JPH10181376A - Rotation transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a two-way clutch that will not damage an idling function even if there are more or less dimensional variations and eccentricity is a little produced in a shaft and an outer ring. SOLUTION: This device is provided with plural cam surfaces 7 in an inner member 2 rotatably fitted in an output outer ring 1 and also a cylindrical surface 6 in this output outer ring 1, and a wedge-shaped space is formed in a gap between the opposited surfaces, and a roller 12 as an engager is built in a pocket 11 of a cage 8 set up in this space, constituting a two-way clutch. In succession, a recess 31 is installed in and around a central part of the cam surface 7 of the inner member 2 so as not to take part in this roller 12, and therefore reliability in an idling function of the two-way clutch is enhanced, and thus the extent of dimensional accuracy in the constituent parts can be loosely set up.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotation transmission device used for switching between transmission and interruption of a driving force on a driving path of a four-wheel drive vehicle.

[0002]

2. Description of the Related Art On a drive path of a four-wheel drive vehicle, 4 W
As a rotation transmission device used for switching between transmission and cutoff of a driving force in order to switch between D and 2WD, the present applicant has disclosed in Japanese Patent Application Nos. 4-182476 and 5-137773.
6, Japanese Patent Application No. 5-137753, Japanese Patent Application No. 5-1383
No. 08 proposed a two-way clutch using a roller as an engaging element.

FIGS. 4 to 7 show a typical example of a rotation transmitting device A using these roller-type two-way clutches. A bearing 3 and a two-way clutch 4 are provided inside an outer ring 1 serving as an output side member. The inner member 2 which is an input side member is rotatably fitted through the input ring 5, and an input ring 5 is attached to the end of the inner member 2 via a spline, and between the outer ring 1 and the inner member 2. The one-way clutch 18 and the rotation resistance applying means 22 are incorporated.

The two-way clutch 4 is provided with a cylindrical surface 6 on the inner diameter surface of the outer ring 1 and on the outer diameter surface of the inner member 2 opposed thereto.
A plurality of flat cam surfaces 7 are provided at predetermined intervals, and each of the cam surfaces 7 forms a wedge-shaped space between the cylindrical surface 6 of the outer ring 1 and both sides in the circumferential direction becomes narrower. I have.

[0005] An annular retainer 8 is provided between the outer race 1 and the inner member 2 via a bearing 3a.
The stopper pin 10 inserted into the pin hole 9 of the peripheral wall of the inner member 2 is connected to the stopper pin 10.

The cage 8 has the same number of pockets 11 as the cam surface 7 in the circumferential direction.
Further, a roller 12 as an engaging element and a spring 13 are incorporated. As shown in FIG. 8, one roller 12 is incorporated into each cam surface 7 of the inner member 2, and when the roller 12 is moved by a predetermined amount in the circumferential direction by the retainer 8, the cam surface 7 and the cylindrical surface 6 are separated. The outer ring 1 and the inner member 2 are integrated with each other. The spring 13 is incorporated between the roller 12 and the side wall of the pocket 11 and presses the roller 12 from both sides to hold the cylindrical surface 6 and the cam surface 7 at a neutral position where they are not engaged. When the roller 8 moves a predetermined amount in the circumferential direction, only the spring on one side of the roller 12 acts on the roller 12 and presses the roller against the engagement surface.

A one-way clutch 18 is press-fitted into the end of the cage 8. Further, a notch 16 is provided at the far end of the retainer 8, and each end of the torsion coil spring 17 is locked between the notch 16 and the spring seat 15 of the inner member 2, respectively. The spring force of the coil spring 17 applies an urging force to rotate the retainer 8 to the inner member in a direction opposite to the rotation direction.

On the other hand, the 1 press-fitted into the end of the cage 8
The direction clutch 18 is connected to the rotation resistance applying means 22 via the input ring 19.

The rotation resistance applying means 22 includes a connecting rod 23
A housing 24 connected to a vehicle body or the like via
The friction pad 25, which is rotatably supported on the outer ring and the inner member by a bearing and is press-fitted into the inner diameter of the housing 24, and the flange 26 provided on the input ring 19 are rubbed with each other. And a disc spring 28 incorporated therein. The spring force of the disc spring 28 acts in a direction in which the friction pad 25 is pressed against the flange 26, and generates a drag torque in the rubbing portion 29 due to the pressure, thereby causing the input ring 19 to rotate together with the retainer 8. On the other hand, a resistance that delays the rotation is given. The rotational resistance generated by the rubbing portion 29 is set to be larger than the rotational force applied to the holder 8 by the torsion coil spring 17 described above.

As shown in FIG. 7, the one-way clutch 18 includes a cam ring 30 press-fitted into the extended end 14 of the cage 8.
A plurality of inclined cam surfaces 31 are formed at regular intervals in the circumferential direction on the inner periphery of the small roller 33, between the cam surface 31 and the input ring 19, a small roller 33 held by a holder 32,
3 includes a cam surface 31 and a spring 34 for pressing the inner ring 19 against the cam surface 31.

In the above structure, when the inner member 2 and the torsion coil spring 17 are driven to rotate the retainer 8 in the direction of the arrow (b) in FIG. 7, the one-way clutch 1 pressed into the retainer 8 is pressed.
8, the input ring 19 and the retainer 8 are integrated,
The drag torque of the rubbing portion 29 of the rotation resistance applying means 22 is applied to the retainer 8. This torque is applied in a direction in which the rotation of the retainer 8 is stopped, and decelerates the retainer 8 with respect to the rotation of the inner member 2.

Conversely, the retainer 8 together with the inner member 2 is
When the one-way clutch 18 rotates in the direction (a), the one-way clutch 18 is disengaged and the one-way clutch 18 idles. For this reason, the resistance of the rotation resistance applying means 22 is not transmitted to the retainer 8, but the torsion coil spring 17 applies a rotational force to the retainer 8 in a direction opposite to the above-mentioned direction (a). Table 8
Is decelerated with respect to the inner member 2.

As shown in FIG. 6, a stopper pin 10 connected to the retainer 8 is provided with a pin hole 9 in the peripheral wall of the inner member 2.
Are loosely fitted with a clearance X in the rotational direction. The gap X in the rotation direction determines a delay angle of the retainer 8 with respect to the inner member 2, and its size is determined from the neutral position of the roller 12 to the cam surface 7 and the cylindrical surface 6 until the roller 12 comes into contact with the engagement position. It is set larger than the distance.

The above-mentioned rotation transmitting device A is mounted on a rear-wheel drive path of a four-wheel drive vehicle in which front wheels are main drive wheels as shown in FIG.

That is, a fluid coupling H or the like as a differential limiting device and an input ring 5 of an inner member 2 are connected in series to a rear wheel propulsion shaft D coming out of a transfer C, and
Is connected to the rear differential E.

The direction of rotation of the inner member 2 during forward running of the vehicle and the direction (a) of FIG.
Is set to match.

In the above-described rotation transmitting device A, when the vehicle travels forward, the retainer 8 is rotated with a delay from the inner member 2 by the torsion coil spring 17, and the relative rotation causes the roller 12, which is the engaging element, to engage. State. Conversely, when the vehicle travels backward, the delay direction of the retainer 8 is switched by the operation of the one-way clutch 18 and the rotation resistance applying means 22, and the rollers 12 are similarly engaged.

When the vehicle travels straight in the forward or backward direction in the engagement operation state, the front wheels, the rear wheels, and the rear wheel propulsion shaft rotate at the same speed, and the roller 12 maintains the engagement standby state. For this reason, two-wheel running with only the front wheels is performed.

On the other hand, if the front wheel or the rear wheel slips during running, the rotation of the rear wheel propulsion shaft with respect to the wheel increases, and the roller 1
Since 2 is engaged, the driving force is transmitted to the rear wheels, and the state is switched to the 4WD state.

Conversely, when the vehicle is suddenly braked and the front wheels try to lock, the rear wheel propulsion shaft rapidly decelerates with the locking of the front wheels, but the rotation of the rear wheel (driven member) is reduced by the rotation of the rear wheel propulsion shaft. Since the rotation exceeds the rotation, the inner member 2 and the outer wheel 1 idle, and the deceleration force accompanying the front wheel lock is not transmitted to the rear wheel. As described above, since no binding force is generated between the rear wheel and the front wheel to be locked, ABS control becomes easy as in the case of the 2WD vehicle.

FIGS. 8 and 9 show a specific operation state of the conventional two-way clutch 4 described above.

As shown in FIG. 8 (A), the rotation of the retainer 8 is delayed with respect to the rotation of the inner member 2, and the roller 12 is engaged with the wedge. If the roller 12 is to rotate faster than the outer ring 1
And the inner member 2 drives the outer ring 1 via the roller 12. On the other hand, when the outer ring 1 tries to rotate quickly in this state, the roller 12 does not engage, and the outer ring 1 can idle with respect to the inner member 2.

FIG. 8 also shows the case where the rotation direction is reversed.
Since the retainer 8 is delayed with respect to the inner member 2 as shown in (C), the same driving and idling functions as described above are exhibited.

The present applicant has filed Japanese Patent Application No. Hei 8-141749.
JP-A-8-150940, JP-A-8-172598 and the like have proposed a structure using an electromagnetic clutch as a rotation resistance applying means for a two-way clutch using a roller as an engaging element. 4 to 9 are denoted by the same reference numerals, and description thereof will be omitted.

FIGS. 11 and 12 show these rotation transmitting devices A.
Are shown below. The rotation transmitting device A holds the roller 12 by a torsion coil spring 17 so that the retainer 8 is neutral with respect to the inner member 2 and the cam surface 7.
Is held at the position shown in FIG.

In this state, a radial gap is secured between the space between the inner member 2 and the outer ring 1 and the roller 12.
The inner member 2 and the outer ring 1 can rotate relative to each other.

A disc-shaped armature 41 is fitted to the end of the retainer 8 so that the armature 41 cannot rotate relative to the retainer 8 and can slide in the axial direction. On the other hand, an electromagnetic coil 42 is inserted between the outer race 1 and the inner member 2 in parallel with the two-way clutch portion as shown in FIG. 11, and the electromagnetic coil 42 does not rotate with respect to the vehicle body via the fixed flange 43 and the like. Fixed to the site. A rotor 44 which is fitted around the electromagnetic coil 42 through an appropriate gap is press-fitted non-rotatably with a non-magnetic rotor guide 45, and the rotor guide 45 is
The rotation of the outer ring 1 is stopped. The armature 41 and the rotor 44 are set so as to form a gap b, so that the armature 41 and the rotor 44 can rotate relative to each other.

The rotation transmitting device A having the above-described configuration
When no current flows through the roller 2, the roller maintains the state shown in FIG. 8B, and the inner member 2 and the outer ring 1 can idle.
On the other hand, when a current flows through the coil 42, the armature 41 and the rotor 44 are pressed and integrated by the magnetic force of the electromagnetic coil 42.

When the outer ring 1 and the inner member 2 try to rotate relative to each other in this state, the retainer 8 rotates with the outer ring 1 via the armature 41 and the rotor 44 against the force of the torsion coil spring 17.

That is, the phases of the retainer 8 and the cam surface 7 are shifted, and the roller 12 is engaged with the inner member 2 and the outer ring 1 as shown in FIGS. Transmission of torque between the two is possible.

The rotation transmitting device A is mounted on a path for driving a driven wheel of a four-wheel drive vehicle, and the current to the electromagnetic coil 42 is electronically changed in real time according to a method of manually switching or a running condition of the vehicle. There is a controlled method, and 2WD-4WD can be switched as needed.

[0032]

In the above-described conventional roller-type two-way clutch, the roller 12 is provided in a wedge-shaped space surrounded by a cam surface formed on the shaft side and a cylindrical surface formed on the outer ring 1. Although it is configured so that the outer ring 1 can idle, it is a precondition that the roller 12 separates from the wedge and that a radial gap is formed between the roller 12 and the wedge-shaped space. For example, when the outer ring 1 idles in the direction of the arrow in FIG. 9A, the roller 12 separates from the wedge and moves in the neutral direction where a gap is formed, so that the roller 12 and the cam surface 7 of the outer ring 1 and the inner member 2 are moved. Does not contact, and can idle.

However, even when the roller 12 is completely at the neutral position as shown in FIG. 8B, the radial gap Y is small and is actually only about 0.1 mm. Therefore, the dimensional accuracy of the clutch component and the coaxiality between the inner member 2 and the outer ring 1 are set extremely strictly. If the gap Y is eliminated, the two-way clutch will not be able to idle (FIG. 9B). ). In addition, the accuracy and rigidity of components such as a bearing that supports the coaxial relationship between the inner member 2 and the outer ring 1 are also related to the gap, and when a large bending moment is applied between the inner member 2 and the outer ring 1, the bearing and the like are not affected. Due to the elastic deformation of the support member, the inner member 2 and the outer ring 1 may be eccentric, and the gap may be lost, so that the spinning may not be possible.

An object of the present invention is to provide a roller-type two-way clutch which does not impair the idling function even if a slight dimensional variation or a slight eccentricity between the shaft and the outer ring occurs.
A directional clutch is provided.

[0035]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, a first aspect of the present invention is to rotationally fit a shaft and an outer ring in and out, and to provide a plurality of cam surfaces on one of the opposing surfaces thereof. A cylindrical surface is provided on the other side, a wedge-shaped space is formed between the cylindrical surface and the cam surface, one of the shaft and the outer ring is used as an input member, the other is used as an output member, and a retainer is provided between the shaft and the outer ring. And a roller that engages with the wedge-shaped space when the retainer and the input-side member relatively rotate in the forward and reverse directions are incorporated into a pocket formed in the retainer, and the input-side member rotates in the retainer. Means for imparting rotational resistance in the opposite direction to the direction,
In a rotation transmitting device in which a means for switching the action direction or action or non-action of the rotation resistance is connected, a concave portion for preventing a roller from being involved in engagement near a central portion of a cam surface formed on a shaft or an outer ring. The configuration provided is adopted.

According to a second aspect of the present invention, in the first aspect of the present invention, the elastic member in which the rotation resistance applying means is hooked between the retainer and the input side member, and the retainer and the non-rotationally fixed portion are provided. It is composed of a friction generating member arranged between them, and adopts a configuration in which the action directions of both are switched by a one-way clutch.

According to a third aspect of the present invention, in the first aspect of the invention, the means for imparting rotation resistance is a disk-shaped armature which is fitted to the retainer so as to be non-rotatable and slidable in the axial direction.
It is composed of a friction member fixed to the outer ring and an electromagnetic coil fixed to a non-rotationally fixed part. The armature and the friction member are pressed against each other by the magnetic force of the electromagnetic coil, and resistance is given between the retainer and the outer ring by the friction force. The above configuration is adopted.

According to a fourth aspect of the present invention, there is provided the rotation transmitting device according to the third aspect, wherein the switching of the current supply to the electromagnetic coil is performed by a manual switch.

According to a fifth aspect of the present invention, in the third aspect of the present invention, the input / output rotation speeds of the rotation transmitting device are read by sensors, and the current flowing to the electromagnetic coil is automatically controlled according to the rotation speeds. The configuration is adopted.

Here, the concave portion provided near the center of the cam surface may be any shape as long as the roller is housed so as not to engage with the wedge, and may be formed in any shape such as an arc or a square.

[0041]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below with reference to FIGS.

The structure of the rotation transmitting device A using the two-way clutch 4 is as described in the section of the prior art with reference to FIGS. 4 to 12, and the rotation transmitting device A of the two-way clutch 4 of the present invention. Since the basic operation of the two-way clutch 4 is substantially the same, the structure of the two-way clutch 4 and its characteristic operation will be described here. Note that the same parts of the two-way clutch 4 as in the conventional example are denoted by the same reference numerals, and description thereof will be omitted.

As shown in FIGS. 1 to 3, the two-way clutch 4
Is provided with an arc-shaped concave portion 31 near the center of the cam surface 7 of the inner member 2 so as to prevent the roller 12 from engaging in engagement with the wedge when the roller 12 is received. The portion of the cam surface 7 that comes into contact with the roller 12 during driving is shown in FIG.
As shown in (A) and (C), almost both ends of the cam surface 7, and the vicinity of the center of the cam surface 7 (hereinafter, a neutral region) is not required at the time of driving. By providing the concave portion 31 in the neutral region, when the outer ring 1 idles with respect to the inner member 2, even if the inner member 2 and the outer ring 1 are slightly eccentric, as shown in FIG. When the neutral region is reached, a gap is created by the recess 31 so that the outer ring 1
Is not engaged with the roller 12 and can be idled as it is.

The shape of the concave portion 31 need not be an arc shape as shown in FIG. 2, but a notch shape as shown in FIG. 3A or a tapered shape as shown in FIG. But it is good.

[0045]

As described above, according to the present invention, the concave portion is provided near the center of the cam surface of the inner member (neutral region) to prevent the roller from participating in the engagement.
The dimensional accuracy of the components constituting the two-way clutch can be set loosely, and the reliability of the idling function can be increased, and the machining cost can be reduced. Further, even if a force such as a bending moment is applied from the outside and the members supporting the inner member and the outer ring are somewhat elastically deformed, the idling function of the two-way clutch is not impaired.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing an entire two-way clutch.

2A is a cross-sectional view showing one engagement state of a two-way clutch, FIG. 2B is a cross-sectional view in a neutral state, and FIG.
Is a sectional view showing the other engagement state of the two-way clutch.

FIGS. 3A and 3B are cross-sectional views showing another shape of a concave portion.

FIG. 4 is a plan view showing a mounted state of the rotation transmitting device.

FIG. 5 is a sectional view of a rotation transmission device.

FIG. 5 shows a conventional two-way clutch in the same as above.
VI-VI sectional view

FIG. 7 is a sectional view of a one-way clutch.

8 (A) and 8 (B) are cross-sectional views showing an engaged state of a conventional two-way clutch.

FIGS. 9A and 9B are cross-sectional views showing the operation of a conventional two-way clutch.

FIGS. 10A and 10B are cross-sectional views showing the operation of a conventional two-way clutch.

FIG. 11 is a sectional view showing another example of the rotation transmitting device.

FIG. 12 is a sectional view taken along the arrow XII-XII in FIG. 10;

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Outer ring 2 Inner member 4 2-way clutch 6 Cylindrical surface 7 Cam surface 8 Cage 11 Pocket 12 Roller 13 Spring 18 1-way clutch 31 Recess

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[Procedure amendment]

[Submission date] April 7, 1997

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] Fig. 8

[Correction method] Change

[Correction contents]

FIGS. 8A to 8C show a conventional two-way clutch, wherein FIGS. 8A and 8C are cross-sectional views showing an engaged state, and FIG. 8B is a cross-sectional view showing an idling state.

Claims (5)

[Claims] 1. A shaft and an outer ring are rotatably fitted inside and outside, and
A plurality of cam surfaces and a cylindrical surface are provided on one of the opposing surfaces to form a wedge-shaped space between the cylindrical surface and the cam surface,
One of the shaft and outer ring is an input member and the other is an output member,
A cage is provided between the shaft and the outer ring, and a roller that engages with the wedge-shaped space when the cage and the input-side member relatively rotate in the forward and reverse directions is incorporated into a pocket formed in the cage, In a rotation transmission device in which a means for imparting a rotational resistance in the opposite direction to the rotation of the input member to the retainer and a means for switching an action direction or an action or an inaction of the rotation resistance are connected to a shaft or an outer ring. A rotation transmitting device, wherein a concave portion is provided near a central portion of each of the formed cam surfaces so as to prevent a roller from participating in engagement. 2. The rotation resistance applying means comprises an elastic member hooked between the cage and the input side member, and a friction generating member formed between the cage and the non-rotationally fixed portion. The rotation transmitting device according to claim 1, wherein the operation direction is switched by a one-way clutch. 3. The rotation resistance applying means is fixed to a disc-shaped armature fitted to the retainer so as to be non-rotatable and slidable in the axial direction, a friction member fixed to the outer ring, and a non-rotationally fixed portion. 2. The rotation transmission device according to claim 1, wherein the armature and the friction member are pressed against each other by a magnetic force of the electromagnetic coil so that a resistance is given between the retainer and the outer ring by the frictional force. . 4. The rotation transmitting device according to claim 3,
A rotation transmission device characterized in that the switching of the current to the electromagnetic coil is switched by a manual switch. 5. The rotation transmission according to claim 3, wherein the input / output rotation speeds of the rotation transmission device are read by sensors, and the current flowing through the electromagnetic coil is automatically controlled according to the rotation speeds. apparatus.