JP3095482B2 - Rotation transmission device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotation transmitting device, and is used, for example, for switching between transmission and interruption of a driving force on a driving path of a vehicle.

[0002]

2. Description of the Related Art In a drive path of a vehicle, the applicant of the present invention has disclosed a device in which transmission and disconnection of driving force to front wheels and rear wheels are switched by a mechanical clutch.
No. 0 proposes.

As shown in FIG. 12, this device rotatably supports an outer ring 82 on an inner member 81, and a small-diameter retainer 83 fixed to the inner member 81 between the two. A large-diameter retainer 84 is provided, and sprags 85 are incorporated in pockets provided in both retainers 83 and 84.

[0004] A pin 87 is inserted into the large-diameter retainer 84 through a pin hole 86 of the inner member 81 with a clearance in the rotational direction.
And the pin 87 is connected via a shaft 88 and a pin 89 to a rotational resistance applying means 90 using a bearing having a large rotational resistance.

In the above-mentioned rotation transmitting device B, an inner member 81 is connected to a front wheel propulsion shaft D branching from a transfer C, and an outer wheel 82 is connected to a front differential E in a vehicle driving path as shown in FIG. Is attached. In the structure mounted in this manner, when the inner member 81 rotates, the small-diameter retainer 83 integrated with the input shaft 81 starts to rotate inside the transmission device B, whereas the large-diameter retainer 84 provides rotation resistance. The rotation of the input shaft 81 is delayed by the rotation resistance applied from the means 90, and the sprag 85 is tilted to the engagement position as shown in FIG.

In this state, when the rear wheel slips during traveling, the inner member 81 tries to rotate faster than the outer wheel 82, and the sprag 85 engages to transmit driving force to the front wheel.

As described above, when the vehicle moves forward or backward, the rotation transmitting device B delays the rotation of the large-diameter retainer 84 by the resistance of the rotational resistance applying means 90 so that the two retainers 8 can rotate.
The phase of the sprags 85 is changed by changing the phases of the sprags 85.

The rotation resistance applying means 90 is not limited to the illustrated rolling bearing, but may be a brake mechanism for decelerating by sliding contact with a friction member, a deceleration mechanism using gears, or the like.

[0009]

However, in the above-described apparatus, the large-diameter retainer 84 is always decelerated by the rotation resistance applying means 90 during traveling of the vehicle, so that the engine torque is not transmitted to the wheels. However, there is a problem that power loss easily occurs.

[0010] Further, during high-speed running or long-time running,
Heat is generated from sliding parts such as bearings, and it is necessary to pay attention to the durable life due to wear of parts.

SUMMARY OF THE INVENTION It is an object of the present invention to provide a rotation transmission device which enables a rotation resistance applying means to operate only in one direction of rotation, thereby reducing power loss and improving durability.

[0012]

Means for Solving the Problems To solve the above-mentioned problems, a first means of the present invention is to provide a retainer and a rotational resistance in one direction of rotation of an outer ring or an inner member connected to the retainer. Providing a one-way clutch that disconnects the connection state with the applying means, connecting the retainer to an elastic member that biases the retainer in a direction opposite to the rotation direction in which the one-way clutch is released and operated,
The rotation resistance due to the bias of the elastic member is set smaller than the rotation resistance of the rotation resistance applying means.

[0013] The second means of the present invention is to change the connection state between the outer ring or the inner member and the rotation resistance applying means in one direction of rotation of the outer ring or the inner member to which the cage is connected. A one-way clutch for disengagement is provided, and an elastic member for urging the outer ring or the inner member in a direction opposite to the rotation direction in which the one-way clutch is disengaged is connected to the outer ring or the inner member, and the elastic member is attached. A structure is adopted in which the rotational resistance due to the force is set smaller than the rotational resistance of the rotational resistance applying means.

[0014]

In the first and second means, when the vehicle travels in one direction (for example, during forward traveling), the connection state of the rotation resistance applying means is disconnected by the one-way clutch, and the elastic member is biased. The retainer and the outer ring or the inner member are relatively moved, and the engagement element is brought into the engagement operation state.

When the vehicle runs in the reverse direction (during reverse), the one-way clutch is locked, and the phase of the retainer is switched by the resistance of the rotation resistance applying means.

[0016]

1 to 5 show a rotation transmitting device according to a first embodiment. As shown in FIG. 1, inside the outer race 1,
An inner member 2 formed of a hollow shaft is rotatably fitted via bearings 3 and 3, and an input ring 5 is attached to an end of the inner member 2 by engagement of a spline 4.

As shown in FIG. 2, concentric cylindrical surfaces 6 and 7 are formed on the inner diameter surface of the outer race 1 and the outer diameter surface of the inner member 2 opposed thereto. Between the surfaces 6, 7, two retainers 8, 9 of different diameter are integrated.
Of the two retainers, the retainer 8 on the small diameter side is
0, the retainer 9 on the large diameter side is fixed to the inner member 2.
A start pin 12 inserted through a pin hole 11 in the peripheral wall of the inner member 2 is connected to the large-diameter holder 9 so as to be rotatably fitted between the small-diameter side retainer 8 and the inner member 2. I have.

A plurality of pockets 13 and 14 are formed in the small-diameter side cage 8 and the large-diameter side cage 9 so as to face each other in the circumferential direction, and each of the pockets 13 and 14 has a sprag 15 as an engaging element. And the spring material 16 are incorporated.

This sprag 15 is, as shown in FIG.
The outer diameter side and the inner diameter side are formed by arcuate surfaces 17, 17 having a center of curvature on the center line of the sprag, and when inclined at a predetermined angle in both the left and right directions, they engage with both engagement surfaces 6, 7 to inwardly engage the outer ring 1 and the inner side. The member 2 is integrated. Further, the spring member 16 is supported by the large-diameter side retainer 9, and provides an elastic force for pressing each sprag 15 from both sides and holding the sprag 15 at a neutral position where the sprags 15 are not engaged with the engagement surfaces 6 and 7.

On the other hand, inside the inner member 2, bearings 18,
An operating shaft 19 is rotatably supported via 18, and a starting pin 12 connected to the large-diameter side retainer 9 is connected to a central portion of the operating shaft 19. The end of the operating shaft 19 has a connecting pin 2 inserted through a pin hole 20 at the end of the inner member 2.
The rotation resistance applying means 22 is connected to an end of the connection pin 21.

As shown in FIGS. 1 and 3, the rotation resistance applying means 22 comprises a differential bearing 23 composed of a rolling bearing and a support case 24 for supporting the bearing 23. It is connected to a fixing member (not shown) such as a differential case via a rod 32. Differential bearing 23
Is fitted into the support case 24 by applying a preload equal to or more than a specified pressure so that the radial gap becomes zero or more, and has a larger rotational resistance than the bearings 3 that support the inner member 2 during rolling. Is set.

The differential bearing 23 and the supporting case 2
4, a one-way clutch 25 for disengaging the two.
Is provided. In the one-way clutch 25, a plurality of inclined cam surfaces 27 are formed at regular intervals in the circumferential direction on the inner periphery of a cam ring 26 press-fitted into the support case 24, and between the cam ring 27 and the outer ring 23a of the differential bearing 23. Is provided with an annular retainer 28, and in a pocket provided in the retainer 28,
Roller 29, the roller 29, the cam surface 27 and the outer ring 23
and a spring 30 for pressing against the surface of a.

In the above structure, when the differential bearing 23 rotates in the direction shown by the arrow B in FIG. 3 via the inner member 2, the roller 29 of the one-way clutch 25 meshes with the cam surface 27 and the surface of the outer ring 23a to fix the roller. The outer ring 23a is integrated with the support case 24, and the rotational resistance of the differential bearing 23 is given to the connecting pin 21. Therefore, a force is applied to the operation shaft 19 and the large-diameter side cage 9 so as to suppress the rotation, and the large-diameter side cage 9 is decelerated with respect to the rotation of the inner member 2.

Conversely, when the operating bearing 23 is rotated through the inner member 2 in the direction of arrow A in FIG.
And the outer ring 23a of the differential bearing 23 idles.
For this reason, the rotational resistance of the differential bearing 23 is not transmitted to the operating shaft 19, and the connection state between the large diameter side cage 9 and the rotational resistance applying means 22 is disconnected.

A torsion coil spring 31 is fitted around the outer periphery of the operating shaft 19, and one end of the coil spring 31 is connected to the operating shaft 19 and the other end is connected to the inner member 2. The coil spring 31 applies a torsional force to the operating shaft 19 in a direction opposite to the rotational direction in which the one-way clutch 25 is disengaged (in the direction of arrow B). 9 is given a rotational resistance to the inner member 2 to decelerate. Further, the coil spring 3
1 is that the rotational resistance due to the urging force is
Is set so as to be smaller than the rotation resistance at which the rotation occurs.

Also, as shown in FIG.
Of the inner member 2 is loosely fitted in the pin hole 11 of the inner member 2 with a clearance X in the rotational direction. Between the pin 21 connected to the rotation resistance applying means 22 and the pin hole 20, A circumferential gap larger than the rotational gap X is provided. The above-mentioned rotational gap X determines the delay angle of the large-diameter side cage 9 with respect to the small-diameter side cage 8, and its size is determined by the sprag 15 from the neutral position between the engagement surfaces 6 and 7 to the spring material 16. The distance is set to be longer than the distance until the two contact surfaces come into contact with each other.

The rotation transmitting device A according to the embodiment has the above-described configuration, and is mounted on the drive path of the vehicle shown in FIG. 6 by branching 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 shaft 1 is connected to the front differential E.

The direction of rotation of the inner member 2 during forward running of the vehicle and the direction of arrow A in FIG.
The direction in which the one-way clutch 25 is locked) is set to match the direction of rotation when the vehicle retreats, and the direction of arrow B (the direction in which the one-way clutch 25 is locked). When the vehicle moves forward in this state, the inner member 2 starts to rotate by the drive of the transfer C, and the small-diameter side retainer 8 integrated with the inner member 2 simultaneously starts to rotate. On the other hand, since the large-diameter side retainer 9 is connected to the operating shaft 19 via the activation pin 12, the biasing force of the torsion coil spring 31 causes the rotation direction gap X between the activation pin 12 and the pin hole 11 to be equal. The rotation starts after the inner member 2. After that, the connecting pin 21 tries to rotate the inner ring of the differential bearing 23 of the rotation resistance applying means 22, but in this rotation direction, the one-way clutch 25 is idling, so that the differential bearing 23 It rotates and does not generate rotation resistance with the support case 24.

For this reason, as shown in FIG. 5, the small-diameter side cage 8 is moved by the action of the coil spring 31 to the large-diameter side cage 9.
The sprags 15 are kept in a later phase than the sprags 15, and the sprags 15 are put on standby in the engagement operation state.

Contrary to the above, when the vehicle retreats, first, the inner member 2 and the small diameter side retainer 8 connected thereto start to rotate. On the other hand, the large-diameter side retainer 9 tries to rotate simultaneously with the inner member 2 by the urging force of the coil spring 31, but this rotation direction is the one-way clutch 25 in the locked state. And the inner ring of the differential bearing 23 rotate together.

In this case, since the rotational resistance of the differential bearing 23 is set to be larger than the rotational resistance of the coil spring 31, the large diameter side cage 9 is decelerated by the resistance of the differential bearing 24 as shown in FIG. The rotation is delayed with respect to the inner member 2 and the small-diameter side retainer 8, and the sprag 15 is inclined to the engaged state.
Thereafter, the differential bearing 23 rotates while generating rotation resistance, and maintains the state of FIG.

As described above, in the forward running state which occupies most of the running mode of the vehicle, when the differential bearing 23 idles and only the urging force of the coil spring 31 acts, the running mode is small and the vehicle does not run at high speed. Thus, the differential bearing 23 rotates while generating resistance. For this reason, even if it rotates at a high speed during forward movement, no heat is generated from the bearings and the like, and the durability of the differential bearing 23 is improved.

In the above structure, the outer wheel 1 and the inner member 2 rotate at the same speed while the vehicle is running straight in the forward or backward direction in a normal state. The sprags 15 rotate together with 8 and 9, and the sprags 15 are maintained in a meshing standby state. For this reason, from the inner member 2 to the outer ring 1
No driving force is transmitted to the vehicle, and the vehicle is driven by two wheels with only the rear wheels.

When the vehicle turns and has a steering angle, and the front wheel and the outer wheel 1 connected thereto rotate faster than the rear wheel, the outer wheel 1 runs over the sprag 15.

As a result, the sprags 15 do not engage, the front wheels and the rear wheels are separated and rotate, and the braking phenomenon at the tight corner does not occur.

On the other hand, if the rear wheel slips during traveling, the front wheel (outer wheel 1) decelerates as the vehicle speed decreases.
Since the rotation of the inner member 2 connected to the transfer C exceeds the rotation, the sprag 15 is engaged with the engagement surfaces 6 and 7, and the outer ring 1 and the inner member 2 are integrated. Therefore, a driving force is applied to the front wheels, and the state is switched to the four-wheel drive state.

FIGS. 7 and 9 show a second embodiment. In this example, frictional members 41 and 42 that are in sliding contact with each other are provided as members that generate rotational resistance, instead of differential bearings.
A one-way clutch 45 is provided between the inner friction pad 42 and a connection pin 44 connected to the operation shaft 43.

In this structure, when the inner member 46 rotates in the backward direction of the vehicle (the direction of the arrow B), the one-way clutch 45 is rotated.
Are locked, and the friction pads 41 and 42 are in sliding contact with each other to generate rotation resistance. Conversely, when the inner member 46 rotates in the forward direction (the direction of arrow A), the one-way clutch 45 is disengaged, and the friction pad 42 does not rotate. For this reason, the friction pads 41 and 42 do not slide while the vehicle is moving forward, and wear is prevented.

Further, as shown in FIG.
The fixing pin 50 for fixing the pin is inserted through a pin hole 51 provided in the large-diameter cage 49 so as to protrude outward, and a tension coil spring 53 is attached between the fixing pin 50 and the starting pin 52. This tension coil spring 53 urges the large-diameter retainer 49 to have a phase delayed with respect to the small-diameter retainer 48 when the vehicle moves forward (rotation in the direction of arrow A in FIG. 9). The rotation resistance due to the urging force is set smaller than the rotation resistance between the friction pads 41 and 42.

In a normal state, between the fixing pin 50 and the pin hole 51 and between the starting pin 52 and the pin hole 54,
Each has a clearance X, X in the rotation direction.
A play for generating a phase difference between 8 and 49 is provided.

Since other structures and operations are the same as those of the first embodiment, the same components are denoted by the same reference numerals and description thereof is omitted.

FIGS. 10 and 11 show a third embodiment. In this example, the inner member 61 and the input wheel 62 are connected to each other by a spline 63 having a gap in the rotation direction, and the rotation resistance applying means 64 is connected to the inner member 61 in the structure of the first embodiment. Is mounted. Further, one end of the operating shaft 66 is fixed to the input ring 62, and the starting pin 67 attached to the operating shaft 66 is attached to the outer ring 68 and the inner member 6.
1 is connected to the small-diameter side retainer 69 incorporated between the two. Since the other structure is the same as that of the first embodiment, the same components are denoted by the same reference numerals and description thereof will be omitted.

In the above structure, the small-diameter retainer 69 starts to rotate at the same time as the input ring 62 rotates, but the inner member 61 and the large-diameter retainer 70 rotate with a delay due to the rotational resistance of the differential bearing 65. Then, the sprag 15 is tilted to the engagement operation state.

In each of the embodiments described above, the inner member is used as the input side, and each retainer is connected to the inner member. However, each retainer is connected to the outer ring, and the outer ring is used as the input side. ,
The same operation as described above can be obtained.

Although the sprags 15 that engage in the forward and reverse directions are shown as the engaging elements that engage the outer ring and the inner member, sprags that engage in only one direction are used symmetrically instead. Alternatively, an engaging element such as a roller may be used.

Further, the rotation resistance imparting means for providing a rotational difference between the retainer and the inner member is not limited to using the above-described differential bearing or friction material, but may be any other optional device such as a speed reduction mechanism using gears. The mechanism described above can also be used.

[0047]

As described above, according to the present invention, the rotation resistance applying means is operated only in one direction of rotation, and the rotation resistance is applied in the other direction of rotation by the urging force of the elastic member. In addition, the transmission and disconnection of the driving force by the free running function of the mechanical clutch can be switched in the same manner as in the conventional structure, and the frequency of using the rotational resistance applying means can be reduced. Therefore, there is an effect that heat generation at the time of high-speed rotation and a power loss of torque transmission can be reduced, and the durability life can be significantly improved.

[Brief description of the drawings]

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

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

FIG. 3 is an enlarged sectional view taken along line III-III in FIG. 1;

FIG. 4 is a cross-sectional view showing an operation state of a sprag during forward movement.

FIG. 5 is a sectional view showing an operation state of a sprag when the sprag is retracted;

FIG. 6 is a diagram showing an example of attachment to a vehicle.

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

FIG. 8 is a sectional view taken along the line VIII-VIII in FIG. 7;

9 is a sectional view taken along the line IX-IX in FIG.

FIG. 10 is a longitudinal sectional front view showing a third embodiment.

FIG. 11 is a cross-sectional view showing the spline engagement portion of the above.

FIG. 12 is a longitudinal sectional front view showing a conventional example.

FIG. 13 is a sectional view showing an operation state of the sprag according to the first embodiment;

[Explanation of symbols]

 1, 47, 68 Outer ring 2, 46, 61 Inner member 6, 7 Engagement surface 8, 48, 69 Small-diameter side retainer 9, 49, 70 Large-diameter side retainer 15 Sprag 22, 64 Rotational resistance applying means 23, 65 differential bearing 25, 45 one-way clutch 31 torsion coil spring 41, 42 friction pad 53 tension coil spring

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-3-14924 (JP, A) JP-A-4-211731 (JP, A) JP-A-60-241532 (JP, A) JP-A-3- 113131 (JP, A) Japanese Utility Model 3-11133 (JP, U) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16D 41/00-47/06 B60K 17/34

Claims (2)

(57) [Claims] 1. An engaging element is engaged between an outer ring and an inner member fitted thereto by a relative rotation of the outer ring or the inner member in the forward and reverse directions between the outer ring and an inner member. A retainer is incorporated, and the retainer and the outer ring or the inner member are rotatably connected to each other via a clearance in the rotational direction, and a rotation difference is generated between the retainer and the outer ring or the inner member to which the retainer is connected. A rotation transmission device provided with a rotation resistance applying means for causing the retainer to be connected to the outer ring or the inner member in one direction of rotation in a one-way rotation direction. And an elastic member for urging the retainer in a direction opposite to the rotational direction in which the one-way clutch is disengaged and operated, and the rotational resistance caused by the urging of the elastic member is applied to the rotational resistance applying means. Smaller than the rotational resistance of A rotation transmission device, characterized in that: 2. An engaging element is engaged between an outer ring and an inner member fitted thereto by a relative rotation of the outer ring or the inner member in a forward / reverse direction between the outer ring and an opposing surface of the inner member. A retainer is incorporated, and the retainer and the outer ring or the inner member are rotatably connected to each other via a clearance in the rotational direction, and a rotation difference is generated between the retainer and the outer ring or the inner member to which the retainer is connected. In the rotation transmitting device provided with a rotation resistance applying means for causing the outer ring or the inner member to be connected to the rotation resistance applying means in one direction of rotation of the outer ring or the inner member connected to the retainer. A one-way clutch for disconnecting is provided, and an elastic member for urging the outer ring or the inner member in a direction opposite to the rotation direction in which the one-way clutch is disengaged is connected to the outer ring or the inner member, and the elastic member is attached to the outer ring or the inner member. The rotational resistance caused by the force A rotation transmission device characterized in that the rotation transmission device is set smaller than the rotation resistance of the resistance applying means.