JPH05118359A - Rotation transmitting device - Google Patents

Abstract

PURPOSE:To arbitrarily select acting and stopping conditions of a clutch, in a rotation transmitting device for switching engagement of an outer ring with an inner member by a free running function of the mechanical clutch. CONSTITUTION:A sprag 15 engaged between engaging surfaces 6, 7 is built in retainers 8, 9 provided between an outer ring 1 and an inner member 2, and the large diameter side retainer 9 is connected to a differential means 22 of giving rotational resistance. A connecting means 26 comprising a drive cylinder 29 and a connecting cylinder 28 is provided between the outer ring 1 and the inner member 2. In order to obtain a free running function, the outer ring is disconnected from the inner member. On the other hand, when both the outer ring and the inner member are connected by the connecting means 26, movement of the sprag 15 is fixed, and a clutch is not actuated.

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 transmission / interruption switching of a driving force on a driving path of a vehicle.

[0002]

2. Description of the Related Art The applicant of the present invention has proposed a rotation transmission device in a drive path of a vehicle in which transmission and interruption of a driving force to front wheels and rear wheels are switched by a mechanical clutch.
-9910.

This apparatus, as shown in FIG. 8, rotatably supports an outer ring 42 on an inner member 41, and between the two,
A small-diameter retainer 43 fixed to the inner member 41 and a rotatable large-diameter retainer 44 are provided, and a sprag 45 is incorporated in a pocket provided in both the retainers 43, 44.

A pin 47 which is inserted into the large-diameter cage 44 through the pin hole 46 of the inner member 41 with a clearance in the rotational direction.
, And a differential bearing 50 having a large rotational resistance is connected to the pin 47 via a shaft 48 and a pin 49.

The transmission device B described above transfers the inner member 41 to the transfer C in a vehicle drive path as shown in FIG.
The outer ring 42 is connected to the front differential E and is attached to the front wheel propulsion shaft D branched from the front differential E. In the structure thus mounted, when the inner member 41 rotates, the small-diameter cage 43 integrated with the inner member 41 starts to rotate inside the transmission device B, whereas the large-diameter cage 44 has a differential structure. Due to the resistance of the bearing 50, the rotation of the inner member 41 is delayed and the sprag is inclined to the engagement position as shown in FIG.

When the vehicle travels straight in the above state, it seems that the front wheels and the rear wheels rotate at the same speed and the inner member 41 and the outer wheel 42 rotate at the same speed. Slight slippage occurs on the wheel, causing engagement of the sprag 45. For this reason, the driving force is transmitted to the front wheels, resulting in four-wheel drive.

When the rear wheel slips during traveling, the inner member 41 naturally tries to rotate faster than the outer wheel 42, so that the sprag 45 is engaged and the driving force is transmitted to the front wheel.
On the other hand, when the vehicle turns and has a steering angle, the front wheels rotate faster than the rear wheels, but the outer wheel 42 overruns the sprags 45, so that the clutch is not engaged and the braking phenomenon at the tight corner does not occur. ..

As described above, the transmission device B is characterized by instantaneously switching the connection between the front wheels and the rear wheels by the free running function of the mechanical clutch and switching between the four-wheel drive and the two-wheel drive.

[0009]

However, in the above transmission device, when the clutch becomes free running during straight running or turning, the front wheels are completely disconnected from the drive system, and the reverse input from the front wheels is transmitted to the drive system. There is no state.

Therefore, for example, when traveling at a slow speed with the engine brake applied on an icy road or a snowy road, the frictional force generated between the front wheels and the road surface is not transmitted to the drive system and the rear wheels are not transmitted. It becomes only engine brake,
It does not contribute to the increase of the braking force.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a rotation transmission device capable of restraining the function of a mechanical clutch according to the use condition and improving the braking force.

[0012]

In order to solve the above-mentioned problems, the present invention provides an outer ring between an outer ring and an inner member fitted to the outer ring by means of relative rotation between the outer ring and the inner member. And a retainer to be engaged between the opposing surfaces of the inner member and the retainer, and the retainer and the outer ring or the inner member are rotatably connected to each other through a gap in the rotation direction, and the retainer and the outer ring to which the retainer is connected. Alternatively, a structure is provided in which differential means for producing a rotation difference is provided between the inner member and the inner member, and coupling means for connecting and disconnecting the outer ring and the inner member is provided.

Here, the coupling means includes a coupling member that engages and disengages the outer ring and the inner member, a drive member that moves the coupling member in an engaging direction, and a biasing force that disengages the coupling member. The elastic member may be a structure that includes the elastic member.

[0014]

In the above structure, when the outer ring and the inner member are separated from each other, the operation of the engaging element becomes free and the free running function of the mechanical clutch can be obtained. Further, when the outer ring and the inner member are joined by the joining means, the engaging element does not operate and the mechanical clutch does not operate.

When incorporated in the drive path of the vehicle, the outer wheel and the inner member are separated during normal traveling, the drive of the four wheels and the two wheels is switched by the operation of the clutch, and when braking by engine braking, the inner wheel and the inner wheel are disconnected. The front wheels and the rear wheels are directly connected by connecting the four side members, and braking is performed by the four wheels.

[0016]

1 to 6 show a rotation transmission device of an embodiment. As shown in FIG. 1, an inner member 2 of a hollow shaft is rotatably fitted inside an outer ring 1 via bearings 3 and, and an end portion of the inner member 2 is engaged with a spline tooth 4 by means of engagement. An input ring 5 that is connected to an external member is attached.

As shown in FIG. 2, engagement surfaces 6 and 7 which are concentric cylindrical surfaces are formed on the inner diameter surface of the outer ring 1 and the outer diameter surface of the inner member 2 which faces the inner ring surface. Two cages 8 and 9 having different diameters are incorporated between the surfaces 6 and 7.
Of these cages, the cage 8 on the small diameter side is fixed to the inner member 2 by a pin 10, and the cage 9 on the large diameter side rotates between the cage 8 on the small diameter side and the inner member 2. A pin 12 inserted through a pin hole 11 of the output shaft 2 is connected to the large-diameter side retainer 9 that is fitted as much as possible.

A plurality of pockets 13 and 14 are formed in the small-diameter side retainer 8 and the large-diameter side retainer 9 so as to face each other in the circumferential direction, and a sprag 15 as an engaging element is provided in each of the pockets 13 and 14. 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 and 17 having a center of curvature on the center line of the sprag, and when they are inclined at a predetermined angle in both left and right directions, they engage both engaging surfaces 6 and 7 and the outer ring 1 and the inner side The member (input shaft) 2 is integrated. Further, the spring member 16 is supported by the large-diameter side retainer 9 and applies an elastic force that presses each sprag 15 from both sides and holds it at a neutral position where it does not engage with both engaging surfaces 6 and 7.

Inside the inner member 2, an operating shaft 19 is rotatably supported via bearings 18, 18, and the operating shaft 1
A pin 12 connected to the large-diameter side retainer 9 is connected to the central portion of 9. In addition, a pin 21 that is inserted through the pin hole 20 at the end of the inner member 2 is attached to the end of the operating shaft 19,
Differential means 22 is connected to the end of the pin 21.

This differential means 22 includes a rolling bearing 23,
The support case 24 supports the bearing 23, and the support case 24 is connected to a fixing member (not shown) such as a differential case via a connecting rod 25. Rolling bearing 2
3 is fitted into the support case 24 by applying a preload of a specified pressure or more so that the radial clearance becomes zero or more, and has a larger rotational resistance than the bearings 3 and 3 that support the inner member 2 during rolling. Is set to.

In the above structure, the rotation resistance of the rolling bearing 23 applies a force to the operation shaft 19 and the large-diameter side retainer 9 so as to prevent the rotation, and the large-diameter side retainer 9 is fixed to the inner member 2.
Decelerates against the rotation of.

Further, the pin 12 connected to the large diameter side retainer 9
Is the clearance X in the rotational direction with respect to the pin hole 11 of the inner member 2.
A circumferential clearance larger than the rotational clearance X is provided between the pin 21 which is loosely fitted with the differential bearing 22 and the pin hole 20 of the inner member 2.

The above-mentioned clearance X in the rotational direction is determined by the cage 9 on the large diameter side.
Is to determine the delay angle with respect to the small diameter side retainer 8, and its size is the distance from the neutral position between the engagement surfaces 6 and 7 until the sprag 15 contacts both engagement surfaces via the spring member 16. Is set larger than.

On the other hand, between the outer ring 1 and the support case 24,
A coupling means 26 for coupling and disconnecting the outer ring 1 and the inner member 2 is provided. As shown in FIGS. 4 and 5, the coupling means 26 slidably engages a coupling ring 28 with an axial spline groove 27 formed on the outer periphery of the inner member 2 so that the end face of the support case 24 is supported. , A drive cylinder 29 for moving the coupling ring 28 toward the outer ring 1 is provided, and the coupling ring 28 is always mounted on the inner member 2.
A disc spring 30 that urges the disc spring 30 in the direction of pulling away from is attached.

On the end faces of the coupling ring 28 and the outer ring 1,
As shown in FIGS. 4 and 6, a large number of engaging teeth 31 and 32 are formed so that the engaging teeth 31 and 32 mesh with each other when they approach each other. The engagement between the engaging teeth 31 and 32 and the engagement of the spline tooth 27 with the coupling ring 28. The outer ring 1 and the inner member 2 are integrally connected by the combination. Further, a sliding member 50 is provided between the pressing ring 51 provided at the tip of the drive cylinder 29 and the coupling ring 28, so that the drive cylinder 29 and the coupling ring 28, which are in different rotation states, can be slid and coupled together. It has become. Since the outer teeth 1 and the inner member 2 rotate relative to each other depending on operating conditions as described later, the engaging teeth 31 and 32 are preferably formed in a tooth shape like a dog clutch so that they can be easily engaged even in a rotating state.

A plurality of the drive cylinders 29 are arranged on the end surface of the fixed support case 24 along the circumferential direction, and high pressure air or hydraulic oil is stored in the cylinders in response to a signal from a switch or the like provided in the driver's seat of the vehicle. It is being introduced.
When pressure is generated in each drive cylinder in this way, each piston 33 simultaneously projects to move the coupling ring 28,
Engage the engagement teeth 31, 32. Also, the drive cylinder 2
When 9 does not operate, as shown in FIG. 4, the coupling ring 28 is separated from the outer ring 1 by the urging of the disc spring 30, and is held in a state of being crimped to the piston 33 of the drive cylinder 29.

The rotation transmitting device A of the embodiment has the above-mentioned structure, and in order to be mounted on the drive path of the vehicle as shown in FIG. 7, the front wheel propulsion shaft D branched from the transfer C is connected to the outer wheel 1. Then, the front differential E is connected to the inner member 2.

In the case of normal running, the coupling ring 28 is separated from the outer ring 1 and the outer ring 1 and the inner member 2 are separated.

When the vehicle travels in this state, the rotation of the engine first rotates the inner member 2 through the transfer C, so that the rotation transmitting device A holds the inner member 2 on the small diameter side. The container 8 starts rotating at the same time. On the other hand, the large-diameter side cage 9 rotates later than the inner member 2 due to the deceleration action of the differential means 22. Therefore, both cages 8 and 9 rotate relative to each other, and as shown in FIG. 4, the sprag 15 tilts in the opposite direction to the rotation direction (arrow direction) of the inner member 2 and stands by at the meshing position.

Since the outer wheel 1 and the inner member 2 rotate at the same speed while the vehicle is traveling straight forward or backward in a normal state, both the inner member 2 and the cages 8 and 9 are rotated. Turn around,
The sprags 15 are kept in mesh.

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 overrun with respect to the sprags 15. Therefore, the sprag 15 does not engage, the front wheel and the outer wheel are separated and rotate, and the braking phenomenon at the tight corner does not occur.

When the rear wheels slip during running, the front wheels (outer wheels 1) are decelerated as the vehicle speed decreases.
Since the rotation of the inner member 2 connected to the transfer C is exceeded, the sprag 15 engages with the engagement surfaces 6 and 7, and the outer ring 1 and the inner member 2 are integrated. Therefore, the driving force is applied to the front wheels, and the state is switched to the four-wheel drive state.

On the other hand, when traveling in a loose braking state by engine braking on an icy road or the like, the driving cylinder 29 is operated in the coupling means 26 to activate the coupling ring 2.
8 is moved, and the outer ring 1 and the inner member 2 are connected by the engagement of the engaging teeth 31 and 32. As a result, the front wheels are directly connected to the transfer wheels and the rear wheels, so that reverse input is performed from the front wheels to the drive system, and deceleration is performed by the frictional force generated between the tires of the four wheels and the road surface.

To release the above braking state, it is sufficient to release the operating pressure from the drive cylinder 29 and retract the piston 33. When a failure occurs in the drive cylinder 29, the disc spring 30 attached to the front wheel 2 forcibly pushes back the coupling ring 28 to separate the outer ring 1 from the inner member 2. That is, in the failure mode, the front wheels remain separated during engine braking, and the tight corner braking phenomenon during turning is avoided. In a four-wheel drive vehicle whose main purpose is off-road running, the disc spring 30 is omitted from the above structure to allow the vehicle to run in a failure mode while the front wheels and the rear wheels are connected, and the four wheels are directly connected to each other. It is also possible to obtain a large driving force by holding.

In the above embodiment, the inner member 2 is the input side and the two cages 8 and 9 are connected to the inner member 2. However, the outer ring 1 may be the input side. In this case, the large-diameter side retainer 9 is fixed to the outer ring 1, the small-diameter side retainer 8 is rotatably connected to the outer ring 1 through the gap in the rotational direction, and the differential means is connected to the small-diameter side retainer. To do.

Further, although the sprag 15 which engages in the forward and reverse rotational directions is shown as the engaging element, instead of this, a sprag engaging in only one direction is used symmetrically, or an engaging element such as a roller is used. It can also be used.

Further, as the differential means, a rolling bearing having a large rotational resistance is used. However, the invention is not limited to this. Can be used.

[0039]

As described above, in the rotation transmission device of the present invention, the outer ring and the inner member are connected and disconnected by the connecting means, so that the operating state of the mechanical clutch and its stop can be arbitrarily switched. Therefore, in transmitting the driving force to the front and rear wheels of the vehicle, when it is necessary to restrain the four wheels during driving or braking, the four wheels can be directly mechanically coupled to each other, and a strong driving force and braking force can be obtained. There is an advantage that power can be exerted.

[Brief description of drawings]

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

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

FIG. 3 is a sectional view showing an operating state of a sprag.

FIG. 4 is an enlarged cross-sectional view showing a coupling means.

5 is a sectional view taken along line VV of FIG.

6 is a sectional view taken along line VI-VI of FIG.

FIG. 7 is a diagram showing an example of attachment to a drive path of a vehicle.

FIG. 8 is a vertical sectional front view showing a conventional example.

[Explanation of symbols]

 1 Outer ring 2 Inner member 6, 7 Engaging surface 8 Small diameter side retainer 9 Large diameter side retainer 15 Sprag 16 Spring material 19 Actuating shaft 22 Differential means 26 Coupling means 28 Coupling ring 29 Drive cylinder 30 Disc spring 50 Sliding material A rotation transmission device

Claims (2)

[Claims] 1. A retainer is provided between an outer ring and an inner member fitted to the outer ring, and a retainer is provided between the outer ring and the inner member so as to engage an engaging element between the opposing faces of the outer ring and the inner member. , Differential means for connecting the retainer and the outer ring or the inner member so as to be co-rotatable through a gap in the rotational direction, and for producing a rotation difference between the retainer and the outer ring or the inner member connected to the retainer And a connecting means for connecting and disconnecting the outer ring and the inner member. 2. The coupling means engages and disengages the outer ring and the inner member, a driving member that moves the coupling member in an engaging direction, and urges the coupling member in a disengaging direction. The rotation transmission device according to claim 1, comprising an elastic member.