JPH0633957A - Torque converter - Google Patents

Abstract

PURPOSE:To reduce the manufacturing cost of a torque converter which provides a holder with resistance to rotation and changes the direction of operation of an engaging part by simplifying the structure of the holder and that of the engaging part. CONSTITUTION:A cylindrical surface 6 and a cam surface, which form a wedge- shaped space, are formed on the opposite faces of an outer ring 1 and an inner member 2, respectively, and a roller 12 serving as an engaging element and a spring for holding the roller 12 in its neutral position are assembled into the pocket of a holder 8 provided between the opposite faces. A torsion coil spring 17 for applying torque to the holder is installed between the holder 8 and the inner member 2 and a rotation-resistance imparting means 22 is connected to an end portion of the holder 8 via a one-way clutch 18.

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, and is used, for example, for switching between transmission and interruption of driving force in a drive path of a vehicle.

[0002]

2. Description of the Related Art A rotation transmission device for switching a driving force for a front wheel and a rear wheel of a vehicle by a mechanical clutch so that a large driving force can be efficiently transmitted to a wheel even at a low speed.
The present applicant has proposed it by Japanese Patent Application No. 3-275715.

As shown in FIG. 13, this device has a rotatable first retainer 73 between an outer ring 71 and an inner member 72, which are rotatably supported, and a second retainer fixed to the inner member 72. A container 74 is provided, and a sprag 75 which is engaged by relative rotation of the outer ring 71 and the inner member 72 is incorporated in a pocket provided in each of the cages 73 and 74.

A pin 77 which is inserted into the pin hole 76 of the inner member 72 in the first retainer 73 with a clearance in the rotational direction.
The rotation resistance imparting means 80 using a rolling bearing 81 having a large rotation resistance is connected to the pin 77 via the operating shaft 78 and the pin 79.

Further, a one-way clutch 83 is provided between the rolling bearing 81 and the support case 82 connected to the fixed member.
A torsion spring 84 that applies a rotational force to the first retainer 73 in a direction opposite to the rotational direction in which the one-way clutch 83 is disengaged is attached between the operating shaft 78 and the inner member 72.

In the above structure, the first cage 73 is decelerated by the rotational resistance of the rotational resistance generating means 80 or the torsion spring 84, and the first cage 73 and the second cage 74 rotate relative to each other as shown in FIG. Then, the sprag 75 is tilted to a position where the outer ring 71 and the inner member 72 are engaged with each other to transmit and cut off the torque.

[0007]

By the way, in the above-mentioned proposed apparatus, as an engaging element for transmitting torque, as shown in FIG.
The sprag 75 engaging in the forward and reverse directions as shown in FIG.
Although the outer ring 71 or the inner member 72 is tilted in the rotating direction by using 74, in such a structure, both cages 73, 7
Pockets 8 for passing through sprags 75 respectively
Requires 5, 86, and each pocket 85, 8
The shape of 6 requires high accuracy in the pitch in the circumferential direction, phase, width dimension, etc. when inclining the sprags 75 at an appropriate angle, resulting in a high processing cost and in assembling parts. There is a problem that it is time-consuming.

Further, since the shape of the sprag 75 is complicated, there is a problem that the manufacturing cost thereof is relatively high.

Therefore, the present invention provides a rotation transmission device which realizes the function of a mechanical clutch for transmitting the driving force to the rotation in the forward and reverse directions without loss, simplification of the structure and reduction of the manufacturing cost. It is an object.

[0010]

In order to solve the above-mentioned problems, the present invention provides a cylindrical surface on one of the facing surfaces of an outer ring and an inner member fitted to the outer ring, and a cylindrical surface on the other. A plurality of cam surfaces forming a wedge-shaped space are formed, and a pocket of a cage provided between the facing surfaces of the outer ring and the inner member is provided between the cylindrical surface and each cam surface by relative rotation of the outer ring and the inner member. A roller that engages with the retainer, the retainer and the outer ring or inner member are rotatably connected through a gap in the rotational direction, and the retainer rotates between the retainer and the outer ring or inner member to which the retainer is connected. A retainer is provided with a rotational resistance generating means for generating a difference, and a one-way clutch for disconnecting the connection between the retainer and the rotational resistance generating means with respect to one direction rotation of the outer ring or the inner member connected to the retainer. What is the rotation direction in which the one-way clutch is disengaged? Connecting the elastic member for urging the retainer in a direction, the rotational resistance by the elastic member is the set smaller than the rotation resistance of the rotation resistance generating means relative to the cage.

[0011]

In the above structure, when the outer ring or the inner member rotates in one direction, the one-way clutch disconnects the retainer from the rotation resistance imparting means, and the elastic member biases the retainer and the outer ring. The inner member and the inner member are moved relative to each other in the circumferential direction to bring the roller into an engagement operation state between the cylindrical surface and the cam surface. Further, with respect to the rotation in the opposite direction to the above, the one-way clutch locks, the phase of the retainer is switched by the resistance of the rotation resistance adding means, and the roller is brought into the engagement operation state.

In the above structure, since the engaging element is a roller having a simple shape and only one retainer is required to operate the roller, the structure can be simplified and the manufacturing cost can be reduced. Further, since the roller only has to be rotationally moved toward the engagement position between the cylindrical surface and the cam surface, it is not necessary for the pocket of the cage to have a highly accurate phase and width dimension.

[0013]

1 to 5 show a first embodiment of the present invention. As shown in the drawing, an inner member 2 is rotatably fitted into the outer ring 1 via bearings 3 and 4, and an input ring 5 is inserted into the end of the inner member 2 via a spline.
Is installed.

A cylindrical surface 6 is formed on the inner diameter surface of the outer ring 1,
On the outer diameter surface of the inner member 2 facing it, a plurality of flat cam surfaces 7 are formed at a predetermined interval. Each of the cam surfaces 7 and the cylindrical surface 6 of the outer ring 1 forms a wedge-shaped space in which both sides in the circumferential direction are narrowed.

An annular retainer 8 fitted and guided by the inner member 2 is rotatably provided between the outer ring 1 and the inner member 2, and the retainer 8 has an inner member 2 therein. Pin hole 9 on the peripheral wall
The starter pin 10 inserted through is connected.

The cage 8 is formed with the same number of pockets 11 as the cam surface 7 in the circumferential direction, and each of the pockets 11 is formed.
A roller 12 as an engaging element and a spring 13 are incorporated in the. This roller 12 is provided on each cam surface 7 of the inner member 2.
Each of them is incorporated into the cam surface 7 and the cylindrical surface 6 when the cage 8 moves a predetermined amount in the circumferential direction.
The outer ring 1 and the inner member 2 are integrated with each other. Further, 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 form the cylindrical surface 6
However, when the cage 8 moves by a predetermined amount in the circumferential direction, the roller 12
Only the spring on one side acts on the roller 12 and presses the roller against the engagement surface.

Inside the inner member 2, the connecting pin 1 is fitted into two axial pin holes 14, 14 provided in the 180 degree direction.
5, 15 are inserted, and one end of each connecting pin 15, 15 is in contact with the starting pin 10 so that torque can be transmitted only in one direction of rotation.

The other ends of the connecting pins 15 and 15 are
It is press-fitted into an end surface hole 20 of an inner ring 19 of a one-way clutch 18 described later.

Further, the spring seat 1 is provided at the rear end of the inner member 2.
6 is fitted, and a torsion coil spring 17 is incorporated between the spring seat 16 and the inner diameter surface of the inner member 2. The torsion coil spring 17 has one end locked to the spring seat 16 and the other end locked to the starting pin 10, and the spring causes the starting pin 10 to move in a direction opposite to the direction of rotation by the connecting pins 15 and 15. The urging force to rotate is given.

On the other hand, the inner ring 19 which is connected to the connecting pins 15 and 15 constitutes a one-way clutch 18, and the one-way clutch 18 is connected with the rotation resistance applying means 22 via a clutch support ring 21. ing.

The rotation resistance applying means 22 includes a connecting rod 23.
The housing 24 connected to the vehicle body of the automobile via the
A friction pad 25 rotatably supported by an outer ring and an inner member by a bearing and press-fitted into the inner diameter of the housing 24 and a flange 26 provided on the clutch support ring 21 are rubbed against each other, and the friction pad 25 and the retaining ring 27 are A disc spring 28 is incorporated between them. The spring force of this disc spring 28 is
The friction pad 25 acts in a direction of being crimped to the flange 26, and by the crimping, a drag torque is generated in the rubbing portion 29, and the drag torque causes the inner ring 19 that tries to rotate together with the cage 8. On the other hand, it gives resistance to delay the rotation. Further, the rotational resistance force generated at the rubbing portion 29 is set to be larger than the rotational force applied to the retainer 8 by the torsion coil spring 17 described above.

The one-way clutch 18 has a cam ring 30 press-fitted into a clutch support ring 21 as shown in FIG.
A plurality of inclined cam surfaces 31 are formed on the inner periphery of the retainer 3 at regular intervals in the circumferential direction, and the cage 3 is provided between the cam surfaces 31 and the inner ring 19.
The small roller 33 held by 2 and the spring 34 for pressing the small roller 33 against the cam surface 31 and the inner ring 19 are assembled.

In the above structure, the inner member 2 and the connecting pin 1
By driving 5 and 15, the inner ring 19 of the one-way clutch 18
Is rotated in the direction of the arrow (b) in Fig. 3, the one-way clutch 1
8 is locked, the inner ring 19 and the clutch support ring 21 are integrated, and the drag torque of the rubbing portion 29 of the rotation resistance applying means 22 is applied to the connecting pin 15. Therefore, a force for stopping the rotation is applied to the starting pin 10 and the retainer 8, and the retainer 8 is decelerated with respect to the rotation of the inner member 2.

On the contrary, the inner ring 19 together with the inner member 2 is
When rotating in the direction (a), the one-way clutch 18 disengages from the inner ring 19, and the one-way clutch 18 idles.
For this reason, the resistance of the rotation resistance applying means 22 is equal to that of the connecting pin 1.
Although not transmitted to 5, 5, the torsion coil spring 17 gives the starting pin 10 a rotational force in a direction opposite to the above (a) direction, so that the spring force causes the cage 8 to decelerate with respect to the inner member 2. To be done.

As shown in FIG. 2, the actuating pin 10 connected to the retainer 8 is loosely fitted in the pin hole 9 formed in the peripheral wall of the inner member 2 with a clearance X in the rotational direction. , 15 and the axial clearance Y between the axial pin holes 14, 14 is defined by the connecting pins 15, 15.
0 is set to allow full rotation in the X gap.
The rotation direction clearance X determines the delay angle of the retainer 8 with respect to the inner member 2, and the magnitude thereof is from when the roller 12 contacts the cam surface 7 and the cylindrical surface 6 to the engagement position. It is set larger than the distance.

The rotation transmission device A of the embodiment has the above-mentioned structure, and when it is mounted on the drive path of the vehicle shown in FIG. 6, it branches from the transfer C to the input ring 5 of the inner member 2. The front wheel propulsion shaft D is connected, and the outer wheel 1 is connected to the front differential E.

The inner member 2 when the vehicle is traveling forward
Direction of rotation and the direction of arrow (a) in FIG. 3 (one-way clutch 1
8 is the direction in which it disengages), and the direction of rotation at the time of retreat and the direction of arrow (b) (the direction in which the one-way clutch 18 locks) are set to match.

In this state, when the vehicle travels forward, the inner member 2 starts to rotate due to the drive of the transfer C.
The cage 8 is provided with a torsion coil spring 17 via a start pin 10.
Due to the biasing force, the rotation of the starter pin 10 and the pin hole 9 is delayed by the clearance X in the rotational direction, and the inner member 2 starts to rotate. After that, the connecting pins 15 and 15 try to rotate the disc spring 28 of the rotation resistance applying means 22, but since the one-way clutch 18 is idling in this rotation direction, the disc spring 2
8 and the clutch support ring 21 do not rotate, and no rotation resistance is generated between them and the support case 24.

Therefore, by the action of the torsion coil spring 17, the cage 8 is held in a phase later than that of the inner member 2 as shown in FIG.

Contrary to the above, when the vehicle retreats, the inner member 2 first starts to rotate, whereas the cage 8 is moved to the inner member 2 by the urging force of the torsion coil spring 17. Try to rotate at the same time. However, in this rotational direction, the support ring 21 and the disc spring 28 rotate together because the one-way clutch 18 is locked.

In this case, the support ring 2 by the disc spring 28
1 and the friction pad 25 with the rotational resistance of the torsion coil spring 17
Since the rotation resistance is set to be larger than the rotation resistance due to, the cage 8 is decelerated by the rotation resistance as shown in FIG. 5, the rotation is delayed with respect to the inner member 2, and the roller 12 is brought into the engaged state. After that, the disc spring, the support ring, and the friction pad rotate while generating rotation resistance, and the state of FIG. 5 is maintained.

Considering the above operation in the actual running of the vehicle, the outer wheel 1 and the inner member 2 rotate at the same speed while the vehicle is running straight forward or backward in a normal state. The roller 12 is maintained in a meshing standby state. Therefore, the driving force is not transmitted from the inner member 2 to the outer wheel 1, and the two-wheel traveling is performed only with the rear wheels.

When the vehicle turns to have a steering angle and the front wheels and the outer wheels 1 connected thereto rotate faster than the rear wheels, the outer wheels 1 run over the rollers 12. Therefore, the rollers do not engage with each other, the front wheels and the rear wheels are separated and rotate, and tight corner braking does not occur.

On the other hand, when the rear wheel slips during traveling, the rotation of the inner member 2 connected to the transfer C increases with respect to the front wheel (outer wheel), so that the roller 12 engages with the cylindrical surface 6 and the cam surface 7. Then, the outer ring 1 and the inner member 2 are integrated. Therefore, the driving force is applied to the front wheels, and the four-wheel drive state is switched to.

7 and 8 show a second embodiment. In this example, each cam surface 7 in the structure of the first embodiment described above is used.
Two rollers 41 and 42 are arranged between the roller 41 and the cylindrical surface 6, and a spring 43 for urging the rollers 41 and 42 in a direction of separating the rollers is incorporated between the rollers 41 and 42.

In the above structure, as shown in FIG. 8, when the inner member 2 rotates in the direction of the arrow, the cage 44 that decelerates is
The one roller 41 is separated from the engagement position, and the other roller 42 is urged via the spring 43.
Press 2 into the engagement position.

On the other hand, FIGS. 9 to 11 show a third embodiment. In this example, unlike the first embodiment,
The outer ring is on the input side and the inner member is on the output side.
As shown in FIG. 9, the input flange 53 is provided at the end of the outer ring 51.
, And an output ring 54 is attached to the end of the inner member 52.

As shown in FIG. 11, a plurality of polygonal cam surfaces 55 are formed on the inner diameter surface of the outer ring 51, and a cylindrical surface 56 is formed on the outer diameter surface of the inner member 52 facing the cam surfaces 55. An annular cage 57 is incorporated between the cylindrical surface 56 and the cam surface 55. The cage 57 is rotatably fitted to the outer ring 51, and is fitted in a pocket 58 provided on the peripheral surface of the cage 57, which engages with the cam surface 55 and the cylindrical surface 56 by rotating in the forward and reverse directions. And a spring 13 that holds the roller 12 in a neutral position.

On the other hand, the rear end of the retainer 57 is rotatably supported between the outer ring 51 and the inner member 52 by a bearing 59 having a two-layer structure, and its extension is integrated with the inner ring 60 of the one-way clutch 18. The one-way clutch 18 is connected with the rotation resistance applying means 22.

Further, at the front end of the retainer 57, 18
Two notches 61 and 62 are formed facing each other in the 0 degree direction, and fixing pins 63 and 64 press-fitted into the input flange 53 of the outer ring 51 are fitted into the notches 61 and 62, respectively. Further, both ends of a C-shaped ring spring 65 are respectively locked between the end wall of the one notch 61 and the one fixing pin 63, and the one-way clutch 18 is locked by the ring spring 65. Rotational force in a direction opposite to the rotational direction in which the retainer is operated is applied to the retainer 57.

The other fixing pin 64, which is not locked by the ring spring 65, has a clearance X in the rotational direction with respect to the notch 62.
And the size of the gap X in the rotational direction is set to be larger than the distance from the neutral position of the roller 12 to the engagement position.

The rotation transmitting device B of the third embodiment as described above.
Is mounted on the drive path of the vehicle as shown in FIG.
The input flange 53 of the outer ring 51 is connected to the transfer C via the front wheel propulsion shaft D, and the output ring 54 of the inner member 52 is connected to the front differential E (in this case, the direction of the transmission device B is as shown in FIG. 6). It is the opposite of the device A shown in FIG.

In the above structure, the outer ring 51 and the fixing pin 6 are
When the cage 57 and the inner ring 60 of the one-way clutch 18 rotate in one direction via 3, 64, the one-way clutch 18 is locked, and the rotational resistance of the rotational resistance imparting means 22 is given to the cage, so that the cage 57 becomes The speed is reduced with respect to the outer ring 51.

On the contrary, when the outer ring 51 and the retainer 57 rotate in the opposite direction to the above, the one-way clutch 18 is disengaged and the retainer 57 and the rotation resistance applying means 22 are disconnected. At this time, the ring spring 65 applies a rotational force to the cage 57 in a direction opposite to the above direction, and the urging force decelerates the cage 57 with respect to the outer ring 51 in the rotational direction.

In the structure of the above third embodiment,
As shown in FIG. 12, two rollers 41 and 42 and a spring 43 are incorporated between each cam surface 55 and the cylindrical surface 56, and the rollers 41 and 42 are alternately arranged between the cam surface 55 and the cylindrical surface 56. You may make it engage.

Further, in each of the above embodiments, the rotation resistance imparting means for providing a rotation difference between the cage and the inner member or the outer ring is not limited to the structure using the disc spring and the friction pad described above, but a gear is used. Any other mechanism such as the speed reducer used can be utilized.

[0047]

As described above, according to the present invention, since the roller is used as the engaging element and the number of the retainer for operating the roller is one, and the high machining accuracy for the pocket of the retainer is not required, the structure is simplified. And a reduction in manufacturing cost, and there is an effect that a rotation transmission device that switches between transmission and interruption of drive torque by a mechanical clutch can be provided at low cost.

[Brief description of drawings]

FIG. 1 is a vertical sectional front view showing a first embodiment.

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

FIG. 3 is a sectional view showing the one-way clutch of the above.

FIG. 4 is a sectional view showing an operating state of the same roller.

FIG. 5 is a cross-sectional view showing an operating state in the opposite direction of FIG.

FIG. 6 is a diagram schematically showing a drive path of a vehicle.

FIG. 7 is a sectional view showing a second embodiment.

FIG. 8 is a sectional view showing an operating state of the above.

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

10 is a sectional view taken along line XX of FIG.

FIG. 11 is a sectional view taken along line XI-XI of FIG.

FIG. 12 is a sectional view showing another embodiment of the above.

FIG. 13 is a vertical sectional front view showing a conventional example.

FIG. 14 is a sectional view showing an operating state of the above sprag.

[Explanation of symbols]

 1, 51 Outer ring 2, 52 Inner member 6, 56 Cylindrical surface 7, 55 Cam surface 8, 44, 57 Cage 11, 58 Pocket 12, 41, 42 Roller 13, 43 Spring 17 Torsion coil spring 18 One-way clutch 22 Rotation Resistance imparting means 63, 64 Fixed pin 65 Ring spring A, B Rotation transmission device X Rotation direction clearance

Claims (1)

[Claims] 1. A cylindrical surface is formed on one of opposing surfaces of an outer ring and an inner member fitted to the outer ring, and a plurality of cam surfaces forming a wedge-shaped space with the cylindrical surface is formed on the other side of the outer ring, A roller that engages between the cylindrical surface and each cam surface by the relative rotation of the outer ring and the inner member is incorporated into a pocket of the cage provided between the facing surfaces of the inner member, and the cage and the outer ring or the inner side. A member is rotatably connected to the member through a gap in the rotation direction, and rotation resistance generating means for generating a rotation difference is provided between the holder and the outer ring or the inner member to which the holder is connected, and the holder is connected. A one-way clutch for disconnecting the connection between the retainer and the rotation resistance generating means for one-way rotation of the outer ring or the inner member is provided, and the retainer is provided in a direction opposite to the rotation direction in which the one-way clutch is disengaged and operated. Connect the elastic member that urges the cage to the cage. On the other hand, a rotation transmission device in which the rotation resistance of the elastic member is set to be smaller than the rotation resistance of the rotation resistance generating means.