JPS60495Y2 - Gap adjustment ring - Google Patents

Description

[Detailed Description of the Invention] This invention relates to a clearance adjustment ring used to adjust the axial clearance when installing a bearing on a base.

Conventionally, when a one-rotation shaft is attached to a base via a bearing, the outer case of the bearing is supported in the axial direction and in the direction perpendicular to the axis, and a predetermined load is applied.

This operation is to adjust the so-called tightening, and removes gaps between the members that make up the bearing, thereby ensuring the rigidity of the bearing itself.

In addition, this operation determines the rotation starting torque of the bearing, that is, the preload, and also determines the position of the bearing.

Among these, to adjust the gap in the axial direction, for example, the first
As shown in the figure, a housing 2 of a ball bearing 1,
A thin metal plate 5 called a shim is attached to a contact portion X with the retainer 3 fixed by a bolt (not shown) and a contact portion Y between the retainer 3 and the outer case 4 of the ball bearing 1.
Perform an operation to sandwich the .

By adjusting the thickness of the metal plate 5, a gap within the bearing 1 is removed, and the relative manner of assembly of the inner case 6 and outer case 4 is determined.

When determining the thickness of the shim used in this way, there are two methods:
After temporary assembly of related parts, bearing 1 from housing 2
The method is determined by measuring the amount of protrusion of the retainer 3 and the depth t of the retainer 3, or after temporary assembly after inserting a shim of an appropriate thickness, the preload of the rotating shaft 7 is measured, and if this is inappropriate, another method is determined. The method used is to replace the shim with a thickness of

However, all of these methods require considerable time for measurement, temporary assembly, etc., and are unsuitable for mass production, resulting in increased costs.

The object of this invention is to provide a clearance adjustment ring that can easily adjust the axial clearance of a bearing.

This idea is structured so that an annular elastic plate is sequentially bent in the circumferential direction to alternately form corrugated plate parts with different amplitudes, and an elastic force corresponding to the amount of deflection produced by the larger corrugated plate part 1 is applied to the bearing. be done.

According to this invention, the load in the amplitude direction, that is, the axial direction - deflection 8
Characteristics can be changed nonlinearly.

In other words, the spring constant is set small in the range where only the corrugated plate part with a large amplitude is deflected, and the change in load is set to be relatively small for differences in the amount of deflection within that range, and the load is approximately approximated. Add to bearing.

This makes it possible to apply an appropriate preload to the bearing regardless of differences in the accuracy of the gap.

On the other hand, in a range where two or more types of corrugated plate portions having different amplitudes are bent, the spring constant can be increased to elastically support a large load in the axial direction.

This invention will be explained below with reference to the accompanying drawings.

FIG. 2 shows a cross section of a main part inside the transmission 9 that houses the gear 8. As shown in FIG.

The gear 8 is pivotally connected to a housing 11 formed integrally with the outer wall by a tapered roller bearing (hereinafter simply referred to as a roller bearing) 10, and integrally connected to a rotating shaft 13 fitted into an inner case 12 of the roller bearing 10. Rotate.

Reference numeral 14 is a ring-shaped retaining ring that positions the inner case 12 and the rotating shaft 13.

The roller bearing 10 has an outer circumferential surface 151 of an outer case 15 in pressure contact with an inner circumferential wall surface 16 of the housing 11, and an outer circumferential surface 152 in pressure contact with a gap adjustment ring 18 as an embodiment of the invention.

This clearance adjustment ring 18 is supported by an annular retainer 17 fixed to the housing 11 side with a tightening bolt (not shown).

That is, the retainer 17 restricts the displacement of the outer case 15 in the axial direction A, and the gap adjustment ring 18 is compressed according to the gap a between the retainer 17 and the outer case 15 to apply a predetermined load P to the outer case 15. become.

As shown in FIG. 3a, the gap adjustment ring 18 has an annular shape as a whole, and is formed into a corrugated plate shape by sequentially bending an elastic plate in the circumferential direction.

Furthermore, there are two different amplitudes h1 in the circumferential direction. Corrugated plate portions 181 and 182 of h2 are formed alternately (see Fig. 3).

The corrugated plate portion 181 with the large amplitude h1 is formed into one large waveform, and the corrugated plate portion 182 with the small amplitude h2 is formed into a shape in which many small waveforms are continuous.

FIG. 4 shows a load P vs. deflection amount δ characteristic diagram in the amplitude direction of the clearance adjustment ring 18, that is, in the axial direction A when it is attached to a bearing.

This characteristic diagram has a non-linear shape, and in the range A up to the amount of deflection δ1, only the large-amplitude corrugated plate portion 181 of the gap adjustment ring receives the load P in the axial direction A, and is compressed, and in the range up to the amount of deflection δ2. At the mouth, both the small amplitude corrugated plate portion 182 and the large amplitude corrugated plate portion 181 receive the load P and are compressed.

In range A, the spring constant of the clearance adjustment ring 18 is set to be relatively small.

Therefore, in this range A, the change in the load P is relatively small compared to the change in the amount of deflection δ.

This gap adjustment ring 18 is attached to the inner wall surface 171 of the retainer 17.
When installed in the gap a between the outer case 152 and the outer case, if the deflection amount δ of the gap adjustment ring 18 is set to a value smaller than and similar to δ1, the load P applied to the outer case 15 will be equal to the deflection at that time. The value corresponds to the amount of deflection δ1, and is approximated to the load P1 corresponding to the amount of deflection δ1.

This means that if the value of the gap a is within a predetermined range, the warp load P
This means that a value close to 1 can be added to the outer case 15, and the length of the gap a can be adjusted with a certain degree of freedom.

On the other hand, when the gap adjustment ring 18 receives a large load in the axial direction A, the large amplitude corrugated plate portion 181 first bends by itself by δ1, and then moves toward the end of the range.

In this case, the small amplitude wave plate portion 182 with a relatively large spring constant
and the large-amplitude corrugated plate portion 181 having a relatively small spring constant are simultaneously displaced, so the overall spring constant becomes rapidly larger than in range A.

At this range opening, even if the clearance adjustment ring 18 receives a large load P2, the increase in the amount of deflection Δδ can be suppressed to a small value, and the gap adjustment ring 18 can elastically receive a large load over a relatively wide range.

In other words, the clearance adjustment ring 18 that receives a large load P2 from the outer case 15 is deflected by a relatively small amount of increase Δδ.
After this temporary large load P2 is removed, it immediately returns to its original position (near δ1).

At this time, the gear 8 side is also displaced by the increase in the amount of deflection Δδ at the same time, but since this gear position displacement is kept small as described above, the displacement of the gear 8 due to the elastic deformation of the gap adjustment ring 18 is caused by the displacement of the gear 8. No inconvenience will occur.

In order to use the clearance adjustment ring 18 shown in FIG. 3 to attach the roller bearing 10 shown in FIG. 2, first the roller bearing 10 and the retainer 17 are fixed to the housing 11.

The gap a between the two at this time is set in advance.

That is, this gap a is approximately the deflection amount δ1 of the gap adjustment ring 18.
The thickness may be set to a value when compressed to a smaller value, and even if this value is set relatively roughly, it will not differ much from the load P1 at that time.

Therefore, the gap a has a certain degree of freedom.

By installing the gap adjustment ring 18 in this gap a, the roller bearing 10 is prevented from shifting toward the gear 8 by the side surface of the gear 8, and by the gap adjustment ring 18 from shifting toward the retainer 17. .

In this case, since the gap adjustment ring 18 elastically presses the outer case 15 toward the gear 8 side with almost a load P1, this load P1 reduces the gap in the roller bearing, that is, the outer case 15, the taper roller 19, and the taper roller 19. The gaps between the roller bearing 10 and the inner case 12 are removed, and the backlash of the roller bearing 10 in the axial direction A is removed, so that the rigidity of the roller bearing 10 can be increased.

Furthermore, since an appropriate preload can be applied to the roller bearing 10 using this load P1, various noises generated due to rattling of the roller bearing 10 can be reduced, and rattling in the axial direction A due to initial wear of the roller bearing 10 can be automatically corrected. It is carried out in a regular manner.

As described above, if the gap adjustment ring 18 is used, there is less need to provide precision to the gap a between the roller bearing 10 and the retainer 17, and the roller bearing 10 can be easily attached to the housing 11.

Moreover, even though the degree of freedom of the gap a is relatively large, it is possible to apply almost the same level of load P1 to the roller bearing, and it is possible to apply the same level of preload to the roller bearing 10.

Furthermore, when a large load P2 is applied from the gear 8 side, the gap adjustment ring 18 is elastically deformed by a slight increase in deflection Δδ, and when this load P2 is removed, it can return to its original position. Since it is a body, inconveniences due to a decrease in rigidity are also prevented.

The gap adjustment ring 18 shown in FIG.
1 and a small-amplitude waveform portion 182, but in some cases, a small-amplitude waveform portion (not shown) may be added, and three types of corrugated plate portions may be alternately formed.

Incidentally, instead of the roller bearing 10 shown in FIG. 2, the gap adjustment ring 18 to which this invention is applied can be used to mount a ball bearing or other well-known bearing, and the same effect can be obtained.

Although the clearance adjustment ring 18 is attached to the transmission in the above description, it can also be used in general structures having bearings, such as transfers and differential gears.

As mentioned above, the clearance adjustment ring 18 to which this invention is applied
Using this makes it easier to install various bearings, and it also makes it easier to apply the same level of preload to each bearing during mass production.

[Brief explanation of the drawing]

Fig. 1 is a cross-sectional view of the main parts showing the conventional way of mounting a bearing, and Fig. 2 shows the mounting state of a roller bearing that is mounted by installing a clearance adjustment ring as an embodiment of this invention. FIG. 3A is a perspective view of the clearance adjustment ring, FIG. 3B is a developed view thereof, and FIG. 4 is an axial load-deflection 8 characteristic diagram of the clearance adjustment ring. 10...Roller bearing, 17...
Retainer, 18...Gap adjustment ring, 181.
...Large amplitude wave plate part, 182...Small amplitude wave plate part, a...Gap, δ...Deflection amount, P
...Load, A...Axial direction.

Claims (1)

[Scope of utility model registration request] An annular elastic plate is sequentially bent in the circumferential direction to alternately form at least two corrugated plate parts with different amplitudes, and only the corrugated plate part with the larger amplitude is compressed in the amplitude direction and remains in a bent state. , a gap adjustment ring configured to be installed in the gap between the facing side of the bearing and the fixed member and to apply a preload to the bearing.