JPS6117739A - Damper with split hubs - Google Patents

Abstract

PURPOSE:To make a damper with stable performance and good durability at low cost and in a simple configuration by fitting a rubber member between a main hub and a sub-hub, and thereby coupling two hubs with resilience in the circumferential direction of hubs. CONSTITUTION:Inner cogged spring 25 of main hub 11 is made with a certain clearance to the outer cogged spline 12a in the rotational direction. Inner cogged spline 31 of sub-hub 30 meshes with said outer cogged spline 12a with a minor clearance between so as to allow sliding in the axial direction, and in this position a rubber member 41 is fitted between the two hubs 11, 30 so as to accomplish coupling of two hubs with resilience in the circumferential direction of hubs. This eliminates generation of unstable friction to ensure stabilized performance, and there no unreasonable stress will be applied to lead to enhancement of durability.

Description

Detailed Description of the Invention (Industrial Application Field) The present invention provides a hub-split damper which has a main hub and a sub-hub, and is adapted to absorb torsional vibration by elastically connecting the two. Regarding equipment.

(Prior art) The WJ structure is effective in preventing the occurrence of gear tapping noise in the transmission transmission due to fluctuations in engine rotation when the crankshaft is connected in the engine idle state.
A configuration in which the hub on the input side is divided into two and a C-shaped spring is connected between the two cylindrical hubs is already known (for example, Utility Model Publication No. 56-988).

However, in this configuration, the C-shaped spring is expanded and contracted in the direction in which its diameter expands and contracts, so that unreasonable stress is applied to the C-shaped spring.

In particular, if a load is applied in the direction in which the diameter expands, the problem of breakage is likely to occur. Moreover, there is a problem in that relatively strong and unstable metal-to-metal friction occurs between the end surfaces of both hubs and the C-shaped spring, resulting in unstable operation. In the above structure, there is no member that actively generates hysteresis torque, and the C-shaped spring is simply compressed, resulting in a substantial vibration energy of 1! - is hardly consumed. Furthermore, in the above conventional configuration, it is necessary to specially prepare a pin for attaching the C-shaped spring and a case for connecting the two hubs, which complicates the groove construction and increases the number of parts. Higher costs are unavoidable.

(Objective of the Invention) The present invention provides a hub split type damper device that has a main hub and 5 sub-hubs and absorbs torsional vibration by elastically connecting the two, which has a simple structure that does not increase costs. The purpose is to provide a high durability, stable operation, and stable hysteresis torque.

(Structure of the Invention) The present invention is characterized in that the internal spline of the cylindrical main hub on the input side is fitted to the external spline of the output shaft through a predetermined gap provided in advance in the rotational direction, and the cylindrical sub-hub The main hub and sub-hub are elastically connected in the circumferential direction of the hub by fitting the internal splines of the main hub with relatively no gaps in the rotational direction and installing and fixing a rubber-like member between the main hub and the sub-hub. This is a puff division type damper device characterized by the following.

(Example) Fig. 1 (arrow ``points forward'') is a partial cross-sectional view of a case where a damper device according to the present invention is adopted for an automobile clutch disc.A main hub 11 is an output shaft 12 (for example, a drive shaft of a transmission). The hub 7 is spline-fitted to be slidable in the axial direction, and is provided with an annular hub flange 13 on the outer peripheral surface.An annular friction member 14, 15 is provided on the inner periphery of both front and rear sides of the hub 7 flange 13. (sriction washers, cone springs, etc.) are placed,
Both I! ! ! Hub flange 13 with friction members 14 and 15 in between
A pair of disc-shaped lead plates 16 are installed on both the front and rear sides of the
．． 17 (clutch plate and retaining plate)
The main hub 1 is rotatable in a position perpendicular to the center line O-0.
1 is supported. The outer peripheries of both side plates 16.17 are integrally connected by a stop pin 18 parallel to the center line O-O, and the hub flange 13 and both side plates 16.17 have the same number of window holes 19.20. 21(
(Only one of each is shown in the figure) is assembled in plural numbers.

Each set of three window holes 19.20.21 faces parallel to the center line O-O of the output shaft 12, and each set of window holes 19.2
0.21 is fitted with a coil spring 22 (1 to - John spring). Each coil spring 22 extends in the circumferential direction of the clutch disc, and the hub flange 13 and both side plates 1617 are elastically connected by the coil spring 22. side plate 1
A plurality of cushioning plates 23 are fixed to the outer peripheral end of the cushioning plates 7 so as to occupy substantially the same plane, and annular facings 24 are attached to both sides of the cushioning plates 23. Further, the facing 24 is sandwiched between a flywheel and a pressure plate on the engine drive side (not shown).

As shown in FIG. 2, an internal spline 25 is formed on the inner circumference of the main hub 11.
meshes with the external spline 12a of the output shaft 12.

In addition, a cylindrical nub hub 30 is rotatably fitted in front of the main hub 11 at a distance.
The motor also has an internal spline 31 on the inner peripheral side, and the internal spline 31 meshes with the external spline 12a of the output shaft 12. As shown in FIG. 3, the internal spline 25 of the main hub 11 has clearances a and b in the rotational direction with respect to the external spline 12a, and a predetermined play is provided in the rotational direction. Note that the arrow x1 indicates the positive rotation direction during torque transmission, and the gap a is set to be wider than the gap in the disk free state. Further, as shown in FIG. 4, the internal spline 31 of the sub-hub 30 meshes with the external spline 12a through only a small gap of 1- to allow sliding in the axial direction.

As shown in FIG. 2, the main hub 11 and the sub-hub 30
The outer peripheral surfaces of the main hub 11 and the sub-hub 30 are covered with a generally cylindrical torsion rubber 41 from the outer peripheral side. The torsion rubber 41 is made of a rubber-like elastic material, and the portion that contacts the outer circumferential surface of the main hub 11, the outer circumferential surface of the sub-hub 30, and the front end surface is fixed by a baking groove.

Next, the operation will be explained. When the 7 acing 24 in FIG. 1 is pressed against the flywheel by a pressure plate (not shown), torque is applied from the flywheel to the facing 24, the cushioning plate 23, and the side plate 1.
6.17, it is transmitted to the main hub 11 via the coil spring 22 and the hub flange 13. Here, since the torsional rigidity of the coil spring 22 and the torsional rigidity of the rubber 1!11 in Figure 2 is set low, the coil spring 22 (Figure 1) is first compressed. The torsion rubber 41 is twisted, and twisting occurs between the main hub 11 and the sub-bald part 30.

That is, in FIG. 3, if the main hub 11 is twisted relative to the output shaft 12 in the direction of arrow x1, for example, the main hub 11 is twisted against the output shaft 12 until the gap a disappears and the internal spline 25 comes into contact with the external spline 12a. It spins idly against the opponent. On the other hand, as shown in Figure 4, only a small gap is provided between the sub-hub 30 and the output shaft 12 for sliding movement, and while the main hub 11 (Figure 3) is spinning idle, both main hubs 11 , twisting occurs in the rotational direction between the nub hub 30, and the torsion shield 41 is twisted.

When the main hub 11 rotates further after the idle period,
Internal spline 25 of main hub 11 It output shaft 12
Since the main hub 11 and the rib hub 30 are brought into contact with the external spline 12a of the rib hub 30, twisting between the main hub 11 and the rib hub 30 will no longer occur. Therefore, in the next step, the first
The coil spring 22 shown is compressed and both side plays 1-16.17 are twisted relative to the hub flange 13. This twisting causes friction on the surface of the friction member 14.15.

When the stop bin 18 comes into contact with the end face of the notch 13a formed in the hub flange 13, both the one-noid plates 1d and 17 and the hub flange 13I are integrated, and the torque from the side plates 16 and 17 is reduced. stop bin 18
, the hub 7 flange 13, and the main hub 11, and are directly transmitted to the output shaft 12.

Note that the same operation occurs when torsional torque is applied in the opposite x1 direction. However, at this time, the operation is performed so that the gap shown in FIG. 3 disappears. Therefore, since the gap is set narrower than the gap a in the disk free state, the maximum torsion angle between the main hub 11 and the sub-hub 30 is smaller than that when torsion torque is applied in the x1 direction.

Here, if the torsion between the side plate 16.17 and the output shaft 12 is expressed by the torsional angle θ, and the torsional torque in the ×1 direction applied to the side plate 16.17 is expressed by Tq, the above operation is as shown in Fig. 5. It is expressed like a graph φ (reverse × 1 direction is omitted). The idle rotation angle of the main hub 11 is 0 to θ1, and the angle during which the coil spring 22 (FIG. 1) is compressed is θ1 to θ2. As is clear from FIG. 5, a progressive relationship is obtained between the angle 0 and θ1 due to the twisting of the torsion rubber 41 made of a rubber-like elastic material, and from the angle θ1 to the next stage (compression stroke of the coil spring 22). The transition will be smooth. Also angle 0~θ
The hysteria between cis1 and h1 is generated by the internal ff# house of the torsion rubber 41 itself, and the angle *e1
The hysteresis torque h2 between ~θ2 is the friction member 14.1
5 (Figure 2).

Next, a manufacturing process for attaching the torsion rubber 41 to the main hub 11 and the rib hub 30 will be explained. First, the main hub 11 and the sub-hub 30 are held at predetermined relative positions using a ring-shaped jig (not shown) similar to the output shaft 12 and having teeth on the outer peripheral surface. At this time θ, in a state where the main hub 11 and the sub-hub 30 are fitted onto the protruding horn shaft 12 in the disc free state, a predetermined gap a, b of a predetermined size is created between the spline 25 of the main hub 11 and the sub-fin 12a (Fig. 3). The main hub 11 is held in a slightly twisted position with respect to the sub-hub 30 so that the main hub 11 is formed.

While holding the main hub 11 and the sub-hub 30 with a jig, the outer peripheral surfaces of the main hub 11 and the sub-hub 30 and the front end surface of the sub-hub 30 are roughened, and the surfaces are further degreased. Next, unvulcanized rubber is applied to the outer peripheral surfaces of the main hub 11 and sub-hub 30 to form a roughly cylindrical shape, and also to cover the front end surface of the sub-hub 30.
ζ Pour into the sea urchin.

Subsequently, vulcanization and baking are performed to firmly fix the rubber to the surfaces of the main hub 11 and the sub-hub 30.

As a result, a torsion rubber 41 is formed, and the torsion rubber 41 elastically connects the main hub 11 and the main hub 30 with the main hub 11 and the main hub 30 disposed at a predetermined relative position.

According to this process, the relative positional relationship between the two hubs 11' and 30 in the disk free state can be made much higher in M degree than in the past.

(Effect of the invention) The internal spline 25 of the cylindrical main hub 11 on the input side is fitted to the external spline 12a of the output shaft 12 through predetermined gaps a and b provided in advance in the rotational direction, and the cylindrical By fitting the internal splines 31 of the shaped sub-hub 30 with relatively no gaps in the rotational direction, and installing and fixing a rubber-like member (for example, torsion rubber 41) between the main hub 11 and the sub-hub 30, the main hub 11 and the sub-hub 30 are elastically connected in the circumferential direction of the hub; ゛(a) Unreasonable stress is not applied as in the case of the conventional C-shaped spring, which prevents breakage of the spring. Defects will no longer occur and durability will be improved.

(b) Since a rubber-like member is installed and fixed between the main hub 11 and the j-hub 30, unstable friction between metals does not occur as in conventional configurations, and the structure is stable. The operation is turned blue.

(C) Internal J! of the rubber-like member! ! 8. Since hysteresis torque is generated by rubbing, the vibration absorption ability is increased.

(d) By using the rubber-like member, it is possible to obtain a progressive six-angle-torsion torque characteristic that is ideal for absorbing torque vibrations.

(C) Since the two halves of the hub are connected by a rubber-like member, the structure is extremely simple and costs can be significantly reduced.

(Another Embodiment) (a) The fixation of the torsion rubber 41 to the main hub 11 and the sub-hub 30 is not limited to the 7'-old method, but may also be performed by, for example, adhesion, band fastening, serration fitting, etc. can.

(b) As shown in FIG. 6, the torsion rubber 41 may be formed into a bellows shape. In this case, the central part of the rubber 41 may be formed in advance into a bellows shape, and both ends of the inner peripheral surface may be fixed to the main hub 11 and the sub-hub 30 by burning or adhesive.

(C) It is also possible to improve the fixing strength of the torsion rubber 41 by forming recesses and grooves in advance on the outer peripheral surfaces of the main hub 11 and the leaf hub 30.

(d) Instead of the torsion rubber 41, a cylindrical torsion rubber 42 made of a rubber-like elastic material is installed and fixed concentrically between the opposing end surfaces of the main hub 11 and the sub-hub 30 as shown in FIG. Good too.

In this case, there is an advantage that the diameter of the hub portion can be made smaller than that of the torsion rubber 41 described above.

(e) Instead of the cylindrical torsion rubber 4'2, the 8th
As shown in the figure, a plurality of torsion bars 43 made of a rubber-like elastic material are installed and fixed between opposing end surfaces of the main hub 11 and the sub-hub 30. Each torsion rubber 43
are arranged at balanced positions, that is, at equal intervals in the circumference lJ.

(f) The hub flange 13, side plates 16, 17, etc. are not essential members; for example, if the input side member is directly connected to the main hub 11, a damper joint with an extremely small radius can be obtained.

(0) The present invention can also be applied to a type of damper disk having a nub plate between the plate 16, 17 and the flange 13.

(h) The gaps εl and b are shown in the example where a>b, but they can be arbitrarily determined depending on the characteristics of the vehicle to be employed.

[BRIEF DESCRIPTION OF THE DRAWINGS] Fig. 1 is a vertical cross-sectional partial view of the case where the present invention is applied to a clutch disc, Fig. 2 is an enlarged longitudinal cross-sectional partial view of the hub portion of Fig. 1, Fig. 3, and Fig. 4. are a partial cross-sectional view taken along the line ■-■ in FIG. 2, and a partial partial view taken along a TV-IV cross-section in FIG. 2, respectively. FIG. 5 is a graph showing the relationship between torsion angle and torsional torque, and FIGS. 6 and 7 are longitudinal sections of different embodiments. FIG. 8 is a longitudinal partial front view of yet another embodiment. 11... Main hub, 12
...Output shaft, 12a...External spline, 25...
・Internal tooth spline, 30... Rib hub, 31... Internal tooth spline, 41.42, /13... Torsion rubber (an example of rubber-like part removal) Patent applicant Jinkin Seisakusho Co., Ltd. Procedure amendment ( (Voluntary) September 28, 1982

Claims (1)

[Claims] The internal spline of the cylindrical main hub on the input side is fitted to the external spline of the output shaft through a predetermined gap in the rotational direction, and the internal spline of the cylindrical sub-hub is fitted relatively in the rotational direction. Fit together without any gaps,
A hub split type damper device characterized in that a main hub and a sub-hub are elastically connected in a circumferential direction of the hub by installing and fixing a rubber member between the main hub and the sub-hub.