JPS58203228A - Coupling construction of spline - Google Patents

Abstract

PURPOSE:To remarkably reduce or prevent noise which is created between internal and external spline gears when a torque is fluctuated, by resiliently energizing the internal and external spline gears in the circumferential direction. CONSTITUTION:A pair of the first and the second linear spring 30 and 30a are synmetrically arranged. Those opposite ends 32, 32a are engaged in notches 33 and 33a, respectively, and mounting parts 31 and 31a are engaged in annular grooves 32 and 32a, respectively. Then, linear springs 30 and 30a stretch axially over both sides of a coupling sleeve 15. Intermediate parts 33 and 33a abut spline gears 13b and 14 b of the first and the second external spring 13a and 14a, respectively and serveas pressure part for pressing the external spline gears 13b and 14b. A separating distance l between the intermediate parts 33 and 33b in their natural configurations, is determined longer than the root width l1 between the external spline gears 13b and 14b.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a spline coupling structure including an inner spline and an outer spline that mesh with each other to transmit torque.

In general, there are various examples of machines in which torque transmission shafts are connected using splines.

For example, the spline coupling structure is also used in a sub-transmission for switching between two wheels and four wheels in a four-wheel drive vehicle. That is, FIG. 1 shows an auxiliary transmission 1, and this auxiliary transmission fi
kl is a main gear 2 that is connected to a drive shaft of a main transmission (not shown) and is rotationally driven, and a counter drive gear 3 that is rotated by this main gear 2. Equipped with a counter low gear, these counter drive gears3. On the counter low gear table, there is a high gear r6. tff-gears 7 are in mesh with each other. Clutch gears 8 and 9, which are used as external splines, are formed in the opposing parts of the high gear 6 and low gear 2, respectively.
A clutch gear lo, which is integral with the rear drive shaft 5 and has the same diameter as the clutch gears 8 and 9, is formed between the high gear 6 and the low gear 7, and the clutch gear lo has a coupling sleeve 11 formed with an internal spline. mesh,
By this axial movement of the coupling sleeve 11, the rotation on the high gear 6 side or the rotation on the low gear 7 side is switched and transmitted to the rear drive shaft 5. Therefore, a gl spline connection structure is adopted between the clutch gears 8, 9, 10 and the coupling sleeve U. Furthermore, the rear drive shaft 5
At one end, a shaft 12 connected to a front axle (not shown) is disposed coaxially and oppositely, and a rear clutch gear 13 and a front clutch gear 14, which are used as external splines, are formed at the opposing portions of the shafts. A coupling sleeve 15 formed with internal splines that can engage simultaneously with these rear and front clutch gear ribs 14 is fitted. The rear drive shaft 5 and the front drive/naft shaft are connected and disconnected by the axial movement of the coupling triple. Therefore, even if the rear clutch gear 13, 71:l is located in the rear clutch gear 14,
A coupling structure of the second spline is formed by the coupling triple and the first spline. Torque is transmitted through the second spline coupling structure.

By the way, in the spline coupling structure described above, in order to enable the coupling sleeves U and U to move in the axial direction, the inner spline teeth of the coupling sleeves U and 15 and the respective clutch gears 8, 9, 10, and L2° are connected to each other. A slight gap is provided between the outer spline teeth of No. 13 and the outer spline teeth of No. 13. Therefore, when a torque fluctuation occurs between the coupling sleeve and the clutch gear that mesh with each other, there is a problem in that the respective spline teeth collide with each other and abnormal noises such as impact noises are generated.

In view of such conventional problems, the present invention biases the inner spline teeth and the outer spline teeth in the circumferential direction with resilient force, thereby preventing the inner spline teeth from rotating when the torque fluctuates.

It is an object of the present invention to provide a spline coupling structure that significantly reduces or prevents abnormal noise generated between outer spline teeth. To achieve this objective, the present invention
At least one of the spline teeth on either the inner spline or the outer spline that meshes with each other to reach torque is removed to the extent that it does not interfere with torque transmission, and the other spline is installed in the area where the spline teeth are removed. A linear spring is provided that contacts the spline teeth and biases the spline teeth in the circumferential direction with elastic force. Therefore, in such a spline connection structure,

The outer spline teeth are biased in the circumferential direction by linear springs, and when torque is transmitted between the inner and outer splines in the opposite direction to the biasing direction of the linear springs due to torque fluctuations, the inner and outer spline teeth are biased in the circumferential direction. The spline teeth rotate relative to each other in opposite directions by the gap between them and try to collide with each other, but at this time, the energy of the collision due to the relative rotation is absorbed by the biasing force of the linear spring. It can reduce the impact when the inner and outer spline teeth collide. Furthermore, by appropriately adjusting the biasing force of the linear springs or the number of linear springs, it is possible to almost completely eliminate the impact when the inner and outer spline bushes collide. Therefore, in the present invention, one embodiment of the present invention will be described below to achieve the excellent effect of significantly reducing or preventing abnormal noise that occurs when torque fluctuation occurs between the inner and outer splines. An example will be explained in detail based on the figures.

Fig. 2 shows the connecting structure of the second spline of the auxiliary transmission shown in the conventional example described above, where 5 is a 4-gloss drive shaft, 7t is a front drive shaft, and one end of this front drive shaft is 7t. It is coaxially and rotatably fitted into a central hole 5a formed at the end of the rear drive shaft 5 via a needle bearing Ib.

Reference numeral 13 denotes a clutch gear formed integrally with the front drive gear 7 of the rear drive shaft 5, and a first outer spline 13a is formed on the outer periphery of the rear clutch gear l. On the other hand, 14 is integrally formed with the front drive shaft, and 14 is formed integrally with the front drive shaft.
A front clutch gear disposed opposite to the J-ya clutch gear, and a second outer spline 141L having the same diameter as the first outer spline 13a is also formed on the outer periphery of this front clutch gear. . The first outer spline Da of the rear clutch gear ratio has an inner spline 15.
A coupling sleeve 15 formed with a letter m is slidably engaged with the coupling sleeve 15, and the coupling sleeve 15 is moved in the axial direction by a fork (not shown) that fits into a circumferential groove 15b formed on the outer periphery. The coupling sleeves ``are connected to the front and rear clutch gears u and 1 as shown by solid lines in the figure.
By meshing across 4, the rear drive shaft 14 is connected to the front drive shaft 14, and torque is transmitted between them. here,
In the first embodiment of the present invention, as shown in FIGS. 3 to 6, the internal spline teeth 1 of the coupling sleeve t
Eliminate one f + c, and in this spline tooth elimination partial prisoner,
The outer spline teeth 1 are in contact with the outer splines *t4a and 13a of the front and rear clutch gears 14 and 13.
4a.

A pair of first and second linear springs (X) and (ma) are arranged to bias la with elastic force in the circumferential direction.

The linear springs 30, 30a are each formed into a substantially U-shape, and a coupling sleeve 1 is attached to each end of the linear springs 30, 30a.
Attachment portions 31 and 31a are formed extending in the circumferential direction of 5. On the other hand, the linear springs 30, 31) are provided on both axial end surfaces of the coupling sleeve (2) over the entire circumference.
An annular groove 32 , Z a is formed with a wire diameter width of a, and notches Ω, 33 a are formed on both sides of the spline removed portion (support) in the axial direction from the center thereof to the annular groove 32 , 32 a. It is. Then, as shown in FIG. Second linear springs 30, 30
by symmetrically arranging the two side parts n, 32a thereof, and fitting the notches 33, X3a, and fitting the mounting part 31, BJa into the annular grooves 32, 32a, Linear spring X), 30
a is disposed straddling both sides of the coupling and sleeve in the axial direction. At this time, the both sides, 1
2 and 32a are formed in advance to be inclined inward as shown by the solid line in FIG. There is. Further, the pair of linear springs X.

The intermediate portions 33 and 33a of 3Da are the side portions j2,
32a are bent in the circumferential direction so that they are separated from each other in opposite directions, and this intermediate part, N9, &l a
is the spline tooth 13'b of the eleventh second outer spline 13a, 14a.

14 b and extranuclear spline teeth 13 b , 1
4 serves as a suppressing portion that presses b. In addition, the said intermediate part Ω.

If you can enter the natural state of Wa! 1lVfif is the fourth
As shown in the figure, the width of the valley of the outside spline teeth t3b and t4b! , set it higher. Furthermore, the both sides X
.

, 12a are formed by retreating inward in the axial direction of the coupling sleeve 15, and the outer spline teeth 14b are linear springs 30, 30a, l-inner spline teeth 15c.
It is easy to overdo it between the two.

'1 With the above configuration, the coupling sleeve 15 is slid as shown in FIG.
5, the inner spline 15a is the rear, and the 1st spline of the front clutch gears 13, 14. Second outer spline 13a
, 14a, and the entire body rotates in the direction of arrow The spline teeth 15c are in contact with each other in the direction opposite to the rotational direction X, and the splines 1114b of the second outer spline 14a are in contact with the inner spline 91Bc in the rotational direction I@.

Therefore, the outer spline @13b.

14 Internal spline tooth 1 adjacent to the side opposite to the abutting side of b
5, gaps a and b are provided between them. At this time, a pair of first . Of the second linear springs 30E and 30a, the first linear spring X located on the rotational direction X side is connected to the spline tooth 14'b of the second outer spline 14a.
, the intermediate part moves in the opposite direction to the rotating direction X,
A gap a' is provided between the intermediate portion Ω and the spline tooth 13b of the first outer spline 13a.

Further, the second linear spring 30a is similarly pressed by the spline teeth 13b of the first outer spline 13a, so that the intermediate portion 33a moves in the rotation direction X, and the intermediate portion 33a and the second outer spline 14a move. A gap b' is provided between the spline fit4b and the spline fit4b.

When in this engaged state, when a torque fluctuation occurs between the rear clutch gear l and the front clutch gear 14 in the deceleration direction due to deceleration, etc., the internal spline teeth 1
1st for 5c. Second outer splice 713a, 14a
The rear and front clutch gears 13 and 14 are connected so that the spline teeth 13b and 14b of
rotates relative to each other. At this time, the outer spline 13a,
With the relative rotation of 14a, the first and second linear springs 30 and 30a are returned, and as shown in FIG. 8, the outer spline ml! At the neutral position where the gaps a, b, between the internal spline teeth 15c and the internal spline teeth 15c are about half, the first. second linear spring X),
X) The intermediate portions g3 and 33a of a come into contact with both the outer splines fi13b and t4b. Then, when the coupling sleeve 15 and the front clutch gear 14 try to rotate relative to each other from this state, the spline 13b of the first outer spline 13a is rotated by the first linear spring. While rotating while compressing this spring X against the biasing force, the second outer spline 14a,
The spline orifices 14b, . . . 1111 rotate while compressing the second linear spring ffa against its biasing force. Therefore, the energy during the relative rotation between the coupling sleeve and the rear and front clutch gears 13 and 14 is the same as that of the first gear. Second linear spring 3
7, absorbed by 317 a. For this reason, the outer spline teeth 13b and 14b will eventually collide with the inner spline teeth in the opposite direction to the state shown in FIG. 7, but the impact force at this time is significantly reduced. Ru. same,
By adjusting the biasing force of the linear spring a) and JOa appropriately, or by providing a plurality of spline tooth removal parts, the linear spring X) can be obtained by providing a plurality of linear springs a) and the spring X.

By adjusting the overall spring force by the number of springs 30a, the impact can be almost completely eliminated.
,.

FIG. 9 shows a second embodiment, in which the coupling sleeve 15
Inner spline 15 A spline tooth removal part 20
a and 20b are provided at two locations facing each other, and a first linear spring xb is attached to one spline tooth removal portion 20a.
Second linear springs 3111c are respectively attached to the other spline tooth removed portion 20b.

FIGS. 10 and 11 show a third embodiment, in which linear springs 30 d and 30 e are attached to the outer spline side. That is, in this embodiment, the linear spring 30d,
30s is installed, and in this embodiment, as in the first embodiment described above, the rear clutch gear arm has a spline tooth removal portion 20c, an annular groove 32b,
32c etc. are formed. And the above-mentioned 1. Second linear springs 30d and 3De are disposed in the spline tooth removal portion 20c to urge the internal spline teeth 15c in opposite directions, respectively.

Although this embodiment shows the case where the linear springs 30d and 30e are attached to the eleventh clutch gear 13, linear springs can be similarly attached to the front clutch gear (not shown).

FIG. 12 shows a fourth embodiment, in which a linear spring material is bent into a substantially R-shape to form a linear spring JI7f, and a mounting portion X provided at one end of the linear spring material is connected to a coupling sleeve ■. It is attached to one end face in the axial direction.

The bent both-side pressing portions 36 and 35a of the linear spring 37f are disposed in the circumferential direction within the spline tooth removal portion 2Oa, so as to press the outer spline teeth (not shown) in the circumferential direction.

Therefore, the second point mentioned above. Third. The fourth embodiments also have the same effect as the first embodiment, and have the effect of reducing or almost completely preventing abnormal noise between the inner and outer splines that occurs during torque fluctuations.

Although each of the embodiments described above discloses a case in which the present invention is applied to the second spline coupling structure of the sub-transmission 1 shown in FIG. 1, the present invention is not limited thereto. The present invention may be applied to a structure, and the present invention is also applicable to a spline coupling structure constituted by one outer spline and one inner spline, which is generally used without being limited to the sub-transmission 1. I'm not even talented at what I can do.

In addition, each of the above embodiments has shown a pair of linear springs or suppressing portions provided in the circumferential direction due to the presence of two outer splines, but as described above, a single outer spline and an inner spline When the coupling structure is constructed, a single linear spline having biasing force in only one direction may be attached.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view of an auxiliary transmission equipped with a conventional spline coupling structure, FIG. 2 is a cross-sectional view showing the spline coupling structure of the present invention, and FIG. 3 is a schematic diagram showing the spline coupling structure of the present invention. The partially enlarged sectional view, FIG. 4, shows the spline connection structure of the present invention! [Front view, FIG. 5 is a partially enlarged view of the linear spring used in the present invention, FIG. 6 is a perspective view of the linear spring used in the present invention, and FIGS. 7 and 8 are views of the spline of the present invention. 9 is a front view showing the second embodiment of the present invention, FIG. 10 is a front view of main parts showing the third embodiment of the present invention, and FIG. 11 is a front view showing the operating state of the coupling structure. 10
A sectional view taken along the line ff--■ in the figure, and FIG. 12 is a perspective view showing a fourth embodiment of the present invention. 5... Rear drive/naft, school... front drive noft, 13... rear clutch gear, 13a... first outer spline, 13b... spline scoop, 14...
...Front clutch gear, 14a...Second outer spline, 14b...Spline shaft, 15...Coupling sleeve, 15a...Inner spline, 15c...
・・Spline fungus, 笈. 20a, 20b, 213c, 20 (
1 = Spline tooth removal part, X), X) a,
37 b, Mc, 30 d, 37 e-
- Linear spring. 1-14ζ

Claims (2)

[Claims] (1) It has an inner spline and an outer spline that mesh with each other and transmit torque, and at least one of the spline teeth on either the inner or outer spline is removed to the extent that it does not interfere with torque transmission. A spline coupling structure characterized in that a linear spring is disposed in the spline tooth removed portion to abut on another spline tooth and bias the abutted spline tooth with elastic force in the circumferential direction. . (2) The linear spring has a substantially U-shape that is arranged straddling both sides in the axial direction of the internal spline or external spline that forms the spline tooth removal portion, and both ends of the linear spring serve as mounting portions. The spline coupling structure according to claim 1, characterized in that the intermediate portion of the linear spring serves as a suppressing portion that applies elastic force to the opposing spline tooth.