JPS59175672A - Preventive device against rotational vibration noise of gear - Google Patents

Abstract

PURPOSE:To prevent the hitting noise of engaged gears by fixing an elastic member provided with a friction member fixed at a top end on one of the engaged gear and slidingly keeping this friction member in contact with the other gear. CONSTITUTION:One gear 2 of a pair of mutually engaged gears 1 and 2 is fixed with an elastic member 4 provided with a friction member 5 fixed on a top end and this friction member 5 is slidingly kept in contact with the other gear 1. In this way, an engaging faces of this pair of gears 1 and 2 are maintained in contacting state all the time by a friction power generated by a relative speed difference. This construction permits to prevent the hitting noise generated by backlash.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a device for preventing rotational vibration and rotational noise caused by pan crush of a pair of meshing gears.

Conventionally, gears have been used in many devices for power transmission, but when the gears are meshed, it is necessary to provide a bank plate between the tooth surfaces of the teeth that mesh with each other.

However, this pack lash causes rattling between the meshing gears due to rotational fluctuations or torque fluctuations of the drive source, and this is transmitted as vibration or noise, causing discomfort.

As a method for preventing this rattling, a device as shown in the first diagram is conventionally known.

In this conventional device, a friction member 5 fixed to the tip of a spring 4 fixed to a stationary member 3 is frictionally engaged with the side surface of one gear 1 of a pair of gears 1 and 2 by the elastic force of the spring 4. This is to prevent rattling.

However, in this conventional device, one side is rotating and the other is stationary, so the frictional force generated by the large relative speed difference is excessive, resulting in a large loss of kinetic energy.
The friction member 5 and the contact surface 1' were also subject to a large amount of wear, and had the disadvantage of being unsuitable for high-speed rotation.

It is an object of the present invention to eliminate the above-mentioned drawbacks of conventional devices and to prevent rattling caused by backrun.

The device for preventing rotational vibration noise of a gear according to the present invention is constructed by frictionally engaging a friction member disposed to rotate integrally with at least one gear with the other gear through an elastic member with a relative speed difference. The meshing surfaces of the gears are always kept in contact by the frictional force generated by the relative speed difference, making it possible to prevent rattling caused by backlash.

Embodiments of the present invention will be described with reference to the drawings. FIG. 2 is a sectional view of a pair of gears, and FIG. 2a is a partial plan view thereof. An elastic member 4 is fixed to one gear 2 by a fixing member 6, and a friction member 5 is fixed to the tip of the elastic member 4. Furthermore, this friction member 5 is attached to the contact surface 1a of the other gear 1.
is frictionally engaged with the elastic member 4.

Fig. 3 is a modification of Fig. 2 in which the friction member 5 is frictionally engaged with the circumferential surface of the hub of the other gear 1 instead of the side surface of the other gear 1. This is an example that can be used.

Hereinafter, the operation of the apparatus of the present invention will be explained in detail with reference to FIG.

If the circumferential speeds of the pair of gears 1 and 2 at the pitch point 7 are the same and have a speed of Vo, then the friction member 5
This is the contact surface of gear 1 which is the engagement surface with.

Similarly, the circumferential speeds of the friction member 5 are different between (1) and (2), and this speed difference causes sliding between the friction member 5 and the contact surface 1a, generating a frictional force. It turns out.

That is, according to the above formula, vl is always smaller than V2, and now if gear 1 is on the driving side and gear 2 is on the driven side, gear 1
is in a state where it always attracts the gear 2, so that the pitch point 7 always maintains a state of contact, and rattling can be prevented even if rotational fluctuations or torque fluctuations occur. In the above embodiment, the friction member 5 is fixed to the elastic member 4, but the friction member 5 may be fixed to a mating gear and frictionally engaged with the elastic member 4.

There are other methods of fixing the elastic member 4, such as caulking and welding, in addition to the embodiments, and the shape of the elastic member 4 can also be in various forms that exert the same elastic force. In addition, the friction operating part (Fig. 2a
By arranging the part ( ) closer to the axis of the drive side, rattling can be more effectively prevented.

The elastic member can also serve as a friction member, and the rotation between the friction member and the gear can be performed directly or indirectly through the elastic member or the like.

The device shown in FIG.
2, a spline 10 is formed on the outer periphery of the hub 11, and a sleeve 9 engaged with the spline is disposed movably in the axial direction. On the other hand, an axial protrusion 2a is disposed on the side surface of the gear 2, and a spline 10a that can be engaged with the spline of the sleeve 9 is provided on the outer periphery of the protrusion 2a. The shaft 12 and the gear 2 are relatively rotatable, and the shaft 12 and the gear 2 are fixed in position between the collar 13 and the snap 14 and the hub 11 in the axial direction. When the circumferential speeds of the gear 2 and the hub 11 at the spline IO are synchronized, the sleeve 9 can be held on the spline 10a even during rotation, forming a type of clutch device.

In this type of device, by providing a gear rotational vibration noise prevention device, it is possible to effectively prevent rotational rattling that frequently occurs when the spline is not engaged.

In particular, when used in vehicle transmissions, torque fluctuations are relatively large, especially when the transmission of a reciprocating internal combustion engine is in the neutral state and the engine is idling, but it is effective in such cases. . Further, in the flange engaged state, rattling is likely to occur when the vehicle is being driven, especially in a driving state where engine drive and engine braking are frequently repeated, but this can also be effectively prevented.

Are the above explanations parallel? Although we have discussed the case where spur gears installed on the shaft mesh externally, the effect is the same for bevel gears (Fig. 85) and planetary gears (Fig. 6), and rattling can be prevented. . In Fig. 6, if sun gear S, ring gear R, and binion gear P, between S and P,
It can be applied to both P and R, and can also be applied between the carrier C and S or R of the pinion gear. Further, the frictional movement part may be arranged closer to the axis of the driven side.

As is clear from the explanation up to now, the device of the present invention has the following advantages over conventional devices.

(1) Since the relative movement due to the relative rotational speed difference depending on the positional relationship between the friction member and the contact surface is utilized, a large loss of kinetic energy and excessive wear of the friction member and the contact surface can be effectively prevented.

(2) Since there is always a relative speed difference between the friction member and the contact surface, the meshing surfaces of the pair of gears can be kept in constant contact.

(3) Applicable to high-speed rotation, small gears, etc.

(4) Simple structure and no space burden.

[Brief explanation of the drawing]

FIG. 1 is an axial sectional view of an example of a conventional device, FIG. 2 is an axial sectional view of an example of the device of the present invention, FIG. 2a is a partial plan view as seen from the direction of arrow A in FIG. FIG. 3 is a sectional view of another example of the device of the present invention, FIG. 4 is an explanatory diagram of the principle of operation of the device of the present invention, and FIGS. 5 and 6 are schematic diagrams showing another embodiment of the present invention. It is. 1.2. , , , , gear la, 1151. Contact surface of friction member 3 , Stationary member 4 , Elastic member 5 , Friction member 8 , Fixed member? , , , , , , , Pitch point 8......'' Tsukurashi S , , , , , , Sun gear p , , , , , , Pinion gear R , , , , , , , Ring gear C, , , , , , Carrier Figure 1 Figure 20 Figure 3 Figure 4 cTI document on page 1 (no change in content) Figure 5 !'J'4'r (content No change) Figure 6 Procedural Amendment (Voluntary) April 22, 1980 Commissioner of the Patent Office Kazuo Wakasugi 1 Indication of the Case 1988 Patent Application No. 0702 (March 1988)
Date of amendment: Date of amendment order: Date of amendment order: Date of amendment order: Date of amendment order: Date of amendment order: Date of amendment order

Claims (1)

[Claims] Rotational vibration of a gear, characterized in that a friction member arranged to rotate integrally with at least one gear of a pair of mutually meshing gears is frictionally engaged with the other gear through an elastic member with a relative speed difference. Noise prevention device.