JPS6014992Y2 - spring clutch - Google Patents

Description

[Detailed explanation of the invention] In this invention, the shaft ends of both rotating shafts on the driving side and the driven side are concentrically abutted against each other, a single coiled spring is fitted across both shafts, and this spring is This relates to a spring clutch that transmits rotation in one direction from the driving side to the driven side using the frictional force generated by tightening the winding.It improves the quick response when engaging the clutch, and at the same time allows the driven side rotating shaft to rotate in both forward and reverse directions when the clutch is released. The purpose of this is to enable the rotation of

First, a conventional spring clutch will be explained with reference to FIGS. 1 and 2. In the figures, a spring clutch 1 is rotatably supported on a hollow shaft 2.

3 is a snap ring for preventing the input side rotating shaft 1 from coming off, and the hollow shaft 2
It is fitted into a groove provided around the .

Reference numeral 4 denotes an output side rotation shaft which is fitted into the hollow shaft 2 with one end facing one end of the input side rotation shaft 1, and is coupled to the hollow shaft 2 by a set screw 5.

Reference numeral 6 denotes a coil-shaped clutch spring that is fitted over the outer circumference of the abutting ends of both rotating shafts 1.4, and both ends are bent 7 and 8 in the radial direction, and one of the bent portions 7 is connected to the output side rotation. The other bent part 8 is engaged in a radial hole provided in the shaft 4 and in a radial notch provided in one end of the control collar 9, respectively.

The control collar 9 is fitted around the clutch spring 6, and a protrusion 10 is formed on the outer periphery of the control collar 9. A control piece for a plunger of a solenoid (not shown) is engaged with or disengaged from the protrusion. It has become.

In the above configuration, when the control piece operated by a solenoid (not shown) is separated from the protrusion 10 of the control collar 9 and is not engaged with the protrusion, the spring 6 maintains its free length, that is, the inner part of the spring The circumferential surface is in pressure contact with the outer circumferential surface of both rotating shafts 1° 4, and when the input rotating shaft 1 is rotated in this state, the inner circumferential surface of the spring 6 and the opposing outer circumferential surface of the input rotating shaft 1 Frictional force is acting on the spring, and the relationship between the winding direction of the spring and the rotation direction of the input rotating shaft 1 is such that the spring is tightened by the rotation of the rotating shaft, so the spring rotates. As the shaft 1 rotates, the spring is tightened, and as a result, the frictional force between the two rotary shafts and the spring further increases, and the two rotary shafts become coupled, and the rotation of the input-side rotary shaft 1 is transmitted to the output-side rotary shaft 4. be done.

In addition, in this clutch engaged state, the control collar 9
rotates with both rotating shafts 1 and 4.

Next, in this connected state, a control piece (not shown) is engaged with the protrusion 10 of the control collar 9 by the action of a solenoid, and when the rotation of the control collar is restrained, the spring 6 receives a force in the unwinding direction. Since the diameter is increased, the frictional force between the spring and both rotating shafts becomes zero or almost zero, and the clutch is released.

The structure and operation of a conventional spring clutch of this type are as described above. However, in such a conventional spring clutch, since there is only one protrusion 10 on the circumference of the control collar 9, the control piece is moved by operating a solenoid. Even if the protrusion 10 is placed within the rotation locus, the protrusion may not necessarily be in the locking position with respect to the control piece, and in the worst case, the clutch operation time (clutch release time in this case) may be longer than the control collar. There will be a delay by the time required for one rotation.

In addition, when the clutch is in the released state, by disengaging the control piece (not shown) from the protrusion 10 of the control collar 9, the rotation shaft 4 on the output side is rotated together with the control collar and the spring in the direction to unwind the spring. This is possible with the rotary shaft 4 alone, but rotation in the opposite direction is impossible because the spring 6 is tightened and the contact friction force of this spring against both the rotary shafts 1 and 4 is increased.

In other words, in the clutch release state, the driven-side rotation shaft can rotate in one direction but cannot rotate in the other direction, which may be extremely inconvenient depending on the application.

The present invention solves such problems, and an embodiment of the present invention will be described below with reference to FIGS. 3 and 4.

In the same figure, reference numerals 11 and 12 denote rotary shafts on a hollow shaft 13 with their ends abutted against each other, and a clutch spring 14 is fitted across both shafts, with a bent portion 1 at one end of the spring.
5 is engaged with a hole in the radial direction of one rotating shaft 11. In this embodiment, the rotating shaft 11 that engages one end of the clutch spring becomes the input side, and the clutch spring 14 is fitted into the rotating shaft 11 on the input side. The structure is such that a gap exists between the inner circumference of the spring and the outer circumferential surfaces of both rotating shafts, which are opposing surfaces.

Reference numeral 16 is a cylindrical intermediate collar that is fitted onto the clutch spring and has a notched groove on one end surface, and a bent portion 17 at the other end of the clutch spring 14 is engaged with this notched groove.

Reference numeral 18 denotes a coil-shaped control spring fitted onto the intermediate collar 16 in pressure contact, the winding direction of which is opposite to that of the clutch spring 14, and one end of which is bent 19 outward in the radial direction. ing.

20 is an intermediate collar 16 covering the control spring 18;
The bent portion 19 of the control spring is engaged with a notched groove on one end of the control ring, which is fitted so as to be rotatable relative to the control ring, and a plurality of pawls 21 protrude at equal intervals on the outer periphery. established,
A control piece (not shown), which would have been engaged with the protrusion 10 of the control collar 9 in the conventional case, is instead engaged with or disengaged from one of these claws.

The embodiment of the present invention is constructed as described above, and when the control piece (not shown) is separated from the pawl 21 of the control ring 20, the rotation of the control ring is not restricted. The clutch only rotates with the collar 16, control spring 18, and control ring 20, but no rotation is transmitted to the output rotating shaft 12, and the clutch is in a released state.

In addition, in this clutch released state, the output side rotating shaft 1
2 has a gap between the clutch spring 14 and the clutch spring 14, and since there is no restriction on rotation, the clutch spring 14 can freely rotate in either the forward or reverse direction.

Next, in this state, when a solenoid (not shown) is actuated to bring the control piece into the rotation locus of the control ring 20, the pawl closest to the control piece engages with the control piece, and as a result, the control ring 20 The rotation of is restricted,
Along with this, the intermediate collar 1 is controlled via the control spring 18.
Also, since one end of the clutch spring 14 is engaged with the groove of the input rotating shaft 11, the rotation of the rotating shaft 11 tightens the clutch spring 14, and as a result, the clutch spring 14 is tightened. A strong frictional force is generated between the input side rotating shaft 11 and the output side rotating shaft 1 via the clutch spring 14.
2, and the clutch becomes ready to engage.

Further, after the clutch is engaged, the intermediate collar 16 and the control spring 18 are stopped, but since a slip occurs between them, the rotation of the intermediate collar is not restricted in any way.

That is, the frictional force between the control spring 18 and the intermediate collar 16 restrains the rotation of the intermediate collar to enable tightening of the clutch spring 14 when the clutch is engaged, but after the clutch is engaged, the frictional force between the intermediate collar and the intermediate collar is The setting is such that slip occurs.

As is clear from the above, the present invention provides a plurality of pawls (which may be protrusions or recesses) on the circumference of the control ring 20 to restrain the rotation of the control ring 20 when the clutch is engaged. Therefore, the time from when the solenoid is activated to engage the clutch until the clutch completes engagement can be shortened, and in other words, the responsiveness of clutch engagement can be improved. For example, when two clutches of the same type are connected use,
When one of these clutches is engaged and the other is disengaged, or the relationship is reversed to obtain either forward or reverse rotation, when one of the clutches is engaged, it is done at the same time or approximately. The other clutch can be released at the same time, so that the so-called clutch fight phenomenon at this time can be avoided.

Furthermore, by adding the control spring 18 and the control ring 20, the output rotating shaft 12 can freely rotate in any direction when the clutch is released.
When using two clutches to extract either forward or reverse rotation by switching their coupling relationship, the rotation when one clutch is engaged is restrained by the output rotating shaft of the other clutch. It has the effect of preventing

[Brief explanation of the drawing]

1 and 2 are a longitudinal sectional view and a transverse sectional view showing a conventional clutch, and FIGS. 3 and 4 show an embodiment of the present invention, with FIG. 3 being a longitudinal sectional view and FIG. is a side view of the upper half of the control ring; 11.12...Rotating shaft, 14...Clutch spring, 16...Intermediate collar 18.
... Control spring, 20 ... Control

Claims (1)

[Scope of utility model registration request] Concentric rotating shafts with one end butted against each other, fitted across both rotating shafts with a gap between them and the outer peripheral surfaces, A coiled clutch spring that is dynamically connected to the shaft; an intermediate collar that is fitted around the outer periphery of this spring and to which the other end of the spring is dynamically connected; a coiled control spring whose direction is opposite to that of the clutch spring, and a plurality of coiled control springs fitted on the intermediate collar so as to be rotatable relative thereto, coupled to one end of the control spring, and on the outer periphery. A control ring having an engagement protrusion is provided, and the rotation of the control ring is restrained by engaging a control piece operated by a solenoid or the like to the protrusion on the control ring to engage the clutch. Features a spring clutch.