JPS605812B2 - clutch mechanism - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a clutch mechanism that can be switched without requiring external power.

Various clutch mechanisms capable of switching and driving two output shafts have been proposed, but as shown in FIG. 1, many of them generally require external power when switching.

The clutch mechanism shown in the figure includes an output gear 6a having rotation shafts 5a and 5b on the left and right sides of a drive gear 4 connected to the motor via a gear box 2 and a rotation shaft (drive shaft) 3.
, 6b are arranged at a distance from each other, and a pair of idler gears ga, 9b are rotatably supported on a substantially T-shaped lever 8 having a rotation fulcrum 7, and the upper end of this lever 8 is connected to a solenoid 1.
One of the idler gears 9a, 9b is interposed between the drive gear 4 and one of the output gears 6a, 6b by moving the plunger 11 back and forth in one direction. Therefore, when the plunger 11 is sucked in the direction of the solid arrow by the solenoid 10 as shown, the idler gear 9a is interposed between the drive gear 4 and the output gear 6a,
The output gear 6a rotates in the same direction as the drive gear 4 rotates in the direction of the solid arrow (hereinafter referred to as normal rotation). Then, when the current to the solenoid is cut off, the plunger 11 moves in the direction of the broken line arrow due to the repulsive force of the coil spring 12.
An idler 9b is interposed between the drive gear 4 and the output gear 6b. As a result, the output gear 6b rotates in the same direction as the drive gear 4 rotates in the direction of the dashed arrow (hereinafter referred to as reverse rotation). However, since the clutch mechanism shown in FIG. 1 requires external power such as the solenoid 10 for switching, it has a large number of parts and a complicated structure, which makes it difficult to downsize and increases the cost.

In order to fundamentally solve these drawbacks, the present invention provides a clutch mechanism capable of two-way transmission that eliminates the need for external power by using internal power from a drive source such as a motor for switching operation. It is intended to.

The clutch mechanism of the present invention includes a driving rotating body rotated by a drive source, and first and second driven rotating bodies selectively rotated by the driving rotating body via a transmission rotating body. The proximal end of the output shaft is supported by the same D-shaped rotation shaft as the rotation axis of the drive rotation body, and the transmission rotation body is supported on the free end side, so that when the drive rotation body rotates in the forward and reverse directions, the drive rotation is A transmission rotating body is inserted between the driving rotating body and the first driven rotating body when rotated by the torque from the body, and when rotating in the normal direction, the transmitting rotating body is inserted between the driving rotating body and the second driven rotating body when rotating in the reverse direction. a lever for inserting a transmission rotor between the levers, and a state in which the transmission rotor is between the drive rotor and the first driven rotor and between the drive rotor and the second driven rotor; The device is characterized in that it consists of a first and a second stopper that hold the device in place, and will be described in detail below with reference to the drawings.

FIG. 2 is a diagram showing a first embodiment of the present invention in which each rotating body is a gear, and the same parts as in FIG. 1 are designated by the same reference numerals.

In Fig. 2, 21 is the rotation shaft (drive shaft) of the drive gear 4.
3, a lever having a rotating shaft 22 concentric with 3 on the base end 21a side, 23 a transmission gear that is pivotally supported by a rotating shaft 24 on the free end 21b side of the lever bar 21 and meshes with the drive gear 4; 25 lever bar 21;
3 and the transmission gear 23 (slip ring (
(rotational friction imparting means consisting of a helical spring, etc.), 26a
, 26b are a pair of stoppers that hold the substantially central lower end of the ladder bar 21 at the illustrated position and a rotational position 180° different from that; 27 is a spacer; 28a, 428b are pupil body frames. In the clutch mechanism of Yokinari described above, when the forward rotation output gear 6a is driven, it is in the state shown in the figure, and when the drive gear 4 rotates in the normal direction, the output gear 6a rotates in the normal direction via the transmission gear 23 (rotation in the direction of the solid line arrow).
do.

At this time, the transmission gear 23 extends and the lever bar 21 receives a reaction force, but this transmission reaction force R appears downward as shown in FIG. 2c. This reaction force R is received by the stopper 26a and keeps the lever 21 and the transmission gear 23 at the solid line position shown in the figure. If there is a slip ring 25 between the lever 21 and the transmission gear 23, this reaction force increases in accordance with the frictional force applied by the slip ring, but this is also suppressed by the stopper 26a, so that when the lever 21 There is no rotation in any clockwise direction. From this state, when the rotation direction of the motor 1 is reversed and the drive gear 4 is reversed, the transmission reaction force R' of the transmission gear 23 is
changes upward, the lever 21 rotates in the direction of arrow F, and the meshing state between the transmission gear 23 and the output gear 6a is released.

When the mesh is released, the reaction force R' disappears and the transmission gear 23
simply rotates freely, but in this mechanism, rotational friction is applied to the transmission gear 23 by the slip ring 25, so the reaction force due to this friction (also in the same direction as the reaction force Rr) pulls the lever 21. Then rotate it in the direction of arrow F.
Eventually, the transmission gear 23 revolves around the drive gear 4 while rotating (if the friction is large, the rotation stops and rapidly revolves), and the lever 21 moves counterclockwise approximately 180 degrees until it abuts against the stopper 26b. Spread around. Lever 21 is stopper 2
6b prevents further rotation, the transmission gear 2
3 is interposed between the drive gear 4 and the reverse rotation output gear 6b, as shown by the dashed line in FIG. 2c.

Then, when the drive gear 4 continues to rotate in reverse, the transmission gear 23
The output gear 6b rotates in the reverse direction when the stopper 26b receives the downward transmission reaction force R''.
No external power is required during operation.

This reduces the number of parts and simplifies the structure. Furthermore, since the power necessary for switching is obtained from the internal power source for driving the output gear, that is, the motor 1, there is an advantage that the clutch mechanism can be constructed using a part of the motor speed reduction mechanism. In the embodiment shown in Fig. 2, the frictional force is set to an appropriate level to stop the transmission gear 23 at the time of switching, and the frictional force caused by the slip ring 25 results in a loss during driving. If the reduction mechanism is used, the load on the motor 1 will be 1/50 of the frictional force of the slip ring 25.
There is no practical problem since it only adds so much. FIG. 3 is a diagram showing a second embodiment of the present invention in which each rotating body is a friction wheel, and the same parts as in FIG. 2 are given the same reference numerals.

Drive friction wheel 31, transmission friction wheel, or idler 3 in FIG.
2. The forward rotation and reverse rotation output friction wheels 33a, 33b correspond to the gears 4, 23, 6a, 6b shown in FIG. 2, respectively.
When the driving friction wheel 31 is rotating normally, a reaction force R appears in the clockwise direction, and the lever 21' is rotated to a position where it meets the stopper 26a. Therefore, the output friction wheel 33a rotates normally via the idler 32. Next, when the drive friction wheel 31 is reversed, a reaction force R appears in the opposite direction, and the transmission friction wheel 32 floats up. This transmission friction wheel 32 is the drive friction wheel 3
1, it is supported by the lever 21 so that it can be strongly pressed even in this floating state (34 is a spring for pressing the Hydra to do this), so it floats away from the output friction wheel 33a. and the idler 32 stops rotating,
As the driving friction wheel 31 rotates together with the lever 21, the shaft 22
Rotates around. Eventually, the lever 21 will move to the stopper 26b.
When the idler 32 is stopped and inserted between the drive friction wheel 31 and the output reversing friction wheel 33b, the output friction wheel 33b rotates in reverse via the idler 32. In the clutch mechanism of this embodiment, since there is a constant frictional force between the drive friction wheel 31 and the idler 32 and between the idler 32 and the bar 21, the slip ring 25 shown in FIG. 2 is not necessary.

Shafts 24, 5 of idler 32 and output friction wheels 33a, 33b
Distance between a and 5b Now, of course, the lever 21 is at the stopper 26a.
The idler 32 and the output friction wheel 33a are
In other words, the idler 32 is set to be press-fitted between the friction wheel 31 and 33a or 33b so that the required transmission force can be obtained by the frictional force between them. FIG. 4 is a diagram showing a third embodiment of the present invention.

In this embodiment, the rotating body is a gear as in FIG. 2, but the transmission gear 41 is simply rotatably supported by the lever 21. That is, in this embodiment, the slip ring 25 shown in FIG. 2 is not required, and since the rotational friction that existed in the ones shown in FIGS. 2 and 3 is substantially absent, the transmission loss is reduced. However, instead of this, a deformable leaf spring 42 is provided. As shown in the figure, the leaf spring 42 has a symmetrical shape having four claws 42a, 42b, 42c, and 42d, and is fixed at the center by a screw 43, and each of the left and right halves of the claw group exhibits an elastic action independently. In the state shown in the figure, rotational force is transmitted from the drive gear 4 to the normal rotation output gear 6a via the transmission gear 41, and a reaction force R is generated in the clockwise direction.

The point that this reaction force R is received by the stopper 26a is the same as in each of the embodiments described above. Next, when the drive gear 4 is reversed, the reaction force R that the transmission gear 41 receives becomes counterclockwise, and the transmission gear 41 reaches the position where the meshing state with the output gear 6a is released (indicated by the broken line in the figure). The transmission gear 41 rotates slightly around the driving gear 4 together with the transmission lever 21. At this point, the transmission gear 41 is connected to the catch 42a of the leaf spring 42, and the transmission gear 41 is prevented from rotating by this pawl 42a. Therefore, when the driving gear 4 further reverses, the transmission gear 41 revolves around the driving gear 4 while deflecting the pawl 42a inward (in the direction of arrow R'), and reverses the rotation through the pawls 42b, 42c, and 42d. It is connected to the output gear 6b.At this point, the transmission gear 4
1 has already separated from the leaf spring 42, and the counterclockwise reaction force is received by the stopper 26b. Therefore, the output gear 6b is driven via the transmission gear 41 and rotates in reverse. The pawls 42a to 42d of the leaf spring 42 operate sequentially during transition from normal rotation to reverse rotation or from reverse rotation to normal rotation, and prevent the transmission gear 41 from rotating along the dotted line F' path.

Pawls 42c, 42d when changing from normal rotation to reverse rotation, or pawls 42b, 42c when changing from reverse rotation to normal rotation.Although it is unnecessary considering the weight of the lever 21 and transmission gear 41, it is possible to horizontally position the clutch mechanism shown in the figure. In other words, all of them are required if each rotating axis is made vertical. As described above, the clutch mechanism of the present invention is capable of switching the power transmission between the two output shaft systems without requiring external power, so it can be made compact and inexpensive due to the reduction in the number of parts.

Therefore, it is effective to apply the present invention to a forward/reverse drive device as shown in FIG. 5, for example. The figure shows a pair of winding drums 51a,
This is a so-called map display in which a long map 52 on which a road map or the like is displayed is wound between the 51b and 51b. In the example shown in FIG. 5, the clutch mechanism shown in FIG. 2 is applied, and the output gear 6
The respective shafts 5a, 5b of a, 6b are connected to drums 51a, 51b. Incidentally, 53 and 54 are the output gears 6a and 6b spaced apart according to the interval between the drums 51a and 51b, and the bar 2.
An even number of idler gears are interposed to match the length of 1. In the illustrated state, the map 52 is sent in the direction of arrow F, and the motor is reversed to shift the transmission gear 23 to gear 4,
54, the map will be sent in the opposite direction of F2,
For example, the driver can drive the car while viewing the selected road map.

[Brief explanation of drawings]

1A and 1B are a perspective view and a side view showing an example of a conventional clutch mechanism; FIGS. 2A, B and C are a perspective view, a top view and a side view showing a first embodiment of the present invention; Figures 3a and 3b are a plan view and a side view showing the second embodiment of the present invention;
The figure is a side view showing a third embodiment of the present invention, and FIG. 5 is a perspective view of a map display to which the clutch mechanism of the present invention is applied. 1: Motor, 2: Gabox, 3: Rotating shaft (drive shaft)
, 4: Drive gear, 5a, 5b, 22, 24: Rotating shaft, 6
a, 6b: Output gear, 21: Lever, 23, 32, 41
: Transmission gear, 25: Slip ring, 26a, 26b:
Stopper, 31: Drive friction wheel, 33a, 33b: Output friction wheel, 42: Leaf spring, 42a to 42d: Claw, 51a, 5
1b: Winding drum, 52 mimap, 53, 54; idler gear. Figure 1 Figure 2 Figure 3 Figure 4 Figure 5

Claims (1)

[Scope of Claims] 1. A driving rotary body rotated by a drive source; a first rotary body selectively rotated by the driving rotary body via a transmission rotary body;
First and second output shafts each include a second driven rotary body, the base end of which is rotatably supported by a rotary shaft concentric with the rotary shaft of the drive rotary body, and the transmission rotary body is pivoted on the free end of the first and second output shafts. When the driving rotating body rotates in the forward and reverse directions, the transmission rotating body is inserted between the driving rotating body and the first driven rotating body. a lever for inserting a transmission rotation body between the drive rotation body and a second driven rotation body; and a lever for inserting the transmission rotation body between the drive rotation body and the first driven rotation body and the drive rotation body. A clutch mechanism comprising first and second stoppers that are held between a second driven rotating body and a second driven rotating body. 2. Claims characterized in that the driving rotary body, the transmission rotary body, and the driven rotary body are all gears, and the transmission rotary body is rotatably supported by a lever with rotational friction applied by a rotational friction imparting means. Clutch mechanism according to item 1. 3. Claims characterized in that the driving rotating body, the transmitting rotating body, and the driven rotating body are all friction wheels, and the driven rotating body is driven by the driving rotating body via the transmitting rotating body due to frictional coupling. Clutch mechanism according to item 1. 4. The drive rotor, the transmission rotor, and the driven rotor are all gears, and the drive rotor is provided with a leaf spring that prevents the rotation of the transmission rotor that floats up due to reaction force when the rotation direction of the drive rotor is changed. A clutch mechanism according to claim 1.