JPS5836902Y2 - two-way freewheel - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION This invention relates to a two-way freewheel used, for example, as a transfer declutch device in an all-wheel drive vehicle.

Conventional push-button declutch devices include two sets of freewheels arranged in forward and reverse directions, and one of the freewheels is selectively used depending on the direction in which the vehicle is traveling (forward or backward).

However, with such a combination of two sets of freewheels, it is necessary to release one of the freewheels depending on the shift position (forward/forward position) of the transmission, so it is necessary to select the freewheel using the control linkage etc. Operation is required.

Further, even in a transfer declutch device using a so-called differential mechanism, a locking mechanism must be provided in order to operate the declutch device.

However, providing a control linkage or locking mechanism in this manner has the drawback of increasing the size and complexity of the transfer mechanism.

This idea was made in view of the above circumstances, and
The system is always rear-wheel drive, and when the rear wheels slip, the system automatically switches to all-wheel drive without any special operation.Moreover, when the front wheels rotate at a higher speed than the rear wheels, such as when turning, The object of the present invention is to provide a two-way freewheel that can protect the power transmission system and the steering system by allowing this and can be used as a transfer declutch device or the like.

Hereinafter, this invention will be described in detail based on embodiments shown in the accompanying drawings.

As shown in FIG. 1, a clutch body 2 is screwed into the shaft end of a drive shaft 1, which is rotatably driven in both forward and reverse directions, through a square screw or the like so that it can move forward and backward.

The clutch body 2 has a first drive 7 facing the clutch body 2 at a predetermined interval.
A flange 3a and a second flange 3b are provided.

A driven flange 5, which is sandwiched between the driving flanges 3a and 3b, is integrally provided at the shaft end of the driven shaft 4, which is supported on the same axis as the driving shaft 1.

A plurality of grooves 6 are equally spaced on the surface of the driven flange 5 that faces the first driving flange 3a, that is, the first surface 5a of the driven flange 5, the grooves becoming shallower as the drive shaft 1 rotates in the forward direction. and a second flange 5 opposite to the driven flange 5, that is, facing the second driving flange 3b.
In the same manner as described above, grooves 6 which become shallower as the direction of rotation of the drive shaft 1 is reversed are formed at equal intervals in b.

In each of these grooves 6, a trochanter 7 such as a steel roller having a diameter larger than the maximum depth of the groove 6 is installed so as to be movable in the rotational direction of the drive shaft 1, and each trochanter 7 and the groove A spring 8 is stretched between the end face of the shallowest part of the groove 6 to elastically hold the trochanter 7 in the deepest part of the groove 6.

In addition, since the diameter of each trochanter 7 is larger than the maximum depth of the groove 6,
Part of the trochanter T is always connected to the first and second driving flanges 3a and 5b of the driven flange 5, respectively.
, protrudes toward the 3b side.

On the other hand, a slip ring 11 is installed in a groove 9 recessed on the outer periphery of the clutch body 2 via a spring 10,
By bringing the outer periphery of this slip ring 11 into sliding contact with the inner surface of the freewheel case 12, rotational resistance is imparted to the clutch body 2.

The square screw screwing the drive shaft 1 and the clutch body 2 together provides rotational resistance to the clutch body 2 when the clutch body is rotated in the reverse direction of the drive shaft 1 with respect to the drive shaft 1. When the drive shaft 1 is rotated in the forward direction, the clutch body 2 spirals and the first drive flange 3a approaches the first surface 5a of the driven flange 5, and conversely, rotational resistance is applied to the clutch body 2 and the clutch body 2 is driven. When the shaft 1 is reversed, the clutch body 2 is screwed back, and the first driving flange 3a and the first surface 5a are separated, and at the same time, the second driving flange 3b approaches the second surface 5b of the driven flange 5. is oriented to.

In the above configuration, when power is not being transmitted or when the drive shaft 1 is stationary and only the driven shaft 4 is rotating,
As shown in FIG. 2A, the first and second drive flanges 3
a, 3b and the first surface 5a and second surface 5 of the driven flange 5
Since the distance between the drive shaft 4 and the drive shaft 4 is equal and none of the drive 7 flange comes into contact with the trochanter I, the driven shaft 4 can freely rotate in either the forward or reverse direction.

When the drive shaft 1 rotates in the forward direction, the clutch body 2 screwed onto the drive shaft 1 is subjected to rotational resistance due to the friction between the slip ring 11 and the case 12. As shown in FIG. 2B, the first driving flange 3a moves close to the first surface 5a of the driven flange 5.

Then, the trochanter I protruding from the first rotor 5a receives the frictional force between it and the first drive 7 flange 3a, and moves in the normal rotation direction in the groove 6 against the spring 8.

At this time, the groove 6 formed in the first surface 5a is formed to become gradually shallower in the forward rotation direction of the drive shaft 1.
Due to the movement, the trochanter 7 is strongly wedged between the first drive 7 flange 3a and the bottom surface (sloped surface) of the groove 6, producing a so-called wedge action.

Therefore, the first drive 7 flange 3a and the driven flange 5 are integrated via the rotor 7, and power is transmitted from the drive shaft 1 to the driven shaft 4.

Further, when both the drive shaft 1 and the driven shaft 4 rotate in the normal direction, and the driven shaft 4 is rotating at a higher speed than the drive shaft 1, the second
As shown in FIG. Since the trochanter 7 is rotating at a high speed, there is no wedge action on the trochanter 7, so no transmission is performed between the two shafts 1.4.

On the other hand, when the drive shaft is reversed, the clutch body is screwed back and the second drive flange approaches the second surface of the driven flange, so the power transmission effect is similarly established in the reverse direction.

In the above embodiment, rotational resistance is applied to the clutch body 2 by mechanical means, but as shown in FIG. Rotational resistance may be fluidly provided by engagement with lubricating oil filled in the case 12.

In addition, when the blades 13 are provided on the outer peripheral surface of the clutch body 2 in this way, the blades 13 are made parallel to the axial direction, or the drive shaft 1 and the clutch body 2 are screwed together as shown in FIG. The screwing movement of the clutch body 2 may be facilitated by providing a twist angle in the opposite direction to the square screw.

As explained above, according to this invention, power is transmitted from the drive shaft to the driven shaft in both forward and reverse rotations, but power is not transmitted from the driven shaft to the drive shaft. Because the driven shaft always rotates at a speed equal to or higher than that of the drive shaft, and when the drive shaft is stationary, the driven shaft can be rotated in any direction and at any speed, making it possible, for example, to prevent transfer problems in all-wheel drive vehicles. It is possible to provide a simple and compact automatically operated two-way freewheel for use in various power transmission systems including declutch devices.

[Brief explanation of drawings]

The drawings show a two-way freewheel according to this invention, and FIG. 1 is a sectional view of one embodiment, and FIG. 2A, B,
3 is a sectional view of another embodiment, and FIG. 4 is a partially developed plan view of the same. 1... Drive shaft, 2... Clutch body, 3
a...First drive flange, 3b...
Second driving flange, 4... Driven shaft, 5...
...Followed flange, 5a...First part, 5b.
...Second surface, 6...Groove, 7...
Trochanter, 8... Spring, 11... Slip ring, 13... Vane.

Claims (1)

[Scope of utility model registration request] a drive shaft to which a clutch body having first and second drive flanges arranged in parallel and facing each other in the axial direction is screwed so as to be reciprocatable; a driven shaft having a driven flange interposed between the flanges;
When the drive shaft rotates in the normal direction, the clutch body is screwed forward to bring the first driving flange close to the first surface of the driven flange, and when the drive shaft rotates in reverse, the clutch body is screwed back to bring the second driving flange closer to the driven flange. and a braking device that applies rotational resistance to the clutch body so as to be close to the second surface of the driven flange, and grooves that become shallower as the drive shaft rotates in the forward rotation direction are formed equidistantly on the first surface of the driven flange. Grooves that gradually become shallower as the direction of reversal is reached are formed at equal intervals on the second surface of the driven flange, and in the deepest part of each port, a trochanter with a diameter larger than the maximum depth of the groove is held elastically by a spring. A two-way freewheel.