaxial members of the torsional damping device during torque transmission is such that the friction increases from the rest position of the torsional damping device (the position corresponding to zero torque transmission). It also has the effect of being directly proportional to displacement.

However, although conventional torsional damping devices have the above-mentioned advantages, the various friction means significantly increase the overall dimensions, especially the axial dimensions, of the torsional damping device, and also the desirable friction values. The problem is that accuracy cannot be obtained.

It is an object of the present invention to provide a torsional damping device of the type described above, in particular for a clutch plate in a motor vehicle, which is particularly efficient in operation and has desirable properties both in the forward and reverse directions of torque. obtained,
Moreover, it is an object of the invention to provide a torsional damping device whose overall dimensions, particularly in the axial direction, can be reduced and a simple and robust construction is obtained.

Another object of the invention is a torsional damping device of the type described above, which has a very simple construction and which reduces the magnitude of the friction depending on the relative angular position of its two coaxial members. It is an object of the present invention to provide a torsional damping device that can be changed with high precision.

According to the invention, there is provided a torsional damping device comprising two coaxial members arranged to rotate with respect to each other within a defined range of relative angular movement, one of said coaxial members being arranged to rotate with respect to each other within a defined range of relative angular movement. the other coaxial member comprising two guide rings, one on each side of the hub flange, with resilient means disposed circumferentially between the coaxial members, Each guide ring is provided with an opening adapted to accommodate the elastic means, and a friction means is arranged axially between the coaxial members, and the friction means is arranged between the first flange and the first flange. a pressure ring inserted between a guide ring, said pressure ring being provided with a plurality of lugs each having an annular friction surface on each side thereof and substantially coplanar with said pressure ring; lugs are adapted to effect a resilient clamping action of said pressure ring on one of said coaxial members, and each said lug has a recessed base on one of said coaxial members. and an end applied to the pressure ring in a contact area outside the periphery of the friction surface of the pressure ring.

With such an arrangement, the overall dimensions, especially the axial dimensions, of the torsional damping device are reduced.

It is not necessary to have double curvature of the lugs, and the desired precise control of the friction force depends on the thickness of the pressure ring. To facilitate adjustment of the frictional force, the thickness of the pressure ring may be varied and holes may be formed in the lugs.

According to another feature of the invention, the pressure ring comprises three types of circumferential flanges arranged in circumferential rows and in a regular order, one of the three types of circumferential flanges being connected to the pressure ring. a contact flange being coplanar and adapted to contact the end of the lug, and another of the three peripheral flanges being substantially coplanar with the pressure ring and attached to the lug; and a centering flange for centering the pressure ring relative to one coaxial member, and the remaining one of the three circumferential flanges is bent toward the hub flange and attached to the lug. The drive flange is adapted to engage with a clearance a notch in the other coaxial member.

The contact flange of the pressure ring is preferably slightly bent at its ends, which improves bearing engagement conditions with the lugs.

According to such a configuration, the pressure ring is centered with respect to one of the coaxial members attached to the lug, and the pressure ring is in frictional engagement with the lug attached to the coaxial member. A contact flange will be provided in the condition.

Also, by means of a drive flange cooperating with a notch provided in the other coaxial member, the pressure ring is brought into frictional cooperation with one coaxial member attached to the lug, and the drive flange is then brought into frictional cooperation with the one coaxial member attached to the lug. will be effectively driven by the other coaxial member.

In reality, the clearance formed between the bending flange of the pressure ring and the notch is larger during reverse operation than during forward operation, so that the pressure ring Therefore, the lug is not placed in JP frictional engagement with one of the coaxial members taken by τ1, and a predetermined ratio is then obtained for the relative angular movement between the two coaxial members of the torsional damping device. It will be done.

Preferably, the friction means further comprises a first friction ring inserted between the pressure ring and the hub flange, and a second friction ring inserted between the hub flange and the second guide ring. include. This second friction ring is advantageously constrained to rotate together with the second guide ring, while an elastic ring is inserted between the second friction ring and the second guide ring.

According to a further feature of the invention, in one embodiment of the invention, when the torsion damping device is applied to the clutch plate, the facing carrier is attached to the first guide ring and the lug is attached to the facing carrier. It will be done. In another embodiment, the facing carrier is attached to the hub 7 flange and the puffer is attached to the facing carrier.

According to a further feature of the invention, when the torsional damping device is applied to a clutch plate, the flange is combined with the hub, in which case the flange and the hub are mounted with a small circumferential clearance and are elastically The means act against the circumferential clearance, thirteen friction rings are inserted between the second guide ring and the hub, and an elastic ring acts against the opening of the third friction ring and the second guide ring. inserted into.

According to a further feature of the invention, the end of each lug is shaped in such a way that the elastic clamping action described above is obtained as a force that can vary depending on the relative angular position of the coaxial members. According to a further feature of the invention, the ends of each lug are circumferentially elongated.

According to a further feature of the invention, each lug has a generally curved shape characterized by an open practical radial arm at its base and at its end.

In one embodiment of the invention, each puffer end includes a relatively rigid portion adjacent to the aforementioned radial arm and at least one relatively flexible lateral portion.

In another embodiment, the ends of the lugs are beveled.

Other objects and advantages of the present invention will become apparent from the following description with reference to the accompanying drawings. Is the invention novel? iy-m is detailed in the claims.

Figure tIS1 is a partially cutaway elevational view showing an automobile clutch plate incorporating the torsion damping device according to the present invention, and Figure 2 is a cross-sectional view of the clutch plate along the dashed line - ■ in Figure 1. 3 is a partial elevational view of the facing carrier showing both the lugs supported from the facing carrier and the pressure ring partially drawn in dash-dotted lines, and FIG. is a partial elevational view of a pressure ring showing both its contact flange, centering flange and drive 7 run, with the hub flange at one point M4
Figure 5 is a cross-sectional view taken along the line ■-■ in Figure 4, and Figure 6 is a diagram showing the assembly of the hub 7 runno and the hub. FIG. 7 is an enlarged cross-sectional view of the first guide ring, and shows a state in which a slight circumferential clearance therebetween is elastically maintained; FIG. FIG. 7 is a diagram showing the attached planar lug in a state before contacting with the pressure ring; FIG. 8 is a diagram similar to FIG. FIG. 9 is an enlarged view of the clutch plate in combination with the friction means; FIG. 10 shows the lugs supported from the facing carrier and the seven flange of the pressure ring, the lugs supporting the relative angular position of the two coaxial members of the torsional damping device. one of them
11 is a view similar to FIG. 10 showing another position for the relative angular position of the two coaxial members of the torsional damping device; FIG. FIG. 12 is a diagram similar to FIG. 10 or MS11 showing a modified example of the lug, and FIG. 13 is a plan view of FIG. 12.

In the embodiment illustrated by way of example in FIGS. 1 to 9, the torsional damping device, which is designed in particular for a clutch plate of a motor vehicle, comprises two coaxial members A and B. In the embodiment shown by way of example in FIGS. These coaxial members A and B are arranged to rotate with respect to each other within a defined range of relative angular movement.

The coaxial member A consists of a hub flange 10, which is combined with a hub 11. The hub 11 is attached to the main shaft of an automobile gear box and is adapted to rotate therewith.

The coaxial member B consists of two guide rings 12 and 13, one each on each side of the hub flange 10. Guide ring 12
and 13 are attached to each other by spacers 14,
The spacers 14 pass through a circumferential/jaw 15 provided on the hub flange 10. Between the coaxial members A and B elastic means 16 and 17 are arranged circumferentially. These elastic means are constructed as a rigid extraneous spring 16 and a less rigid spring 17. The stiff springs 16 are accommodated in openings 18 formed in the guide rings 12 and 13 and in the hub 7 rungs 10 and which have a relatively small circumferential extent. In addition, the spring 17 with small rigidity is connected to the opening 19.
These openings 19 are formed in the guide rings 12 and 13 and in the hub flange 10 and have a relatively large circumferential extent. In practice, the opening 18 formed in the hub flange 10 is
3, whereas all of the openings 19 are of the same size.

The various openings 18 and 19 are arranged circumferentially in rows at substantially the same mean radius. The openings 18 with a relatively small extent and the openings 19 with a relatively large extent are arranged alternately.

Furthermore, a friction means is arranged in the axial direction between the coaxial members A and B.

Are these friction means hub 7? The pressure ring 20 is inserted between the guide ring 10 and the first guide ring 12 . This pressure ring 20 has an annular friction surface 2 on each side.
1 and 22 (FIG. 9). The annular friction surface 21 cooperates with the hub flange 10 via a friction ring 23, and the annular friction surface 22 cooperates directly with the guide ring 12 of @1.

Lugs 24 are punched in order to elastically clamp the pressure ring 20 against the first guide ring 12 .

The lugs 24 are preferably substantially coplanar with the pressure ring 20 and have a base 25 .
is attached to a coaxial member B consisting of guide rings 12 and 13. More specifically, each lug 24
5, the base 25 of which is attached to a carrier 26 having a friction surface 27 (FIG. 2). A carrier 26 with a friction surface 27 is attached to the first guide ring 1 by means of a rivet 28.
2 and is adapted to be connected to the drive shaft of a motor vehicle, for example by being clamped between two plates of the clutch when the clutch is engaged.

In this way, each lug 24 will be supported via its base 25 from a carrier 26 with a friction surface 27. Each lug 24 also includes an end 29 .
is against the pressure ring 20 in its contact area 30 (FIG. 8).
, the contact area 30 is applied to the friction surface 2 of the pressure ring 20
1 and 22. At least one hole 45 is formed in the lug 24 . By appropriately selecting the size of this hole 45, it is possible to adjust the rigidity of the pufferfish 24 and to adjust the frictional force at the location indicated by reference numeral 22.

With the arrangement described above, it is possible to significantly reduce the overall dimensions, especially the axial dimensions, of the torsional damping device.

As shown in FIG. 7, the end 29 of each lug 24 is substantially coplanar with the pressure ring 20 before contacting it. The pressure ring 20 is provided with flanges 31 as described below, these flanges 31 are provided with an end 46, which end 46 is connected to the guide ring 1 of tISi.
It is bent toward the recessed part 47 provided in 2. Such a recess 47 is provided to accommodate the springs 16 and 17.

When the end 29 of the lug 24 is brought into contacting engagement with the pressure ring 20, the end 29 is brought into contact with the flange 31 of the pressure ring 20.
It will come into contact with the deflected end 46 over a large 1J area (FIG. 8). It will be clear that such an arrangement results in a reduction in overall axial dimensions.

As shown in more detail in FIGS. 4 and 5, the pressure ring 20 is provided with three types of circumferential flanges 31, 32 and 33 in circumferential rows, these circumferential 7 runs repeating. are distributed in order a. The peripheral flange 31 or contact flange 31 is substantially flush with the pressure ring 20 and is adapted to contact the end 29 of the lug 24. Circumference 7 runs: j32, i.e. the centering flange 32 is made flush with the pressure ring 20 and centers the pressure ring 20 against the carrier 26 with the friction surface 27 at a point indicated by reference numeral 32A (MS3 figure). It is supposed to be done. The peripheral 7 flange 33 or drive flange 33 (FIGS. 4 and 5) is bent toward the hub 7 rank 10 and is engaged with a clearance in a notch 34 provided in the hub flange 10.

The friction means of the torsional damping device also include a friction ring 23 inserted between the pressure ring 20 and the hub flange 10 (FIG. 9). Friction ring 23 is pressure ring 20
It may or may not be attached to the

The hub flange 10 and the second guide ring 13 also include:
A second friction ring 35 is provided. This second friction ring 35 is attached to the second guide ring 13 and is restrained in rotation together with the second guide ring 13, for example by pegs 36, which pegs 36 are attached to the second guide ring 35. It is attached and engaged with the hole 37 provided in the guide ring 13 of wS2.

An elastic ring 38 is inserted between the second friction ring 35 and the second guide ring 13, and this elastic ring 38 provides an elastic clamping action in the axial direction between the hub flange 10 and the various rings. It will be done.

As shown in more detail in FIG.
and the hub 11 is mounted with a slight circumferential clearance between the respective teeth 39 and 40, which clearance is maintained resiliently by a spring 41.

The torsional damping device further includes a third friction ring 42 (ninth
Figure). An elastic ring 43 is inserted between the third friction ring 42 and the second guide ring 13.

The combination of components 39, 40, 41, 42 and 43 is designed to eliminate the so-called clead point noise when the torque is near the zero value.

As the torque increases, the teeth 39 and 40 come into contact and the component then moves as if friction at the point indicated by reference numeral 42 acts between the second guide ring 13 and the hub flange 10. All of these will start. Added to such friction is the friction associated with friction ring 35 and friction ring 23.

When torque is transmitted in the opposite direction, the pressure ring 20
The clearance between the drive flange 33 of the hub flange 10 and the edge 34 of the hub flange 10 is such that the pressure ring 20
It would be too large to accompany it with 0. On the other hand, when torque is transmitted in the forward direction, the pressure ring 2
Drive flange 33 of 0 and edge 34 of hub flange 10
The clearance between the coaxial members A and 8 will be taken up after the relative angular movement between the coaxial members A and 8 has taken place within a predetermined range, and the pressure ring 20 will be entrained by the hub flange 10, which is indicated by reference numeral 22. An auxiliary friction is introduced between the pressure ring 20 and the guide ring 12 at the points indicated with 42.35 and 23, which friction is added to the friction at the points indicated with reference numbers 42.35 and 23. Spring 16 and /*
17 is such that contact with the centering flange 32 returns the device to the neutral position.

The above-mentioned torsional damping device, in particular a torsional damping device for a clutch plate of a motor vehicle, provides a large reduction in overall dimensions, especially in the axial direction, and its structure is simple and robust. It is clear that consideration has been given to excellent operability in the forward and reverse directions.

As is clear from FIGS. 10 and 11,
Regarding the shape of the end 29 of each lug 24, the pressure ring 2
0 relative to the first guide ring 20, this force varies depending on the relative angular position of the coaxial members A and B. One is illustrated in FIG.
Other relative angular positions are shown in the figure).

More particularly, the end 29 is circumferentially elongated and the lug 24 is of a generally curved shape characterized by a substantial radial arm 50 between its base 25 and its end 29. (Figures 3 and 10). Such end 29 includes a relatively rigid portion 5 adjacent arm 50.
1 (FIG. 10) and at least one laterally free member 52 which is relatively flexible.

Therefore, the elastic clamping force in the axial direction obtained when the rigid portion 51 (FIG. 11) is in contact with the contact flange 31 of the pressure ring 20 is This is greater than the axial elastic clamping force obtained when it is the flexible portion 52 (FIG. 10) that is in contact with 31. Add at least one hole 45 (FIG. 3) to the lug 2 to improve flexibility.
4 is advantageous. Reference number 22 (Figure 9)
The auxiliary friction at the point indicated by is controlled by an elastic clamping force, which is the coaxial member A
and the end 29 of the lug 24 depending on the relative angular position of B.
It can change depending on the shape of. The flexible portion 52 of the end 29 contacts the pressure ring 20 against a predetermined torque.
1, the clamping force is relatively small, and when the rigid portion 51 of the end 29 of the lug 24 is in contact with the contact flange 31 of the pressure ring 20 against an even more extraordinary torque, the clamping force is relatively small. Its clamping force increases. spring 16
and/or 17 is adapted to return the device to the neutral position by contact with the centering flange 32.

In the alternative embodiment illustrated in FIGS. 12 and 13, the construction is similar to that described above with the following exceptions. The difference is that in this embodiment the end 29 of the lug 24 is formed as a bevel 52, so that the clamping force at the point designated by reference numeral 22 is the same as in the previous embodiment. It is at a point that varies as a function of the relative angular position of shaft members A and B.

The important point to note is that the shape of the end portion 29 of the lug 24 may be made as shown in FIGS. This means that it is okay to do so.

Details of each component described above for explanation of the present invention,
It should be understood that various changes in materials and construction may be made by those skilled in the art without departing from the scope of the invention as claimed.

For example, a guide ring may be attached to a hub and a hub flange that is movable relative to the hub. In this case, the lug 24 is attached to the hub 7 flange, the drive flange being brought into engagement with the guide ring, while the pressure ring 2o is brought into friction with the hub flange. Also, a friction ring may be provided on each side of the pressure ring. It should be noted that the lug 24, of which one of the coaxial members A and B forms part, acts axially on the pressure ring 20 for clamping purposes. In short, it acts not on the coaxial member forming part of it, but on the other coaxial member, i.e., in the case of FIG.

[Brief explanation of the drawing]

FIG. 1 is a partially cutaway elevational view showing an automatic heavy-duty clutch plate incorporating a torsion damping device according to the present invention, and FIG. 2 is a cross-sectional view of the clutch plate taken along the dashed line ■-■ in FIG. and FIG. 3 is a partial elevational view of the facing carrier, showing both the lugs supported from the facing carrier and the pressure ring partially drawn in dash-dotted lines. , FIG. 4 is a partial elevational view of a pressure ring showing the contact, centering and drive flanges of the pressure ring together and with the hub flange drawn in dash-dotted lines; Figure 5 is a cross-sectional view taken along line V-■ of Figure fItJ4, and Figure 6 is a diagram showing the assembly of the hub 7 runno and the hub, where the slight circumferential clearance between them is elastically FIG. 7 is an enlarged cross-sectional view of the first guide ring, in which a planar lug attached to the facing carrier is kept in contact with the pressure ring; FIG. - Figure 8 is a view similar to Figure 7 showing the contact body of the lug to the pressure ring in a future condition, the lug being substantially coplanar with the pressure ring; FIG. 9 is an enlarged view showing the state in which the clutch plate is combined with the friction means, and FIG. 10 is a diagram showing the clutch plate being supported from the facing carrier FIG. 6 shows the lugs and the flange of the pressure ring in one of the relative angular positions of the two coaxial members of the torsional damping device;
11 is a view similar to FIG. 10 showing another position for the relative angular position of the two coaxial members of the torsional damping device; FIG. FIG. 12 is a diagram similar to FIG. 10 or FIG. 11 showing a modified example of the lug, and FIG. 13 is a plan view of FIG. 12. [Explanation of main reference numbers and symbols] A, B... Coaxial member 10... Hub flange 11... Hub 12.13... Guide ring 16.17... Elastic means 18.19. ... Opening 20 ... Pressure ring 21.22 ... Annular friction surface 23 ... Friction ring 24 ... Lug 26 ... Carrier 27 ... Friction surface 29 ... End of lug 31...Contact 7 runno 32...Centering 7 runno 33...Drive flange 35...Second friction ring 38...Elastic ring 39...Hub 7 Runno teeth 40...Hub Tooth portion 42...Third friction ring 43...Elastic ring agent Takeshi, patent attorney 1) Masahiko, patent attorney Masahiro Takiguchi, patent attorney Hiroshi Nakazato - F/6.9 -N-1N- ((

Claims (21)

[Claims] (1) A torsional damping device comprising two coaxial members arranged to rotate with respect to each other within a cage with a defined relative angular movement, one of the coaxial members comprising a hub 7 flange. , the other coaxial member comprising two guide rings, one on each side of said hub flange, with elastic means disposed circumferentially between said coaxial members, said hub 7 runno and said hub 7 runno. Each guide ring is provided with an opening adapted to receive said resilient means, and friction means are axially disposed between said coaxial members, said friction means being connected to said hub flange and said first guide. a pressure ring inserted between the pressure ring, the pressure ring being provided with a plurality of lugs each having an annular friction surface on each side thereof and substantially coplanar with the pressure ring; producing a resilient clamping action of the pressure ring on one of the coaxial members;
and each said lug comprises a base attached to one of said coaxial members and an end applied against said pressure ring in a contact area outside the periphery of the friction surface of said pressure ring. A torsional damping device characterized by: 2. The torsional damping device of claim 1, wherein the lugs are adapted to resiliently clamp the pressure ring against the first guide ring. (3) said pressure ring has a circumferential contact flange, said circumferential contact flange being substantially coplanar with said pressure ring and adapted to contact an end of said lug; A torsional damping device according to claim 1. 4. A torsional damping device according to claim 3, characterized in that said circumferential contacts (7) have bent ends to obtain a large contact area with the ends of said lugs. (5) the pressure ring is provided with a centering peripheral flange, the peripheral flange is flush with the pressure ring, and the pressure ring is in the same plane as the guide ring of the coaxial member; 2. Torsional damping device according to claim 1, characterized in that it is adapted to perform centering. (6) the pressure ring includes a peripheral flange for driving;
A torsional damping device according to claim 1, characterized in that the circumferential flange is bent towards the hub flange and engaged with a clearance on/on the hub flange. (7) the pressure ring comprises three circumferential flanges arranged circumferentially in rows and in a regular order, one of the three circumferential flanges being substantially coplanar with the pressure ring; a coaxial contact flange adapted to contact the ends of the lugs, the other of the three circumferential flanges being coplanar with the pressure ring and configured as the guide ring; a centering flange adapted to center the pressure ring relative to the member, the remaining one of the three types of peripheral flanges being bent toward the hub flange and provided on the hub flange; 2. A torsional damping device as claimed in claim 1, characterized in that it comprises a drive flange adapted to engage with a clearance. (8) The torsional damping device of claim 1, wherein the friction means further includes a first friction ring inserted between the pressure ring and the hub flange. (9) Claim 1, wherein the friction means includes a second friction ring inserted between the hub flange and the second guide ring; Device. (10) The torsional damping device according to claim 9, wherein the second friction ring is restrained to rotate together with the second guide ring. (11) The torsional damping device according to claim 9, wherein an elastic ring is inserted between the friction ring of the ttS2 and the second guide ring. (12) The torsional damping device according to claim 1, wherein a facing carrier is attached to the first guide ring, and the lug is attached to the facing carrier. (13) The hub 7 flange is assembled into a hub, the hub 7 flange and the hub are attached with a slight circumferential clearance, and an elastic means is provided that acts against the circumferential clearance, and the second a third friction ring is inserted between the guide ring and the hub;
Claim f:!, characterized in that an elastic ring is inserted between the third friction ring and the second guide ring. Torsional damping device according to item S'1. (14) The ends of each puffer are shaped so that the elastic clamping action is obtained as a force that varies depending on the relative angular position of the coaxial members. Torsional damping device according to clause 1. (15) The torsional damping device according to claim 14, wherein an end portion of each of the lugs extends in a circumferential direction. 16. The twist of claim 14, wherein each puffer has a generally curved shape characterized by an open, substantially radial arm between the base and the end. damping device. 17. The end of each lug includes a relatively rigid portion adjacent the arm and at least one lateral portion that is relatively flexible.
Torsional damping device as described in Section. − (18) The torsion damping device according to claim 14, wherein the end portion of each of the lugs has an inclined shape. 19. The torsional damping device of claim 14, wherein an end of each lug cooperates with a peripheral flange on the pressure ring. (20) The pressure ring further includes a drive flange, and the drive 77 flange is bent toward the hub 77 and engages with a clearance provided on the hub 7 run. A torsional damping device according to claim 14. (21) The facing carrier is attached to the first guide ring.
The torsion damping device according to claim ttS14, characterized in that the puffer is attached to the facing carrier.