JPS5919768A - Gear - Google Patents

Abstract

PURPOSE:To omit a coil spring and to prevent the generation of gear noises resulting from the backlash, by providing a sub-gear having a tooth thickness slightly greater than those of a driving gear and a driven gear, and forming a radial slit at the central portion of each tooth of the sub-gear so that the width of the slit can be varied when the gears are brought into mesh with each other. CONSTITUTION:When a sub-gear 13 is brought into mesh with a mating gear, elastic deformation of the teeth is caused by the force applied from the outside, so that the width of a slit 14 is reduced. Thus, since the teeth of the sub-gear 13 is urged by the elastic force to expand outwards by increasing the width of the slit 14, the teeth of the sub-gear 13 are always held in tight contact with the teeth of a driving gear 12. Although some backlash exists between the teeth of the driving gear 12 and those of a driven gear 11, the backlash is eliminated since the teeth of the sub-gear 13 are expanded outwards through a distance corresponding to the backlash by the elastic force of the teeth of the sub-gear 13.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a gear device, and more particularly to a gear device capable of eliminating knocking noise caused by backlash between gear teeth.

Generally, a backlash B is provided between the teeth of the gears that mesh with each other, as shown in FIG. That is, this is because bank crazing is necessary to prevent gear assembly errors, tooth profile accuracy, tooth wear, thermal expansion, oil film protection, etc.

However, the presence of such hacks causes the gears to make rattling sounds. For this reason, when these gears are used in the transmission of an automobile, they cause discomfort to the occupants due to abnormal sounds and noises. In order to prevent such abnormal sounds and noises, a gear device that can eliminate Paso crush between gear teeth is required.

Examples of conventional gear devices in which the bumps between the teeth of gears can be removed include those shown in FIGS. 2 to 5. In Fig. 3.4, reference numeral 1 denotes a countershaft, which is a driven shaft, and a driven gear 2 is fixed to this driven shaft 1 so that it can rotate as a unit.

The driven gear 2 has a driven gear 2 adjacent to the driven gear 2 in its axial direction.
A subgear 3 having exactly the same tooth profile as the teeth of the driven gear 2 is provided so as to be slidable in the rotational direction. Also,
Nut rings 5.5' are formed on the driven shaft 1 on both sides of the driven gear 2 on the driven shaft 1 so that the driven riJI gear 2 and the sub-gear 3 do not move in the axial direction on the driven shaft 1. is engaged with the groove. The sub gear 3 is adapted to mesh with the drive gear 4 together with the driven gear 2. A groove 2b is provided on the surface 2a of the driven gear 2 that is in contact with the subgear 3 along the concentric circle of the pitch circle of the driven gear 2 and opens at the front 2a, as shown in FIG. 1; 6a with hooks bent in opposite directions at both ends
, 6b is housed. The hook portion 6a of the torsion annular spring 6 engages with the hole 2c parallel to the axis of the driven gear 2, and the hook portion 6a engages with the hole 2c parallel to the axis of the driven gear 2.
b engages with a hole 3a provided in the Zabugito 3 opposite to the groove 2b of the driven gear 2. When assembling the driven gear 2 and the sub-gear 3, the torsion annular spring 6 is elastically deformed and the driving teeth are assembled. Merge with 18.4. When the sub gear 3 meshes with the driven gear 2 and the driving gear 4 in this state, there is a gap between the teeth of the driven gear 2 and the teeth of the driving gear 4. is a helical annular spring 6 interposed between the two.
As a result, there is a biasing force that tends to cause the teeth to always deviate from each other in the circumferential direction, so that the teeth of the sub gear 3 are deviated from the teeth of the driven gear 2 in the circumferential direction, causing the sub gear 3 to shift. The teeth are in contact with the teeth adjacent to the teeth of the drive gear 4 that are in contact with the teeth of the driven gear 2. In this way, the elastic force of the torsion annular spring 60 interposed between the driven gear 2 and the sub gear 3 allows the driven No. 11 The bump between the teeth of the gear 2 and the teeth of the drive gear 4 can be removed.

However, in a gear device that can eliminate such a conventional sawing wheel, a torsion annular "spring" is interposed between the drive UIJ gear and the groove gear, and the drive gear and the groove gear are further assembled. When driving, the torsion annular spring is given elastic deformation to mesh with the driven gear-1
As a result, the number of parts increased and the cost of the gear device became high. There was a problem that the workability was poor.

The present invention was made by focusing on such conventional problems, and provides a gear device including a driving gear supported on a driving shaft and a driven gear supported on a driven shaft and meshing with the driving gear. , rotates integrally with either one of the driving gear and the driven gear, meshes with the other of the driving gear and the driven gear together with the one gear, and has a tooth thickness slightly larger than that of the driving gear and the driven gear. In order to solve the above-mentioned problems, the sub-gear is provided with a slit in the radial direction that can be freely changed to wide or narrow by meshing with the other of the drive III gear and the driven gear. There is.

The present invention will be explained below based on the drawings.

6 to 9 are diagrams showing an embodiment of the present invention. First, the configuration will be explained. In FIG. 6, 10 is a drive shaft, and a driven gear 11 is fixed to this driven shaft 10 so that it can rotate integrally therewith. This driven gear 11 meshes with a driving gear 12 supported by a driven shaft (not shown). Further, the driven gear 11 is connected to the driven gear 11 by serration coupling or the like adjacent to the driven gear 11 in the axial direction.
A zabugito 13 is provided so that it can rotate integrally with 1. The driven gear 11 and the sub gear 13 are the driven shaft 1
On both sides of the driven gear 11 on the driven shaft 10, snap rings 15, 15' engage in grooves formed in the driven shaft 10 to prevent it from moving axially on the driven shaft 10. The sub gear 13 is adapted to mesh with the driven gear 11 and the drive gear 12.

As shown in FIG. 9, the tooth thickness of the subgear 13 is formed to be somewhat larger than the tooth thickness of the driven gear 11 and the driving gear 12. In other words, in FIG. 9, the solid line indicates the tooth profile of the driven gear 11, and the dashed line indicates the subgear 1.
This shows the tooth profile of No. 3. The Boogie? The tooth thickness of No. 13 is at least the same as or slightly larger than the dimension of the tooth groove of the drive tooth No. 2. This is because if the tooth thickness of the gear 13 is smaller than the tooth groove of the drive gear 12, cracks will occur as in the conventional case. Furthermore, as shown in FIG.
The teeth of the sub-gear 13 have elasticity so that they can be changed widely or narrowly depending on the external force caused by meshing. The width of the slit 14 may be radially parallel, as shown in FIG. 8a, or radially tapered, as shown in FIG.

Next, the effect will be explained.

When the sub gear 13 meshes with the driving gear 12 together with the driven gear 11, the external force applied to the teeth of the sub gear 13 elastically deforms the teeth, narrowing the width of the ring 1-14, and allowing smooth meshing. For this reason, the teeth of the subgear 13 have an elastic force against the external force due to meshing, and this elastic force causes the teeth of the subgear 13 to expand outward and open the slit 1.
4 is biased in such a direction that it becomes wider, and for this reason, the teeth of the sub gear I3 are properly pressed against the teeth of the drive gear 12. There is a gap between the teeth of the driven gear 11 and the driving gear 12, but as shown in FIG. expands outward, and the tooth saw between the teeth of the sub-gear 13 and the drive gear 12 is removed.

In addition, in the above embodiment, a gear device in which the sub gear 13 is provided on the side of the driven gear 11 has been described, but the case is not necessarily limited to this case, and the sub gear I3 may be provided on the side of the driving gear 12. It may be something.

As described above, according to the present invention, the structure of the gear device includes a driving gear supported on a driving shaft and a driven float supported on a driven shaft and meshing with the driving gear. A subgear that rotates integrally with either one of the gear and the driven gear, meshes with the other of the driving gear and the driven gear, and has a tooth thickness slightly larger than that of the driving gear and the driven gear. A radial slit is provided in the center of the teeth of the sub gear, which can be changed freely to wide or narrow by meshing with the other of the drive gear and driven gear. By being able to remove the noise, it is possible to prevent the rattling noise of the gears from occurring, thereby eliminating the need to cause discomfort to the occupants of the vehicle due to abnormal sounds, noise, etc. Furthermore, according to the present invention, compared to a C-shaped gear device that eliminates the sagging of conventional gears, a torsion coil spring is not required, so the number of parts is reduced, and loss l- of the gear device can be reduced. When assembling gears, it is not necessary to perform elastic deformation on the torsion annular spring before assembling, so the assembly time can be shortened and the assembly work efficiency can be improved. It will be done.

[Brief explanation of drawings]

Fig. 1 is a -gH front view of a gear showing a scrape crush between the teeth of a general gear, Fig. 2 is a front view of a gear equipped with a conventional scraper removal device, and Fig. 3 is the same as that shown in Fig. 2. A-Δ
4 is a cross-sectional view taken along arrow B-13 in FIG. 2, FIG. 5 is a perspective view of the helical annular spring, and FIG. 6 is a side view 1tl of the gear device for removing the scraper according to the present invention.
i side view and FIG. 7 are partial front views of the sub gear used in the present invention, and FIGS. 8 (a) and 8 (b) are -gl (front view, FIG. 9a is a partial front view of the driving gear and sub gear before the sub gear meshes with the driven gear, and FIG. 9 is a partial front view of the driving gear, driven gear, and sub gear when they mesh. 1.10--One drive shaft, 2.11--One drive gear, 4
, +2----1 driven gear, 13----sub gear, 1.1---- slit. Figure 3 Figure 4 Figure 5 Figure 7 Figure 8 Figure 9 (b)

Claims (1)

[Claims] In a gear device that includes a driving gear supported by a driving shaft and a driven gear supported by a driven shaft and meshing with the driving gear, one of the driving gear and the driven gear rotates integrally with the other. A sub-gear is provided which meshes with the other of the drive gear and driven gear together with the gear and has a tooth thickness slightly larger than that of the drive gear and the driven gear. A radial slit that can be freely changed wide and narrow is installed at approximately medium heat between the teeth of the sub-gear, and the elastic force of the teeth of the sub-gear eliminates the hammering noise between the teeth of the driving gear and the driven gear. A gear device characterized by being able to.