JPH07107419B2 - Direction regulation transmission gear mechanism - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a thin direction regulation transmission gear mechanism having a rotation direction regulation function and a transmission function.

[Conventional technology]

A conventional direction control transmission gear mechanism is shown in FIGS. 4 and 5. FIG. 4 is a plan view showing a conventional direction-regulating transmission gear mechanism, which is composed of a ratchet gear 11b having six saw-toothed teeth 11a and a pinion 11c having 12 teeth of a normal tooth type on the drive side. A ratchet wheel 11 provided, a lever 21 engaged with a ratchet gear 11b of the ratchet wheel 11, and a gear 3 driven to mesh with a pinion 11c of the ratchet wheel 11.
It is composed of 1 and 1 and forms a normal positive transmission mesh. FIG. 4 shows a gear 3 which meshes with the pinion 11c of the ratchet wheel while the lever 21 alternately repeats left turn C'and right turn D'with the left rotation A'of the ratchet wheel 11.
1 is for rotating to the right B ', and FIG. 4 shows a state in which the lever 21 is turning to the left C'in its operation. θ
₅ and θ ₆ are the angle and the bottom of the saw tooth 11a of the ratchet gear 11b with respect to the center of the ratchet wheel 11, respectively.
The angle formed by 11d with respect to the center of the gear is θ ₇ and θ ₈
Are the angles formed by the engagement surface 21a of the lever 21 and the pitch between the two engagement surfaces 21a with respect to the center of the ratchet wheel 11, respectively. Θ _{5 so} that the return angle at becomes smaller,
θ ₆ and θ ₇ are substantially equal to each other, and θ ₈ is set to be approximately (2n + 1) times (n is an integer of 1 or more) times the same, and in the present embodiment, θ ₈ is approximately 3 times θ ₅ ( (when n = 1). Reference numerals 41, 51 and 61 denote a ratchet wheel shaft, a lever shaft and a gear shaft, respectively, which are rotation shafts of the ratchet wheel 11, the lever 21 and the gear 31, and the lever shaft 51 is substantially equal from the two locking surfaces 21b and 21c of the lever 21. It is located at a distance. FIG. 5 is a plan operation view showing the tensioned state at the time of reverse transmission rotation, in which the ratchet gear 11b is rotated along with the reverse transmission rotation E'of the ratchet wheel 11.
2 shows a state in which one of the two locking surfaces 21b and 21c of the lever 21 and the locking surface 11e of FIG. When the ratchet wheel 11 makes the reverse transmission rotation E'immediately after the lever 21 makes a left turn C ', as shown by the solid line, a strut is provided between the locking surface 21b of the lever 21 and the locking surface 11e of the ratchet gear 11b. If the ratchet wheel 11 makes a reverse transmission rotation E'immediately after the lever 21 makes a right turn D ', the engagement surface 21c of the lever 21 and the engagement surface 11e of the ratchet gear 11b are indicated by a chain double-dashed line. It is configured to generate a bracing between and.

[Problems to be solved by the invention]

In the conventional direction regulation transmission gear mechanism as described above, it is excellent in that it can be driven with a small force without using a jump control spring or the like in the ratchet lever, but in the normal transmission, the ratchet wheel is the driving side and the following train wheel. In order to drive, the tooth profile of the ratchet gear is significantly asymmetrical to the left and right, so it is not possible to transmit rotational force using the same tooth profile, and it is necessary to separately provide a pin for rotational transmission, which complicates the component configuration. In addition, it becomes thick in cross section, and there are many inconveniences especially when it is used for a timepiece train wheel or the like which is required to be thin and simple.

INDUSTRIAL APPLICABILITY The present invention solves the above-mentioned conventional problems, can be driven with a small force equivalent to the conventional one, and can be used to drive the subsequent train wheel by using the ratchet wheel tooth profile as it is, and the driving side and the driven side. It is an object of the present invention to provide a thin and simple direction control transmission gear mechanism that enables a combination of gears that keep a constant rotation speed ratio between and.

[Means for solving problems]

In order to achieve the above object, the present invention has the following configuration. That is, the direction control transmission gear mechanism according to the present invention has a first gear having a large fork width with respect to a tooth tip thickness, a turning center outside the first gear, and a radial direction of the first gear. Has two engaging portions each of which has a locking surface that substantially coincides with the locking surface and an engaging surface that forms an acute angle with the locking surface, and the two locking surfaces are approximately equidistant from the turning center and the first gear. With the lever provided to be shifted with respect to the tooth tip pitch of,
It is configured by a second gear that meshes with the first gear.

[Action]

With the above configuration, the lever rotates left and right by the engaging surface of the first gear to drive the second gear during normal rotation, but reverse transmission rotation is transmitted to the first gear for some reason. At this time, the locking surface of the first gear engages with the locking surface of the lever to prevent reverse transmission rotation of the first gear.

〔Example〕

 Embodiments of the present invention will be described below with reference to the drawings.

First Embodiment FIGS. 1 and 2 show a first embodiment of the direction-regulating transmission gear mechanism of the present invention. FIG. 1 is a plan view showing the meshing of the direction-regulating transmission gear mechanism of the present invention. The first gear 1 has eight teeth and has a large fork width with respect to the tip thickness, and the first gear 1. It is composed of an engaging lever 2 and a second gear 3 which is driven to mesh with the first gear. First
With the left rotation A of the gear 1, the lever 2 turns left C and turns right D
The second gear 3 meshing with the first gear 1 is rotating clockwise B while the lever 2 is turning left C, and θ ₁ and θ ₂ are the first gear 1 respectively. Is an angle formed by the tooth tip portion 1a and the tooth fork portion 1b with respect to the center of the gear, and θ ₃ and θ ₄ are the engaging surfaces 2a of the lever 2
And the angle between the two engagement surfaces 2a with respect to the center of the first gear 1. For each angle, lever 2 at the time of forward transmission
Of the first gear 1 until the lever 2 moves slowly and smoothly by using the largest possible rotation angle of the first gear 1 within a range that does not hinder the feeding of the first gear 1 and enters the reverse transmission circuit until it is engaged and locked. Θ ₂ so that the return angle of 1 also becomes smaller
≈ θ ₁ + 2θ ₃ , n (θ ₁ + θ ₂ ) + θ ₂ ≈θ ₃ + θ ₄
That is, θ ₄ ≈ (2n + 1) (θ ₁ + θ ₃ ) (n is an integer of 1 or more)
In this embodiment, θ ₄ ≈3 (θ ₁ + θ ₃ ) (when n = 1) so that the size of the lever 2 is minimized. 4, 5, and 6 are the first gear 1, the lever 2, and the second, respectively.
A first gear shaft serving as a rotation shaft of the gear 3, a lever shaft, and a second gear shaft. The lever shaft 5 has two locking surfaces 2b, 2c of the lever 2.
Are located approximately equidistant from. FIG. 2 is a plane operation view showing a tensioned state at the time of reverse transmission rotation, and with the reverse transmission rotation E of the first gear 1, the locking surface 1c of the first gear 1 and the lever 2
It shows a state in which one of the two locking surfaces 2b and 2c is stretched. When the first gear 1 makes the reverse transmission rotation E immediately after the lever 2 makes a left turn C, as shown by the solid line,
Immediately after the lever 2 makes a bulge between the engaging surface 2b of the lever 2 and the engaging surface 1c of the first gear 1 and immediately after the lever 2 turns right D
When the gear 1 rotates in the reverse transmission rotation E, as shown by the chain double-dashed line, a bulge is generated between the locking surface 2c of the lever 2 and the locking surface 1c of the first gear 1. 7 is lever 2
It is a stopper pin for restricting the turning angle range of the left turn C and the right turn D so that the tension does not occur during the left rotation A of the first gear 1.

Next, the operation will be described.

When the solid line position in FIG. 2 is the initial state, the lever 2 remains in the initial state and is stopped until the first gear 1 is rotated counterclockwise A by approximately (θ ₁ + θ ₃ ) to the two-dot chain line position.
Here, a state in which the first gear 1 is rotated counterclockwise by approximately (θ ₁ + θ ₃ ) from the initial state is referred to as a first state. When the first gear 1 further continues the left rotation A from the first state, the lever 2 turns right D
Starting from the first state, the lever 2 continues to turn right D from the first state until the first gear 1 rotates leftward A by approximately θ ₃ . Further, the first gear 1 is rotated counterclockwise A by an angle of approximately θ ₁ , and the lever 2 is stopped until the rotation angle of the first gear 1 becomes approximately (θ ₁ + θ ₃ ) starting from the first state. . Further, when the first gear 1 continues the left rotation A, the lever 2 starts the left turn C and the rotation angle of the first gear 1 is almost (θ ₁ +2) from the first state.
The lever 2 continues to turn left C until θ ₃ ). Further, the lever 2 is stopped until the rotation angle of the first gear 1 becomes approximately (2θ ₁ + 2θ ₃ ) from the first state by continuing the left rotation A of the first gear 1, and the first gear 1 and the lever 2 are separated from each other. The positional relationship coincides with the first state, and this operation is repeated thereafter. Here, the rotation angle of the first gear required for one cycle of the operation of the lever 2 is equal to one tooth tip pitch of the first gear, and 2θ ₁ + 2θ ₃ ≈θ ₁ + θ ₂ or θ ₂ ≈θ ₁ + 2θ
The relationship of ₃ is established. Further, the rotation angle θ of the first gear 1
₁ is a necessary and sufficient angle for stopping the lever 2 so as not to cause the tension when the first gear 1 rotates leftward, and when θ ₂ <θ ₁ + 2θ ₃ , the tension is applied even when left rotation A. Then, the rotation cannot be continued and θ ₂ > θ ₁ +2
At θ ₃ , the operation of the lever 2 with respect to the rotation of the first gear 1 becomes abrupt as much as the stopped state of the lever 2 becomes longer, and the smoothness of the operation is impaired. Further, in reality, the initial state is not necessarily the position indicated by the solid line, but various states, and the angle of the left rotation A of the first gear 1 from the initial state to the first state is not constant, but after the first state The operation of is repeated in the same manner as described above.

Second Embodiment FIG. 3 is a plan view showing a second embodiment of the direction regulation transmission gear mechanism of the present invention. The backlash between the first gear 1 and the second gear 2 in the first embodiment is reduced within a range that does not hinder the rotation operation, and meshes with the first gear 1 and is the same as the tooth profile of the second gear 2. The third gear 8 having a shape is provided, and the third gear shaft 9 serving as a rotation shaft of the third gear 8 is further provided with the first gear shaft 4
Shows the normal positive transmission meshing of the direction-regulating transmission gear mechanism arranged on a straight line passing through the second gear shaft 5 and the third gear 8
With the right rotation F of the first gear 1, the first gear 1 rotates left A and the lever 2
Shows a state in which the lever 2 is making a left turn C during the operation of rotating the second gear 3 to the right B while alternately operating the left turn C and the right turn D. In the figure, the number of teeth of the first gear 1 is eight and is even, and the third gear shaft 9 is the first gear shaft 4
Is arranged on a straight line passing through the second gear shaft 5 and each backlash is very small. Therefore, when the rotational angle position of the tooth profile of the first gear 1 is translated, the tooth profile of the third gear 8 is almost the same. It is configured to maintain the first gear 1 and the second gear 3 and the first gear 1 and the third gear 3.
The disadvantage that the rotational speed fluctuates with the gear 8 does not appear between the third gear 8 that is the driving side and the second gear 3 that is the driven side, and the rotational speed ratio is almost constant. This relationship is maintained even when the third gear 8 is rotated right F by using the right rotation B of the second gear 3 as a driving force. The arrangement condition of each gear shaft having a constant rotation speed ratio as described above is that the angle formed by the second gear shaft 5 and the third gear shaft 9 with respect to the center of the first gear shaft 4 is the first.
This is to be an integral multiple of the tip pitch angle of the gear 1. Further, in the present embodiment, the third gear 8 has the same shape as the second gear 3, but if the tooth profile is almost the same, it is possible to maintain the rotation speed substantially constant even if the tooth number ratio is changed.

Now, a case where the above-mentioned direction regulation transmission gear mechanism is applied to a part of a timepiece train wheel will be described.

For example, in a timepiece train wheel that is required to be thin and simple, when it is used for a back train wheel train that requires an arbitrary initial position adjustment for time display, slippage occurs in addition to the direction control transmission gear mechanism according to the present invention. Just by providing a mechanism, it is possible to perform initial adjustment by forward / reverse rotation at the needle turning position of the crown without requiring a structure for making a special correction state, and already having a correction function at the crown pulling position. It is possible to add more functions to the existing multi-function display timepiece, and it is possible to provide a more complete multi-function display timepiece.

〔The invention's effect〕

As described above, according to the present invention, the direction regulation transmission that is thin and simple, and can also keep the rotation speed ratio between the driving side and the driven side constant, without impairing the property of being driven by a small force equivalent to the conventional one. A gear mechanism can be provided, and the application range is very wide, and a great effect can be achieved.

[Brief description of drawings]

1 and 2 are a plan view and a plane operation view of a direction regulating transmission gear mechanism showing a first embodiment of the present invention, and FIG. 3 is a plan view showing a second embodiment of the present invention, FIG. 4 and FIG. FIG. 5 is a plan view and a plan operation view showing a conventional direction regulation transmission gear mechanism. 1 ... First gear, 2 ... Lever, 3 ... Second gear, 4 ... First gear shaft, 5 ... Lever shaft, 6 ... Second gear shaft, 7 ... Stopper pin, 8 ... Third gear, 9 ... Third gear shaft.

Claims (3)

[Claims] 1. A first having a tooth width that is large with respect to a tooth tip thickness.
Two engaging parts are provided, which are a gear and an engaging surface that has a center of rotation outside the first gear and that substantially coincides with the radial direction of the first gear and an engaging surface that forms an acute angle with the engaging surface. And a second gear that meshes with the first gear and that has the two locking surfaces that are provided at substantially equal intervals from the center of rotation and are displaced from the tip pitch of the first gear. A direction regulation transmission gear mechanism characterized by being made. 2. The angles formed by the addendum portion and the fork portion of the first gear with respect to the center of the gear are θ ₁ and θ ₂ , respectively, and the engaging surface forming an acute angle of the lever and the pitch between the two engaging portions. When the angles formed with respect to the center of the first gear are θ ₃ and θ ₄ , respectively,
₂ ≈ θ ₁ + 2θ ₃ , n (θ ₁ + θ ₂ ) + θ ₂ ≈θ ₃ + θ
_4. That is, the direction-regulating transmission gear mechanism according to claim 1, wherein it is set such that ₄ or θ ₄ ≈ (2n + 1) (θ ₁ + θ ₃ ) (n is an integer of 1 or more). 3. A backlash between the first gear and the second gear is reduced, and a third gear meshing with the first gear and having the same or substantially the same shape as the tooth profile of the second gear is provided. The direction control transmission gear mechanism according to claim 1 or 2.