JPH0260896B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an apparatus comprising a motor drive control mechanism and a clutch.

This applies in particular to clutches in which, for example, a friction disk is clamped between a reaction plate and a pressure plate under the action of a spring, generally in the form of a diaphragm.
The clutch assumes the joint state by the elastic action of the diaphragm, which, since it rests on the cover connected to the reaction plate, exerts an elastic clamping action on the pressure plate.

The clutch is transferred from the engaged state to the disengaged state by the action of a counter device acting on the moving train formed by the pressure plate and the diaphragm.

This device generally has a translatable stop, called a clutch release bearing, which acts on the central portion of the diaphragm to optionally offset the elastic clamping action of the diaphragm acting on the pressure plate. . In addition to this clutch release bearing, the device generally includes a hawk,
It has a kinetic chain consisting of levers, rods, etc.

The device can be operated manually, for example by a clutch release pedal, or by an automatic device.

The actuating device generally causes the counter device to act on the train by the action of a force. If this force is zero or less than the diaphragm force, the clutch is fully or partially engaged. On the other hand, if the actuating force exceeds the diaphragm force, the clutch will transition to the disengaged state.

In the case of a manual control mechanism in which the counteracting device is actuated from the clutch release pedal, the operator can disengage the train from its second joint limit position by its second width by increasing or decreasing the force exerted on the pedal with the foot. A sharp transition to the limit position or vice versa can be made.

In the case of automatic control mechanisms, the countermeasure device generally receives the actuating device on which the force is acting.

In the inactive state of the automatic actuator due to the action of force, the clutch is engaged. In the active state of this automatic actuating device under the action of a force, the actuating device overcomes the elastic resistance exerted by the diaphragm and moves the clutch into its disengaged state.

However, such automatic control mechanisms generally do not have the sensitivity of the foot acting on the pedal. The control device needs to produce considerably high power.

In any application, applying substantial forces to automatic controls comparable to those of manual controls, all drives and their accessories benefit from a sensitivity comparable to that of manual controls. It involves considerable dimensions, high energy consumption and different conditions for activating and deactivating the drive.

The present invention relates to a device consisting of a motor drive control mechanism and a clutch controlled thereby, which does not have these disadvantages and is capable of automatic operation with low power, high sensitivity, small dimensions and simple construction.

According to the present invention, there is provided a device comprising a motor drive control mechanism and a clutch controlled by the motor drive control mechanism,
This clutch connects the reaction plate 11 of the first part and the second part.
between the pressure plates 14 of the parts, under the action of the elastic return device 15, said second part moves into said first part by means of a stroke determined between two limit positions P ₁ , P ₂ . The motor drive control mechanism includes connecting devices 24 and 19 that are connected to the second portion and can move simultaneously, and this connecting device is adapted to move in the forward and reverse directions with respect to the second portion.
from the engaged first position P ₁ of the clutch against the movement of the elastic return device 15,
The second part 14 is moved to a second position where the clutch is disengaged, and the second part 14 is moved to the first position by moving the second part 24,19 by power through the stroke of the coupling device 24,19. In order to move from the position P ₁ to the second position P ₂ , an electric motor 20 is provided separately from the elastic return device 15 , and a connecting portion 26 is further provided between the electric motor 20 and the connecting devices 18 , 19 . In the device where the connection part 2
6 is a worm 31 driven by the electric motor 20
When the electric motor 20 is stopped or driven in the forward and reverse directions, the worm 31 of the deceleration connection 26 and the connection devices 24, 19 are connected by power independently from the elastic return device.
is adapted to reversibly move the second portion 14 of the clutch between the first position P ₁ and the second position P ₂ by moving down the stroke, and the elastic actuating force relief device 21 , 22, 60, 70 are connected to the coupling device 24, 19 to counter the movement of the elastic return device 15 due to the stroke of said second part;
Thereby the force required by the electric motor is reduced and the elastic actuating force relief device changes in both directions through the stroke of the coupling device as the force applied by the elastic return device to the second part A device is provided, characterized in that it is adapted to apply a force to the coupling device.

According to another feature, the elastic relief device provides a force that varies in absolute value as a function of the stroke of the counter device according to substantially the same law as the force of the elastic return device varies as a function of the stroke of the counter device. is configured to have an effect on

Preferably, at every position of the stroke of the counter device, the instantaneous value of the force of the elastic actuator is substantially equal to and of the opposite direction to the value of the force of the elastic return device at the corresponding position of the stroke of the train. .

In one aspect, these elastic relief devices include a compensating device that acts on the counter device in a direction towards the second limit position, the compensating device comprising a stabilizing device, the action of which causes the counter device to pass through an intermediate position between the two limit positions. when reversed, or preferably with such a compensating device and such a stabilizing device at the same time.

The compensation device, which always acts in the direction opposite to the direction of the return device, has the effect of minimizing the actuating force in an intermediate position of the counter device between the two limit positions. The actuating force, which is a minimum in this intermediate position, exhibits an opposite maximum in the two limit positions.

Since a stabilizer that is inactive in this intermediate position acts precisely at and near the limit positions, the stabilizer reduces the maximum force of the actuating force in these limit positions.

In this way, the actuation force is kept low during the stroke,
This makes it possible to provide a low power actuator.

This is very convenient for the selection of actuating devices, especially in fully or partially automatically operated installations.

As a variant, the elastic relief device acts on the counter device via a motion transmission device, which motion transmission device
The force applied to this device is resolved, on the one hand, into a non-acting component which is absorbed by the train, and, on the other hand, into an active component which obeys the law of change of force as a function of the stroke.

This transmission device is rotatably attached to a shaft,
It has a pinion meshing with a rack connected to a counter device, the elastic relief device consisting of at least one spring, one end of which is attached to the fixed point and the other end of which is attached to said pinion, the unacting component being radially , which is absorbed by the shaft of the pinion, whereas the active component is transmitted tangentially and easily.

First, referring to FIGS. 1 to 9, this shows, by way of example, the application of the present invention to a control mechanism of a coupling device comprising a diaphragm clutch suitable for an automobile.

The clutch (FIGS. 1 and 7) has a cover 10 adapted to be fixed to the flywheel 11 of the motor vehicle engine. This flywheel 11 forms a reaction plate. Kuratsuchi is also
It includes a friction disk 12 connected to a main shaft 13 of a gear box of an automobile. The disc 12 is moved against the reaction plate 1 by the elastic clamping action of a spring 15 in the form of a diaphragm.
1 and a pressure plate 14.

The diaphragm 15 rests on the cover 10 at 16 points and has fingers 17 in its central region which act as shown in FIGS. Transition from the clutched state shown in FIG. 7 to the unclutched state shown in FIGS. 6 and 9 in which the stop 18 pushes against the diaphragm 15 to release the clamping action of the pressure plate 14 and release the friction disc 12. When desired, it is pushed to the left in FIGS. 1 and 7 by a stop 18.

Thus, the state of the clutch is modulated as a function of the position of the movable train formed by pressure plate 14 and diaphragm 15.

The trains 14, 15 move in both directions through a defined stroke between a first limit position P1 (FIG. 7) where the clutch is engaged and a second limit position P2 (FIG. 9) where the clutch is disengaged. can do. The diaphragm 15 forms an elastic return device which urges the trains 14, 15 into the first limit position P1.

The clutch release stop 18 is connected to the train 14,
15 and form part of an associated countermeasure device 18, 19. This counter device can be moved by a stroke corresponding to the stroke of the train. The stroke of the counter device 18, 19 is the same as that of the train 14, 1
A first limit position T1 corresponding to the limit position P1 of No. 5
(Fig. 7) and the limit position P2 of trains 14 and 15
and a second limit position T2 corresponding to .

The countermeasure devices 18, 19 may in particular be mechanical devices. If necessary, it may have hydraulic components such as a liquid column.

Thus, the counter devices 18, 19
4, 15 from its first limit position P1 to its second
is adapted to act on the trains 14, 15 in order to cause a transition to the limit position P2 and vice versa.

A positioning actuator 20 is provided in conjunction with the countermeasures 18, 19 and has the effect of determining the instantaneous position of the countermeasures 18, 19 independently of the elastic return devices 15 of the trains 14, 15.

These positioning actuators 20 are
4,15 with its own stroke P1-P2 or P2-P1.
9 is moved by a stroke T1-T2 or T2-T1.

The counter devices 18, 19 (FIGS. 1 to 9) are
It comprises a lever 19 which is pivotally mounted on a fixed pivot 23. The first end 24 of the lever 19 forms a fork in juxtaposition with the declutching stop 18, which is juxtaposed with the diaphragm 15. The second end 25 of the lever 19 is connected by a joint forming a reducer 26 to an actuating device 2 consisting of an electric motor.
0, an elastic compensator 21 and an elastic stabilizer 22.

The elastic compensator 21 and the elastic stabilizer 22 together form an elastic actuation force reduction device 21 , 22 .

The lever 19 is connected to the electric motor 2 at its second end 25.
For driving by 0, a toothed sector 27 is provided,
This toothed sector 27 meshes with two pinions 30 rotatably provided on the fixed frame 29. The pinion 30 is fixed to a large pinion 28, which meshes with the worm 31 to form a connection forming the speed reducer 26. The worm 31 has opposite ridges, one cooperating with one of the pinions 28 and the other cooperating with the other pinion, to compensate for the axial reaction force of the worm 31.

The worm 31 is rotationally driven by the electric motor 20. This electric motor 20 is configured to be stopped, driven forward, or driven in reverse.

The elastic compensator consists of a helical spring 21, which is mounted between a point 32 of the fixed frame 29 and a latching hole 33 made in the end 25 of the lever 19.

The compensation spring 21 always acts on the device 19 in a direction towards the second limit position P2, ie in a direction opposite to the direction of action of the diaphragm 15. Compensation spring 21
has a force between 20% and 80% of the force of the diaphragm 15, preferably approximately 50%. These forces act on the trains 14, 15 by the opposing device 1
8,19, measured along the axis of the device at the level of the declutching stop 18.

This compensating spring 21 displaces the opposing devices 18, 19 and is located between the limit positions T1 and T2 in an intermediate position TM (the eighth
In order to minimize the operating force in Figure), it has the effect of reducing the operating force required for the electric motor.
This position TM is, for example, when the force of the spring 21 is half the force of the diaphragm 15, the positions T1 and T
It is intermediate between 2 and 2.

The actuation force is thus at a maximum in each of the limit positions T1 and T2, although it is reduced by half. The actuating force is exerted in one direction near the limit position T1 and in the other direction near the limit position T2.

These maximum values of actuation force can be further reduced and intermediate positions
In order to bring this closer to a minimum value in the TM, an elastic stabilizer is provided.

These elastic stabilizers consist of two helical springs 22 interposed between two plates 34 and 35. The plate 34 is connected to the second end 2 of the lever 19.
It is pivoted at 36 to 5. The plate 35 is pivotally attached to the fixed frame 29 at 37.

As can be seen in FIG. 2, the frame 29 has an elongated port 38 through which an axle end 36 fixed to the lever 19 passes, and a hole 39 in the plate 34 engages this axle end 36.

Similarly, as can be seen in Figure 2, the fixed frame 2
9 has an axle 37 into which the hole 40 of the piece 41 fixed to the plate 35 engages.

The stabilizing spring 22 has 20% of the force of the diaphragm 15.
80%, preferably approximately 50%, these forces are applied to the axis of the device in the area of action of the countermeasures 18, 19 acting on the trains 14, 15, i.e. at the level of the declutching stop 18. It is measured along.

As can be seen in FIG.
Align with lever pivot 23 at TM.

The action of the elastic stabilizer 22 is similar to that of the countermeasure device 18,1
9 passes through the intermediate position TM (FIG. 8),
be reversed.

The action of these elastic stabilizers is similar to that of countermeasure device 1
8 and 19 occupy this intermediate position TM (FIG. 8), it is zero. The elastic stabilizer 22 is a counterbalance device 1
When 8, 19 occupy a position between the intermediate position TM and the limit position T1, they act in the direction towards the first limit position T1.

The elastic stabilizer 22 acts in the direction towards the second limit position T2 when the counter device 18, 19 occupies a position between the intermediate position TM and the second limit position T2.

Thus, the required actuation force that the electric motor 20 has to exert is very small during the stroke between positions T1 and T2 or vice versa.

When the force of the spring 21 and the force of the spring 22 are each equal to approximately half the force of the diaphragm 15 (these various forces are measured along the axis of the device at the level of the stop 18), the worm 31
The deceleration connection 26 made of 26 can be reversible or irreversible as a function of the inclination of its threads. This is because in each case the actuating device 20 is positioned by a permanent quasi-equilibrium state encountered during the stroke. If the force ratio of the springs 21, 22 and the diaphragm 15 does not fulfill this condition, in any case the worm 31 can be released by appropriate selection of the inclination of the worm thread so as to position the actuating device 20. It is advantageous to make it reversible.

In operation (Fig. 7, Fig. 8 and Fig. 9),
The electric motor 20 and the opposing devices 18 and 19 are in the limit position T.
When occupying a position as in 1, the counter device 1
8, 19 have no effect on the diaphragm 15 at 24 via the stop 18. In FIG. 7, the effects of springs 21 and 22 cancel each other out. The clutch is engaged with a coupling force determined by the elastic force of the diaphragm 15.

To release the clutch, the electric motor 20 is rotated in a direction that moves the countermeasures 18, 19 from the limit position T1 to the limit position T2. When this is done (FIGS. 8 and 9), the opposing devices 18, 19 overcome the elastic resistance of the diaphragm 15 and release the clutch by releasing the friction disk 12 (FIG. 9). In each of the instantaneous positions of the countermeasures, in which the action of the springs 21, 22 is applied together in FIG. However, at the same time, the operating force that the electric motor 20 has to exert is extremely small, which makes it difficult for this electric motor 20 to
For example, the power of an automobile wiper motor, i.e.
It can supply low power comparable to as low as 50 watts.

To reengage the clutch, operation is carried out in the same manner in the opposite direction, passing from the position of FIG. 9 through the position of FIG. 8 to the position of FIG. Again, the electric motor only needs to provide low operating force. In the position of FIG. 7, the full elastic force of the diaphragm 15 continues, which is never reduced by the action of the springs 21, 22, the actions of the springs 21, 22 canceling each other out.

The low power of the electric motor 20 allows automatic operation under favorable conditions and with small dimensions.

In a variant (FIGS. 10 to 17), the elastic force relief device consists of at least one spring 60, one end of which is connected to an attachment point 61, e.g. frame 29.
The lever 19 is attached at a separate location 61 coaxial with the fixed pivot 23 of the lever 19. The spring 60 may be attached to any location on the lever 19.

The other end of the spring 60 is attached to a pinion 63 at 62. This pinion is rotatably attached to a shaft 64 fixed to the frame 29. The pinion 63 meshes with a rack, which in the example shown in FIGS. 10 to 17 consists of a toothed sector 27, with which the pinion 30 meshes.

As can be seen in FIGS. 13 to 16, the spring 6
The force F (shown by the dotted line) applied to the pinion 63 by the pinion 63 is decomposed into a radial passive component absorbed by the shaft 64 of the pinion 63 and a tangential acting component A shown by the solid line. , this tangential component is transmitted to the lever 19 via the toothed sector 27.

As can be seen in Figures 13-16, if the force F remains substantially constant regardless of position, then
Active ingredient A varies to a large extent. Splicing device P
In FIG. 13, corresponding to T1 and T1, this active component A is zero. The active component A increases to the intermediate position shown in FIG. 15, and decreases again toward the position shown in FIG. 16, which corresponds to the release position P2-T2.

The graph in Figure 17 is similar to Figures 13, 14, and 1.
Various positions corresponding to FIGS. 5 and 16 are shown, and references .

In practice, it is convenient to give FIG. 7 a curve C passing through the points, and, and to show the variation of the action component A as a function of the stroke T1-T2 in the desired shape. In particular, the structure according to the invention makes it possible to obtain spring properties which, in any case, become weaker as the elongation increases, a generally unusual but here desired property. In addition, in the curved portion, a normal shape is given in terms of characteristics, and as the elongation becomes smaller, the resistance of the spring becomes weaker. This is the combination of the characteristics of the curve C through and that represents the desired variable value for the active ingredient A.

In particular, the action component A, in absolute value, follows approximately the same law as the force of the elastic return device 15 varies as a function of the stroke of the train.
It varies as a function of 9 strokes.

With this construction, the elastic force relief device formed by the spring 60 considerably reduces the required actuation force that the electric motor 20 has to exert during the stroke between positions T1 and T2 or vice versa.

During operation (FIGS. 11 and 12), the electric motor 20 and the opposing devices 18, 19 are at the limit position T1.
When occupying a position such as (Fig. 11),
Opposing devices 18, 19 are connected to 24 via stopper 18.
It has no effect on the diaphragm 15 at this point.
The action component A of spring 60 is zero at this position in FIG. The clutch is connected by a joining force which is the elastic force of the diaphragm 15.

In order to release the clutch, the electric motor 20 is rotated in a direction that moves the opposing devices 18, 19 from the limit position T1 to the limit position T2. Once this has been done (FIG. 12), the opposing devices 18, 19 overcome the elastic resistance of the diaphragm 15 and the clutch is disengaged by releasing the friction disc 12 (FIG. 12).
figure).

During this removal operation, the action component A of the force-reducing spring 60
is the method shown in the graph of FIG. 17, that is, in particular,
It changes according to the same law as in the diaphragm 15. This reduces the actuation force.

To reengage the clutch, operation is carried out in the same way but in the opposite direction by passing from the position of FIG. 12 to the position of FIG. 11. Again, the electric motor 20 only needs to output a low operating force. In the position of FIG. 11, the clutch is engaged by the action of the total elastic force of the diaphragm 15, which is in no way reduced by the spring 60, and the active component A of the spring is zero, as is clear from the above description. .

In the variant (FIGS. 18 to 20), the structure is similar to that described with reference to FIGS. 10 to 17, but the pinion 63 is omitted and the force-reducing spring 70 (two (here provided side by side) act directly on the toothed sector lock 25.

As mentioned above, the elastic force is resolved, on the one hand, into a non-acting component, which is absorbed by the frame, and, on the other hand, into an active component, which obeys the law of force variation as a function of the stroke. FIG. 19 shows the joined condition, in which the spring 70 is not easily applied, and FIG. 20 shows the disengaged condition, in which the spring 70 is active.

[Brief explanation of drawings]

FIG. 1 is a diagram of a clutch control mechanism according to the present invention shown with the clutch disengaged. FIG. 2 is an exploded perspective view of this control mechanism. 3, 4 and 5 are diagrams separately showing various elements of the control mechanism. Figure 6 shows the first case with the clutch in the disengaged state.
It is a figure similar to the figure. Figures 7, 8 and 9
The figures schematically illustrate the operation of the control mechanism at a clutch engagement limit position, an intermediate position, and a clutch disengagement limit position, respectively. FIG. 10 is a diagram similar to FIG. 1 of a modified example. FIGS. 11 and 12 schematically illustrate the operation of this variant with the clutch in the engagement limit position and the clutch in the disengage limit position, respectively. Figures 13, 14, 15 and 16
The figure shows the method of action of the force relief spring in various positions. FIG. 17 is a graph illustrating the operation at the various positions shown in FIGS. 13 to 16 and showing the law of variation of the action component of the force relief spring as a function of the stroke. FIG. 18, FIG. 19, and FIG. 20 are diagrams showing other modifications. 14, 15... Train, 18, 19... Opposing device, T1, P1... First limit position, T2, P
2...Second limit position, 20...Positioning actuation device.

Claims (1)

[Scope of Claims] 1. A device consisting of a motor drive control mechanism and a clutch controlled by the motor drive control mechanism, which clutch has an elastic force between the reaction plate 11 of the first part and the pressure plate 14 of the second part. Clamped under the action of a return device 15, said second part is located in two limit positions P ₁ ,
The motor drive control mechanism is connected to the second part and can move at the same time with the stroke determined between P ₂ and the first part. Connecting device 2
4, 19, the coupling device acting on said second part to bring the clutch into the engaged first position P ₁
, the second part is moved against the movement of the elastic return device 15 to a second position in which the clutch is disengaged, and via the stroke of the coupling devices 24, 19, the coupling devices 24, 19 are powered. for moving the second part 14 from the first position P ₁ to the second position P ₂ , an electric motor 20 is provided separately from the elastic return device 15 , and the electric motor 20 and the coupling device In a device in which a connecting portion 26 is provided between 18 and 19, the connecting portion 26 is a deceleration connecting portion equipped with a worm 31 driven by an electric motor 20, and the electric motor 20 is stopped or driven in forward and reverse directions. As a result, the worm 31 of the deceleration coupling part 26 and the coupling device 2
4, 19 down the stroke to move the second part 14 of the clutch into the first position P ₁ and the second position P ₂
It is designed to be reversibly moved between
In addition, elastic actuation force reducing devices 21, 22, 60, 70
are connected to the coupling device 24, 19 to counter the movement of the resilient return device 15 due to the stroke of said second part, thereby reducing the force required by the electric motor, and said resilient actuating force reduction device:
Device characterized in that the force exerted by the elastic return device on the second part imparts to the coupling device a force that varies in both directions over the stroke of the coupling device. 2. The elastic return device 15 consists of a diaphragm,
2. The device of claim 1, wherein the elastic actuating force relief device has an effective force vs. linkage displacement curve similar to a diaphragm spring force vs. moving part displacement curve. 3. As the second part moves through its stroke from one limit position to the other limit position, the effective force curve of the elastic actuation force reduction device is such that it passes through a relative maximum value. The device described in. 4. The diaphragm causes the resilient actuating force relief device to apply a force to the movable part through the coupling device that is approximately equal and opposite to the force applied to the movable part throughout the entire stroke of the second part in both directions. Apparatus according to claim 2. 5. The reduction coupling 26 is pivotally mounted on an axis defined by the shaft and adapted to move a pinion attached to the coupling, the elastic actuating force reduction device comprising at least one spring 60, 70, which One end is attached to a fixed point and the other end is attached to a pinion, which weakens the force applied to this pinion 63, absorbing the non-acting component of the force into the pinion axis and the acting component as a function of the stroke. 2. Device according to claim 1, adapted to obey the law of force variation. 6 The deceleration connection 26 is connected to at least one pinion 2
The pinions 28 and 20 mesh with the rack 27 attached to the coupling device 19, and are connected to the electric motor via the worm 31, and the pinion 63 attached to the elastic actuating force reducing device meshes with the rack 27. 6. A device according to claim 5 which is intermeshing.