JPS60245832A - Clutch device - Google Patents

Abstract

PURPOSE:To prevent overrunning of clutch spring by providing an unilateral clutch between a drive clutch drum and a driven clutch drum. CONSTITUTION:Upon exceeding of the load at the driven side over the top dead centers B, C, moment for rotating a driven clutch drum 8 clockwise will function but since the drive clutch drum 7 will rotate with constant speed, the clutch spring 11 will function in the loosening direction. A unilateral clutch 9 inserted between said clutches 7, 8 will prevent quicker rotation of driven clutch than the drive clutch and rotate with same speed, thereby normal displacement is achieved continuously.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The clutch device of the present invention is used in an office machine such as a copying machine, for example, to use a photoreceptor cleaning means (for example, a fur brush, a cleaning blade, etc.) for only a certain period of time. The present invention relates to a clutch device used for a contact/separation means, a means for connecting/disconnecting drive transmission for fixing pressure, paper feeding pressure, separation claw operation, and the like.

2. Description of the Related Art Conventional Structures and Problems Generally, in office machines such as copying machines, electromagnetic clutches, spring clutches, and the like are widely used as means for connecting and disconnecting drive transmission. Electromagnetic clutches are small and easy to use, but spring clutches are expensive and 1) consume a lot of power, and if the transmitted torque is large, they need to be made large, so they are heavy and have a large inertia, making them difficult to operate. It was inferior. Furthermore, in order to correctly determine the connection/disconnection position, it is necessary to use a position detection switch, etc., which has the drawback of becoming expensive and complicated.

In addition, electromagnetic clutches in particular have the disadvantage that the transmitted torque decreases during long-term use.

On the other hand, spring clutches are inexpensive and can accurately position the connection and disconnection, but because of the winding direction of the spring used for this, they tend to overrun in the opposite direction of the drive transmission direction. This can be extremely inconvenient depending on how it is used. This will be explained with reference to the drawings.

When converting rotational motion into reciprocating motion, a bell crank mechanism shown in FIG. 1 or a cam mechanism shown in FIG. 2 is usually used. In FIG. 1, a bell crank 2 is driven by a driving portion via a shift latch 1, and a lever 4 is caused to reciprocate from the bell crank 2 via a spring 3. Second
When using the cam mechanism shown in the figure, a drive unit (not shown) rotates the cam plate 2' via a shift latch 1', and a lever contacts the cam plate 2' via a roller under the action of a spring 3'. 4' is reciprocated.

If the speed diagram of the lever is shown with the amplitude of the reciprocating lever 4 or 4' on the vertical axis and the time on the horizontal axis, the speed diagram of the bell crank mechanism shown in Fig. 1 will be the sine shown in Fig. 3. It becomes a waveform. On the other hand, with the cam mechanism shown in FIG. 2, any velocity diagram can be obtained by selecting the cam shape. For example, in a bell crank mechanism having the speed diagram shown in Fig. 3, a gradual displacement from the bottom dead center to the top dead center B is generally obtained, and in a cam mechanism, a gradual displacement from the top dead center C to the bottom dead center is generally obtained. . During BC, the clutch is disengaged and the crank mechanism is in a stopped state, and this state is required, for example, in a copying machine's paper feed mechanism, fixing mechanism, and cleaning blade separation mechanism. In such a case, if a force in one direction is applied to the load side by, for example, springs 3 and 3', once the top dead center, which is the maximum operating position, is exceeded, the force in one direction on the load side will be reversed. A moment acts that causes the drive side to turn. At this time, if the drive side is a mechanism that rotates at a constant speed, a gradual displacement as shown in CD in Fig. 3 will be obtained, but if the drive side is a mechanism that is rotated by the above action, a sudden displacement as shown by the chain line GE will be obtained. A displacement is made. Those using a spring clutch as clutch 1 or 1' belong to this mechanism. In other words, when converting rotational motion to reciprocating motion, the spring exhibits overrunning properties due to the load when the top dead center is exceeded, operating faster than the predetermined motion speed, producing shock and noise, and sometimes causing loss of function. It also has the disadvantage that it can also occur.

OBJECTS OF THE INVENTION It is an object of the present invention to provide a clutch device which eliminates the above-mentioned disadvantages when using a spring clutch.

Structure of the Invention The clutch device of the present invention includes a driving clutch cylinder, a driven clutch cylinder forming a window with a part of the driving clutch cylinder, a shaft on which the driving clutch cylinder is rotatably mounted, and the driving clutch cylinder and the driven clutch cylinder. a clutch spring disposed so as to be coaxially positioned and wound over the driven clutch cylinder; and a stop member that is engaged with one end of the clutch spring and interposed coaxially between the driving clutch cylinder and the driven clutch cylinder. and a control mechanism appropriately attached to another member so as to engage and disengage the stop member, and a one-way clutch provided between the drive clutch cylinder and the driven clutch cylinder, Even if a moment acts on the drive side due to the force on the load side, the clutch spring exhibits an overrunning property, and the drive clutch cylinder and driven clutch cylinder can rotate at the same rate. It is.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments of the present invention will be described with reference to the drawings.

FIG. 4 shows a sectional view of a main part of a clutch device according to an embodiment of the present invention. In FIG. 4, one end of the shaft 6 is fixed to a side wall 6a, and the other end is pivotally supported by a side wall 6b. A drive clutch cylinder 7 is rotatably mounted on the shaft 5, and a driven clutch cylinder 8 is mounted with one end thereof abutting each other and coaxially arranged via a drive clutch brush and a one-way clutch 9. The drive gear 10 is constantly driven and rotated by a drive section (not shown). A clutch spring 11 is attached to the inner and outer peripheral surfaces of both latch bodies 7 and 8, and a stop member 12 is fitted on the outside of this clutch spring 11. The stop member 12 is provided with stop pieces 12a, which will be described later, at positions exactly diametrically opposed to each other on its outer peripheral surface.

One end 11a of the clutch spring 11 is locked to a stop member 12, and the other end 11b protrudes through an elongated hole 14 provided in the cam 13 so as to form the same window as the outer periphery of the driven clutch body 8. The end portion 11b is held by a phase adjustment plate 23 of the clutch spring 11. As shown in FIG. 6, a control lever 16 attached to the solenoid 15 is disposed at a position where it engages with the stop piece 12a of the stop member 12. As shown in FIG. One end of a spring 17 that urges the control lever 16 to engage with the stop piece 12a of the stop member 12 is locked to the control lever 16, and the other end of the spring 17 is fixed. The control lever is loosely fitted into a pin 19 implanted in a support plate 18 fixed to the solenoid body.

The control lever 16 takes two different positions in the radial direction of the clutch body when the solenoid 15 is energized and when the solenoid 15 is deenergized. That is, when the solenoid 15 is deenergized, the control lever 16 is in the first position shown by the solid line in FIG.
When energized, it assumes the second position shown by the broken line in FIG. In the first position, the control lever 16 engages the stop piece 12a to stop the stop member, whereas in the second position, the control lever 16 disengages from the stop piece 12a, thereby stopping the stop member. Never.

In FIG. 7, the one-way clutch 9 includes four wedge-shaped recesses 20 formed by the outer peripheral surface of the driving clutch body 7 and the inner concave surface provided on the driven clutch body 8, and each of these wedge-shaped recesses 20.
One roller 21 each inserted into the wedge-shaped recess 2o
A spring 22 is provided between the bottom of the roller 21 and each roller 21. Here, assuming that the speed of the constantly rotating driving clutch cylinder 7 is vl and the speed of the driven clutch cylinder 8 is v2, the one-way clutch 9 is connected and disconnected as follows.

v2>vl...... When (1), the roller 21 presses the spring 22 and is in the enlarged part of the wedge-shaped recess 2o, so that in this one-way clutch 9, the drive clutch body 7 and The driven clutch cylinders 8 are in a state where they can freely rotate with respect to each other.

v2〈vl... (2) When the roller 21 bites into the narrow part of the wedge-shaped recess 2o,
The driving clutch cylinder 7 and the driven clutch cylinder 8 rotate integrally, that is, have the same rotational speed.

The operation of the clutch device of this embodiment configured as described above will be described below.

The lunoid 15 is not energized and its control lever 16 is in the sixth position.
When in the first position shown by the solid line in the figure and engaged with the stop piece 12a of the stop member 12, the stop member 12 stops and the clutch spring 11 Therefore, the spring clutch device is in a disengaged state and the driven clutch cylinder is not rotated. When the solenoid 15 is activated in a triggering manner and the control lever 16 is moved from the first position shown in FIG. 6 to the second position shown in broken lines against the action of the spring 17,
When the stop piece 12a is released, the clutch spring 11 acts to tighten both latch bodies γ, 8, and the both latch bodies are integrally connected, and the stop piece also starts to rotate. The solenoid is deenergized by a trigger and the control lever 1
6 touches the outer periphery of the stop piece 12, the control lever 16
Since the spring 17 is weakly biased so as not to stop the stop member 12, when the stop member rotates once and the control lever 16 and the stop piece 12a are re-engaged, the stop member 12 is stopped and the spring clutch device is activated again. 9, which continues until the solenoid 15 is energized. This is the state Be shown in FIG. In this state, in a copying machine, cleaning means such as a photoreceptor (for example, a fur brush,
It is used as a separation means for using cleaning blades (cleaning blades, etc.) for only a certain period of time, and to maintain the operating state of fixing pressure, paper feeding pressure, and separation claw operation.

At the end of the cycle described above, it is desirable that the driven side of the spring clutch device displaces according to a curve such as the curve CD in Figure 3, but as mentioned above, the load on the driven side reaches the top dead center (as shown in Figure 3). B or 0 point), a moment acts to rotate the driven clutch body 8 clockwise. Since the driving clutch cylinder 7 is rotating at a constant speed, the clutch spring 11 acts in the direction of loosening, and as a result, the driven clutch cylinder 8 undergoes a sudden change as indicated by the chain line GE shown in FIG. However, according to the present invention, since the one-way clutch 9 is inserted between the driving clutch cylinder and the driven clutch cylinder, even if the driven clutch cylinder 8 tries to rotate rapidly due to the load moment, the driving clutch cylinder 7 It cannot rotate faster, but rotates at the same speed. Thereby, the displacement curve C'D in FIG. 3 is maintained.

Furthermore, since the cam 13 is provided integrally with the driven clutch body 8, in order to stop the cam follower driven at the origin of the cam 13, it is necessary to use the control lever 16 and the stop piece 12a.
The position of the clutch spring 11 and the locking position of the clutch spring 11 to the stop member 12 must be accurately matched during assembly, and it is difficult to do so accurately in practice. Therefore, in the present invention,
One end 11a of the clutch spring 11 is locked to the stop member 12, and the other end 11b is projected through an elongated hole 14 provided in the driven clutch body and inserted into the phase adjustment plate 23. As a result, the phase adjustment plate 23 is moved to the other end 1 of the clutch spring 11.
1b can be moved arbitrarily in the direction in which the clutch spring 11 is unwound, so that when assembling, the solenoid 15
When the cam 1 is de-energized, that is, in the first position shown in FIG.
It becomes possible to arbitrarily adjust the cam follower that is driven to the origin in step 3 so as to stop it, and it also becomes possible to arbitrarily adjust the cam follower to stop when it is desired to change the origin of the cam due to the timing. As is clear from the above explanation, the clutch device of the present invention prevents the driven side of the spring clutch device from rotating faster than the driving side even when a force in the direction of loosening the clutch spring acts on the load side. The effect is that a normal displacement state is always achieved. Furthermore, one end of the clutch spring is locked to a stop member provided in the same window as the above-mentioned both clutch bodies, and the other end is inserted through a hole provided in the driven clutch body to extend the clutch spring against both clutch bodies. By making it movable in the direction of loosening, it is possible to arbitrarily change the stop phase of the driven clutch cylinder.

[Brief explanation of drawings]

1 and 2 are configuration diagrams of main parts of a conventional clutch device, FIG. 3 is a speed diagram of a conventional example, and FIG. 4 is a sectional view of main parts of a clutch device according to an embodiment of the present invention, Fig. 5 is a perspective view of a clutch spring used in the embodiment of the present invention, Fig. 6 is a plan view showing the relationship between the solenoid and the stop member in the embodiment of the present invention, and Fig. 7 is an embodiment of the present invention. FIG. 5... shaft, 7... drive clutch body, 8...
... Driven clutch body, 9 ... One-way clutch, 11 ... Clutch spring, 12 ... Stop member, 12a ... Stop piece, 15 ...・
・Solenoid, 16... Control lever. Name of agent: Patent attorney Toshio Nakao and 1 other person 2nd
Figure 3 Figure 4 Figure 5 Figure 6 Figure 5; Epi-Ro Figure 7-J ((L

Claims (2)

[Claims] (1) A driving clutch cylinder, a driven clutch cylinder coaxial with a part of the driving clutch cylinder, a shaft on which the driving clutch cylinder is rotatably mounted, and a coaxial structure extending over the driving clutch cylinder and the driven clutch cylinder. a clutch spring disposed in such a manner as to be wound tightly, a stop member to which one end of the clutch spring is engaged and coaxially interposed between the driving clutch cylinder and the driven clutch cylinder; What is claimed is: 1. A clutch device comprising: a control mechanism attached to other members as appropriate to engage and disengage; and a one-way clutch provided between the driving clutch cylinder and the driven clutch cylinder. (2) One end of the clutch spring is locked to a stop member interposed coaxially between the driving clutch cylinder and the driven clutch cylinder, and the other end is inserted into a hole provided in the driven clutch cylinder, and the clutch spring is The clutch device according to claim 1, wherein the clutch device is configured to be movable in a loosening direction relative to the driving clutch cylinder and the driven clutch cylinder.