JPH07269605A - Holding member of clutch engaging element - Google Patents

Abstract

PURPOSE:To prevent burrs to be generated in forming of pockets from interfering with rotation of both holders by a simple structure in a holding member for controlling positioning and attitude of clutch engaging elements by the pockets provided on two holders to be relatively rotated. CONSTITUTION:A first holder 7 and a second holder 8 are fitted to each other, and sprags are inserted into pockets 9, 10 so provided as to face both holders 7, 8. A circumferential groove 16 is provided in the center area of the second holder 8, and the fitting gap between the pocket parts is increased, so as to prevent interference of burrs. Outside diameter surfaces 8a, 8a of the second holder 8 are brought in slide contact with the inside diameter surface 7a of the first holder 7, so as to guide rotation of both holders.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a holding member for a clutch engagement element which controls the positioning and posture of the engagement element by two retainers.

[0002]

2. Description of the Related Art A conventional two-way clutch using a sprag, as shown in FIG. 10, has a driving member 41 fitted inside and outside.
Between the driven member 42 and the driven member 42, a first retainer 43 and a second retainer 44 having different diameters are incorporated, and a plurality of radially opposed pockets 45, 46 are formed on the peripheral surfaces of the retainers 43, 44. A sprag 47 as a clutch engaging element is inserted into each of the pockets 45 and 46.

The first retainer 43 is rotatable with respect to the driving member 41 and the driven member 42, and the second retainer 44 is connected to the driving member 41 so as to rotate together with the driving member 41.
When the first retainer 43 and the second retainer 44 rotate relative to each other due to the rotation difference between the driven member 42 and the driven member 42, the sprag 47 is tilted by the guide of the pockets 45 and 46 and engages with the drive member 41 and the driven member 42.

In this clutch structure, the first cage 43
The second retainer 44 and the second retainer 44 are fitted inside and outside so that they can rotate relative to each other, and the fitting surfaces of both retainers 43 and 44 are controlled by a minute gap, so that the rotation of the first retainer 43 is controlled by The two cages 44 guide the cage to prevent rattling of the cage during clutch operation.

[0005]

By the way, in general, the pockets 45 of the first retainer 43 and the second retainer 44,
46 is formed by press working, and in the case of the first cage 43, the peripheral surface of the cage is punched from the outside to the inside by a punch to form the pocket 45.

However, when the pocket is formed by punching with the press as described above, a burr a is generated on the inner diameter side of the pocket 45 of the first retainer 43, and both retainers 43, 44 are formed.
In the combined state, the burr a may interfere with the outer diameter surface of the second cage 44 facing each other with a minute gap. When the burr thus interferes, the first retainer 43 may be rotated by the second retainer 44 and may not function as a clutch.

Conventionally, in order to solve the above-mentioned problems, after forming pockets, the peripheral surface of the cage is subjected to post-processing such as polishing to remove burrs that have occurred. There is a problem that the number of steps in manufacturing the cage is increased and the manufacturing cost is increased.

Therefore, the present invention is intended to solve the above-mentioned problems and to provide a holding member which can prevent the entrainment phenomenon between the cages due to burrs by a simple method.

[0009]

In order to solve the above-mentioned problems, according to the present invention, the fitting gaps of the two cages constituting the holding member are set to be large in the pocket forming portion and small in the other portions. Of.

In the above means, a circumferential groove longer than the entire length of the pocket is formed in the pocket forming portion on one fitting surface of both cages, and the fitting gap is set to be large by this circumferential groove. be able to.

[0011]

In the above structure, by making the fitting gap of the pocket forming portion larger than the protruding amount of the burr generated in the pocket, it is possible to prevent the interference between both cages due to the burr.

Further, by controlling the fitting gap of the fitting surface other than the pocket forming portion with a minute value, that portion serves as a guide surface between the cages, and the rattling at the time of relative rotation of each cage is suppressed. be able to.

[0013]

Embodiments of the present invention will be described below with reference to the accompanying drawings. 1 to 6 show an example in which a holding member of the present invention is incorporated into a hub clutch device A mounted on the front wheels of a four-wheel drive vehicle. In FIG. 1, reference numeral 1 is a drive connected to a front wheel axle B. Inner rings 2 that are members are outer rings that are linked to the wheel hub C and are driven members.

The inner ring 1 and the outer ring 2 are rotatably fitted inward and outward by bearings 3 and 4, and concentric cylindrical surfaces 5 and 6 are formed on their opposing surfaces.

A cylindrical first retainer 7 and second retainer 8 are incorporated between the cylindrical surfaces 5 and 6, and the peripheral surfaces of the retainers 7 and 8 are opposed to each other in the radial direction. A plurality of pockets 9 and 10 are provided, and a sprag 11 as a clutch engaging element is inserted into each of the pockets 9 and 10.

The first cage 7 has a needle bearing 13 and a rolling bearing 4 incorporated inside and outside a rear end portion 12 extending rearward, and is rotatable with respect to the inner and outer rings 1 and 2 by the guide of each bearing. It is supported. Further, the second cage 8 is formed with a bent portion 14 that bends toward the inner diameter side at the front end, and the bent portion 14 is crimped to the end surface of the inner ring 1 by the disc spring 15 and the retaining ring 15 ′. It is held so as to rotate together with the inner ring 1 by crimping.

The first retainer 7 and the second retainer 8 are shown in FIG.
Further, as shown in FIG. 6, a circumferential groove 16 is formed in the center of the outer diameter surface of the second retainer 8 so as to be fitted inside and outside so as to be relatively rotatable. The length L ₁ of the circumferential groove 16 is determined by the respective pockets 9 of the first and second cages 7, 8.
It is formed to be larger than the axial length L _{2 of} 10 and shorter than the total length L ₃ of the second cage 8, and the depth t of the circumferential groove 16 thereof.
Is set to be larger than the protruding amount of the burr a formed when the pocket 9 of the first cage 7 is formed.

Further, in the second cage 8, the circumferential groove 16
The diameter dimension D ₁ of the outer diameter surfaces 8a, 8a formed on both sides of is slightly smaller than the diameter dimension D ₂ of the inner diameter surface 7a of the first cage 7, so that both cages 7, 8 are fitted inside and outside. When fitted together, the outer diameter surfaces 8a, 8a and the inner diameter surface 7a are brought into sliding contact with each other with a minute gap so that the relative rotation of both cages 7, 8 is guided.

As shown in FIG. 6, the sprags 11 inserted into the pockets 9 and 10 of the first retainer 7 and the second retainer 8 are arc-shaped engagements having curvature centers on the sprag center line at both ends. When the first retainer 7 and the second retainer 8 are relatively rotated in the forward and reverse directions, the engaging faces 17 and 18 at both ends are provided with the cylindrical faces 5 and 6 of the inner and outer rings. Engage and connect the inner and outer wheels 1, 2 together.

As shown in FIG. 1, the first retainer 7 has a front end portion to which a switch spring 19 serving as one rotation resistance generating means is connected, and a rear end portion 12 of the retainer 7 to which a clutch spring is connected. A rotation resistance generator 21 is connected via 20.

As shown in FIG. 3, the switch spring 19 is composed of a C-shaped compression spring, one end of which is locked to the first retainer 7 and the other end of which is locked to the second retainer 8. Due to the elastic force that tends to increase the diameter, a unidirectional resistance force that is a deceleration force is always applied to the first cage 7.

In addition, as shown in FIG. 1, the rotary resistance generator 21 has a fixed resistance case 22 connected to the knuckle D.
And the input ring 23 connected to the clutch spring 20,
The flanges 24 and 25 facing each other in parallel are provided, and the both flanges 24 and 25 are crimped by the elastic spring 26,
Due to the frictional force generated in the crimp portion, a resistance force larger than that of the switch spring 19 is applied to the input ring 23.

The clutch spring 20 is provided with a continuous winding coil fitted to the rear end 12 of the first cage 7 and the input ring 23, and the bent locking portion 27 at the rear end of the spring is attached to the input ring 23. It is locked together. Further, the winding coil 28 on the front end side of the clutch spring 20 is fitted to the outer periphery of the rear end portion 12 of the first cage 7 in a state of weak interference fit.

In this clutch spring 20, the first retainer 7
When the coil rotates in one direction, the winding coil 28 on the front end side loosens with respect to the first retainer 7, and the first retainer 7 and the input ring 23
Separate the power transmission between. On the contrary, when the first retainer 7 rotates in the opposite direction to the above, the winding coil 28 on the front end side is tightened in the first retainer by the frictional force due to the contact with the retainer, and the first retainer 7 and the input ring. 23 and united together.
In the state where the first cage 7 and the input ring 23 are connected in this way, the resistance of the rotation resistance generator 21 having a large resistance force acts on the first cage 7, and the first cage 7 with respect to the rotation of the inner ring 1 is rotated. Delay the rotation of 7.

This embodiment has the structure as described above, and when the inner ring 1 rotates in one direction (for example, the forward direction of the vehicle),
The first retainer 7 rotates later than the inner ring 1 due to the resistance force of the switch spring 19, and the sprag 11 is guided by the pockets 9 and 10 of the first retainer 7 and the second retainer 8 which relatively rotate as shown in FIG. Is tilted to enter the standby state for engagement. From this state, when the inner ring 1 rotates faster than the outer ring 2,
The sprag 11 engages with the cylindrical surfaces 5 and 6 to integrate the inner and outer wheels 1 and 2, and the driving force is transmitted from the front wheel axle B to the wheel hub C.

The inner ring 1 is in the opposite direction (the backward direction of the vehicle).
When rotated to, the clutch spring 20 is locked and the resistance force of the rotation resistance generator 21 acts, but since the resistance force exceeds the resistance force of the switch spring 19, the first cage 7 is fixed and the sprag 11 is It tilts in the direction opposite to that in FIG. When a difference in rotation occurs between the inner ring 1 and the outer ring 2 in that state, the sprags 11 engage the cylindrical surfaces 5 and 6 to transmit torque.

In the operation of the hub clutch device A described above, even if the burr a is formed on the inner diameter side of the pocket 9 of the first retainer 7 due to the formation of the pocket, the burr a is secondly held by the existence of the circumferential groove 16. Since it does not come into contact with the container 8, it is possible to prevent interference such that the first holder 7 and the second holder 8 (inner ring 1) rotate together.

By controlling the fitting gap between the outer diameter surfaces 8a, 8a on both sides of the circumferential groove 16 of the second cage 8 and the inner diameter surface 7a of the first cage 7 with a minute value. The outer diameter surfaces 8a, 8a and the inner diameter surface 7a function as a guide surface for rotation between the cages, so that both cages 7, 8 can be smoothly rotated relative to each other.

FIGS. 7 and 8 show a second embodiment of the holding member. In this embodiment, a circumferential groove is formed on the outer diameter surface of the first holder 7 on the large diameter side, not on the second holder 8. 16 are provided.

Thus, the circumferential groove 16 is formed on the side of the first cage 7.
Even if the above is provided, it is possible to prevent the burr generated in the pocket 9 of the first retainer 7 from interfering with the second retainer 8, and it is possible to obtain the same effect as that of the above-described embodiment.

FIG. 9 shows a third embodiment. In this example, two types of sprags 31 and 32 that engage with the cylindrical surfaces 5 and 6 in opposite rotational directions are inserted into the pockets 9 and 10 of the first retainer 7 and the second retainer 8, respectively. The respective sprags 31 and 32 are alternately combined on the left and right sides so as to be engaged in both forward and reverse directions.

A circumferential groove 16 is formed at the center of the inner diameter surface of the second cage 8 to prevent burrs from interfering with each other.

In each of the above embodiments, each cage 7,
The pockets 9 and 8 of 8 directly push the sprags to the neutral position and the engagement position.
The posture of the sprag 11 may be held by an elastic material incorporated in the pocket of the first cage.

Further, in the above example, the example applied to the hub clutch device of the vehicle is shown, but it has the rotation transmission device for switching the transmission state of torque on the drive path of the four-wheel drive vehicle and the rotation resistance generating means. The present invention can be similarly applied to the case where the two-way clutch is used alone without using it.

[0035]

As described above, according to the present invention, the fitting gap between both cages is partially changed, the fitting gap of the pocket forming portion is increased to prevent the interference of the burr, and the fitting of the other portions is prevented. Since the relative clearance is guided with a small clearance, the cages can be smoothly rotated relative to each other with a simple structure without post-processing such as polishing, and stable clutch operation can be maintained. .

[Brief description of drawings]

FIG. 1 is a cross-sectional view showing a hub clutch device according to an embodiment.

FIG. 2 is a sectional view taken along line II-II in FIG.

FIG. 3 is a sectional view taken along line III-III in FIG.

FIG. 4 is a perspective view showing a part of the above second retainer.

FIG. 5 is a cross-sectional view showing a fitted state of the same cage.

FIG. 6 is an enlarged cross-sectional view showing the main part of the above clutch.

FIG. 7 is a perspective view showing a first cage according to a second embodiment.

FIG. 8 is a cross-sectional view showing a fitted state of the same cage.

FIG. 9 is a sectional view showing a third embodiment.

FIG. 10 is a sectional view showing a conventional two-way clutch.

[Explanation of symbols]

 1 Inner ring 2 Outer ring 5,6 Cylindrical surface 7 First retainer 8 Second retainer 9,10 Pockets 11, 31, 32 Sprag 16 Circumferential groove 19 Switch spring 20 Clutch spring 21 Rotational resistance generator A Hub clutch device

Claims (3)

[Claims] 1. A plurality of annular cages having different diameters are rotatably fitted inside and outside, and a plurality of radially opposed pockets are formed on the peripheral surfaces of the both cages. A holding member for a clutch engagement element, wherein a fitting gap between the both cages is set to be large in a pocket forming portion and small in other portions in a holding member of the clutch engaging element for accommodating the engagement element. 2. The method according to claim 1, wherein a circumferential groove longer than the entire length of the pocket is formed in the pocket forming portion on one fitting surface of both the cages, and the fitting gap is set to be large by the circumferential groove. A holding member for the clutch engagement element described. 3. The holding member for a clutch engagement element according to claim 1 or 2 is incorporated between a driving member and a driven member fitted inside and outside, and one of the fitted two cages is a driving member. Engagers that are connected so as to rotate together, and that engage with the driving member and the driven member and integrally connect both members to the pockets of the both holders when the both holders rotate relative to each other in the forward and reverse directions. To the cage that does not rotate together with the drive member,
A clutch device in which rotational resistance generating means for applying rotational resistance in mutually opposite directions and means for switching the action direction of the rotational resistance applied to the retainer to the forward and reverse rotational directions of the drive member are connected.