JP5975808B2 - Switch operating mechanism - Google Patents

Description

  The present invention relates to an operation mechanism of a switch for protecting or switching an electric power system, for example, and more particularly to a meshing structure of a large gear and a small gear in the operation mechanism.

  Conventionally, in a switch operating mechanism, a large gear that is fixedly provided concentrically with a cam and has a partially-toothed portion and a groove portion in the partially-toothed portion is engaged with the large gear. One having at least two first teeth and second teeth with a small gear rotatably driven by a driving source and a groove formed in a toothless portion of the large gear so that one side can swing freely. And a spring that presses the other side of the synchronization claw.

  The synchronization pawl is in a position where it meshes with the first gear located on the other side of the small gear and the synchronization pawl immediately after the completion of the energization of the closing spring, and the second tooth located on one side of the synchronization pawl is meshed after the closing operation is started. In some cases, the small gear is configured to be able to smoothly re-engage with the large gear. In addition, between the 1st tooth | gear and 2nd tooth | gear of a synchronous nail | claw, it is in the state which lost one tooth part.

Japanese Patent No. 2529309 JP 2003-31089 A

  The operation mechanism of the conventional switch described above has a missing tooth with one tooth missing between the first tooth and the second tooth provided on one synchronous claw, and the closing operation starts. Thereafter, the large gear is accelerated and rotated by one pitch of the small gear and the missing tooth of the synchronous claw, and collides with and engaged with the second tooth of the synchronous claw, so that an impact force is generated. The impact force at this time collides with a small gear stationary at a so-called angular momentum, which is the product of rotational inertia including the rotational speed of the large gear and the closing spring rod and closing spring connected to the large gear, the closing spring, the cam, and the camshaft. As a result, this is a generated force, and the impact force increases in proportion to the rotational speed of the large gear. When the impact force is increased, the tooth pressure of the second tooth of the synchronous claw and the surface pressure of the small gear are increased, and there is a problem that the second tooth is worn when the number of energy accumulation operations is large.

  The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a switch operating mechanism that can withstand a large number of energy storage operations with low impact force and low tooth wear. To do.

  A switch operating mechanism according to the present invention includes a drive lever that drives a switch that opens and closes an electric circuit, and an operation unit that operates the drive lever, wherein the operation unit includes a motor that generates rotational energy, Connected to the first transmission mechanism for transmitting the rotational energy of the electric motor, the second transmission mechanism that is engaged with the first transmission mechanism and partially formed with a missing tooth portion, and the second transmission mechanism And a notch portion in which a toothless portion of the second transmission mechanism is formed, and one side of the notch portion is swingably supported by the notch portion. A first synchronous claw having one tooth and a second tooth, the pitch between the first tooth and the second tooth being configured as a missing tooth; and the first synchronous claw at the notch Arranged in parallel and supported by one side so as to be swingable, in front of the first synchronizing claw Those made up of a second synchronization pawl having a third tooth missing tooth position between the second teeth and the first teeth.

  According to the switch operating mechanism according to the present invention, it is possible to obtain a switch operating mechanism that is inexpensive and can withstand a large number of switching operations.

It is a block diagram which shows the closed circuit state in the operating mechanism of the switch concerning Embodiment 1 of this invention. It is a block diagram which shows the open circuit state in the operating mechanism of the switch concerning Embodiment 1 of this invention. It is a block diagram which shows the operating mechanism of the switch concerning Embodiment 1 of this invention. It is a left view of FIG. 3 in the operating mechanism of the switch concerning Embodiment 1 of this invention. It is a right view of FIG. 3 in the operating mechanism of the switch concerning Embodiment 1 of this invention. It is the other side sectional view of the AA line of Drawing 3 in the switch operating mechanism concerning Embodiment 1 of this invention. It is a perspective view which shows the large gear, the small gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the operation mechanism of the switch concerning Embodiment 1 of this invention. It is a front view which shows the large gear, the small gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the operating mechanism of the switch concerning Embodiment 1 of this invention. It is the figure seen from the toothless part outer peripheral side of the large gear which shows the large gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the operation mechanism of the switch concerning Embodiment 1 of this invention. It is a block diagram which shows the meshing process of the large gear, the small gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the accumulation | storage stage of the operating mechanism of the switch concerning Embodiment 1 of this invention. It is a block diagram which shows the meshing process of the large gear, the small gear, the 1st synchronizing claw, and the 2nd synchronizing claw at the time of completion | finish of accumulation of energy of the operating mechanism of the switch concerning Embodiment 1 of this invention. It is a block diagram which shows the meshing process of the large gear, the small gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the release stage of the operating mechanism of the switch concerning Embodiment 1 of this invention. It is a block diagram which shows the meshing process of the large gear, the small gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the release completion of the operating mechanism of the switch concerning Embodiment 1 of this invention. It is the figure seen from the toothless part outer peripheral side of the large gear which shows the large gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the operation mechanism of the switch concerning Embodiment 2 of this invention. It is the figure seen from the toothless part outer peripheral side of the large gear which shows the large gear, the 1st synchronizing claw, and the 2nd synchronizing claw in the operation mechanism of the switch concerning Embodiment 3 of this invention. It is a block diagram which shows the operating mechanism of the switch concerning Embodiment 4 of this invention.

Embodiment 1 FIG.
Hereinafter, Embodiment 1 of the present invention will be described with reference to FIGS. 1 to 9. In each figure, the same or equivalent members and parts will be described with the same reference numerals. 1 is a configuration diagram showing a closed state in an operating mechanism of a switch according to Embodiment 1 of the present invention. FIG. 2 is a configuration diagram showing an open circuit state in the switch operating mechanism according to the first embodiment of the present invention. FIG. 3 is a block diagram showing the operating mechanism of the switch according to Embodiment 1 of the present invention. 4 is a left side view of FIG. 3 in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 5 is a right side view of FIG. 3 in the operating mechanism of the switch according to Embodiment 1 of the present invention. 6 is a cross-sectional side view taken along line AA of FIG. 3 in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 7 is a perspective view showing a large gear, a small gear, a first synchronization claw, and a second synchronization claw in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 8 is a front view showing a large gear, a small gear, a first synchronization claw, and a second synchronization claw in the switch operating mechanism according to Embodiment 1 of the present invention. FIG. 9 is a view as seen from the outer peripheral side of the toothless portion of the large gear showing the large gear, the first synchronizing pawl, and the second synchronizing pawl in the switch operating mechanism according to Embodiment 1 of the present invention.

  In each of these drawings, 1 is a vacuum valve, 2 is a fixed side electrode disposed in the vacuum valve 1 and fixed to the fixed energizing shaft 3, and is electrically connected to the upper junction 4 through the fixed energizing shaft 3. . Reference numeral 5 denotes a movable side electrode which is disposed in the vacuum valve 1 and is opposed to the fixed side electrode 2 and fixed to the movable energizing shaft 6, and is electrically connected to the lower junction 7 through the movable energizing shaft 6. . Reference numeral 8 denotes an insulated operating rod, and one side, that is, the upper end side of the operating rod 8 is attached to a lower end portion extending outside the vacuum valve 1 of the movable energizing shaft 6, and the other side of the operating rod 8, that is, The lower end side is inserted into the base frame 9 and positioned in the base frame 9.

Reference numeral 10 denotes a support shaft whose axis is arranged so as to be orthogonal to the opening / closing direction between the fixed electrode 2 and the movable electrode 5 of the vacuum valve 1, that is, the axis of the operation rod 8. Is pivotally supported. Reference numeral 11 denotes a drive lever fixed to the support shaft 10, and one side 11a of the drive lever 11 is connected to one side 110a of an output link 110 which is an operation mechanism unit 100 described later by a connection pin 12, and the drive lever 11 is The support shaft 10 is rotated through.
The other side 11b of the drive lever 11 is connected to the other side, which is the lower end side of the operating rod 8, by a connecting pin 13 so as to be freely rotatable. By the operation of the operation mechanism unit 100, the operation rod 8 is operated in the vertical direction by rotating the support shaft 10 via the drive lever 11, and the opening between the fixed side electrode 2 and the movable side electrode 5 of the vacuum valve 1 is opened. Operation and closing operation are performed.

  The operation mechanism unit 100 includes an electric motor 101, an accumulator shaft 104 that is driven by being engaged with an intermediate gear 103 by an output gear 102 of the electric motor 101, and an intermediate shaft provided concentrically with the intermediate gear 103 on the accumulator shaft 104. A small gear 105 that constitutes a first transmission mechanism together with the gear 103, and a second transmission mechanism that is engaged with the small gear 105 and provided concentrically with the cam shaft 106, and in which part of the toothless portion 107a is formed. A large gear 107, a large gear 107 and a camshaft 106, which are integrated with each other, and a closing cam 108 that rotates in conjunction with the large gear 107, and one side is engaged with the closing cam 108, and the main shaft 109 is configured to be rotatable about a fulcrum, the other side is connected to the other side 110b of the output link 110 by the connecting pin 111, and the one side 113a is connected to the large pin through the connecting pin 114. The closing spring 116 is mounted on the other side 113b via the closing spring seat 115, and is composed of a closing spring rod 113 that stores and releases the closing spring 116 by rotation of the large gear 107. Yes. An energizing mechanism is constituted by the closing spring rod 113 and the closing spring 116.

  117 is a frame, 118 is one side 118a pivotally connected to the output lever 112 via a connecting pin 119, and the other side 118b is an open spring rod to which an open spring 121 is attached via an open spring seat 120, 122 is a limit switch , 123 is a closing coil, 124 is a closing latch, 125 is a closing latch pin that engages with the closing latch 124, 126 is a closing trigger, 127 is a releasing latch, 128 is a releasing latch pin, and 129 is a releasing trigger.

Reference numeral 130 denotes a notch formed in the missing tooth portion 107a of the large gear 107, and is configured as a concave groove portion at the center in the thickness direction of the missing tooth portion 107a of the large gear 107, for example, as shown in FIG. Shows the case.
Reference numeral 131 denotes a notch portion 130 which is a concave groove portion formed in the missing tooth portion 107a of the large gear 107, and is supported by one side so as to be swingable. At least two first teeth 131a and second teeth are arranged. It is the 1st synchronous claw which has 131b, and one pitch part between the 1st tooth 131a and the 2nd tooth 131b is a missing tooth.
132 is disposed in parallel with the first synchronization pawl 131 and supported on one side so as to be swingable in a notch 130 which is a concave groove formed in the toothless portion 107 a of the large gear 107. The second synchronous claw having the third tooth 132a at the missing tooth position between the first tooth 131a and the second tooth 131b of the first synchronous claw 131.

The first synchronization claw 131 and the second synchronization claw 132 are supported so as to be able to swing freely around the synchronization shaft 133, and the tooth shapes of the first synchronization claw 131 and the second synchronization claw 132 are the same. The position of the large gear 7 is restricted by a pin 134 attached to the large gear 7 at a position where the tooth profile and the pitch circle are the same.
135 is a first return spring that presses the other side of the first synchronization pawl 131, 136 is a second return spring that presses the other side of the second synchronization pawl 132, and does not mesh with the small gear 105, The first synchronization claw 131 and the second synchronization claw 132 are pressed against the pin 134.

  Next, the operation of the mechanism configured as described above will be described. The drive lever 11 is connected to an output lever 112 fixed to the main shaft 109 which provides a counterclockwise rotational force by an opening spring 121, and the engagement position is set by engagement of the release latch 127 and the release latch pin 128. Is maintained. When the trip latch 127 rotates counterclockwise by the trip trigger 129, the output link 110 moves upward, and the drive lever 11 rotates clockwise about the support shaft 10 by the upward movement of the output link 110. When the drive lever 11 rotates clockwise with the support shaft 10 as a fulcrum, the operating rod 8 moves downward, the movable energizing shaft 6 connected to the operating rod 8 also moves downward, and the movable electrode 5 is opened. The

  A crank is inserted between the center of the large gear 107 fixed to the cam shaft 106 and is rotated together with the cam shaft 106 and a connecting pin 114 provided on the side surface thereof. A lever crank mechanism (hereinafter simply referred to as a mechanism) is formed by using a connecting pin 114 and a closing spring rod 113 provided on the side surface as a connecting rod.

The large gear 107 is stopped at the closing standby position slightly shifted clockwise from the thought point of the mechanism by the closing latch 124. When the closing latch 124 rotates counterclockwise, the large gear 107 rotates counterclockwise by the mechanical energy stored in the closing spring 116.
The closing cam 108 fixed to the cam shaft 106 together with the large gear 107 rotates to return the driving lever 11 in the open position to the closing position against the rotational force of the opening spring 121. That is, the output link 110 moves downward, and the drive lever 11 rotates counterclockwise about the support shaft 10 by the downward movement of the output link 110. When the drive lever 11 rotates counterclockwise with the support shaft 10 as a fulcrum, the operating rod 8 moves upward, the movable energizing shaft 6 connected to the operating rod 8 also moves upward, and the movable electrode 5 is closed. Is done.
When the small gear 105 meshed with the large gear 107 rotates counterclockwise, the large gear 107 rotates clockwise against the rotational force of the closing spring 116, and returns to the state shown in FIG. Each element described above is incorporated in the frame 117 to form an operation mechanism section.

Next, the operation of the meshing portion between the large gear 107 and the small gear 105 will be described. As shown in FIGS. 7 and 8, a portion of the large gear 107 facing the small gear 105 is formed with a missing tooth portion 107a from which a predetermined number of teeth are removed, and the missing tooth portion 107a is, for example, a central portion in the thickness direction. A notch 130 is provided as a concave groove.
A first synchronous claw 131 having at least two first teeth 131a and second teeth 131b having the same shape as the tooth shape of the large gear 107 is provided in the notch portion 130 formed in the toothless portion 107a of the large gear 107. One of the pitches between the first teeth 131a and the second teeth 131b of the first synchronization pawl 131 is missing.

Further, in the notch portion 130 formed in the missing tooth portion 107a of the large gear 107, the first synchronizing claw 131 is disposed in parallel with the first synchronizing claw 131 between the first tooth 131a and the second tooth 131b. A second synchronization claw 132 having third teeth 132a is disposed at the missing tooth position, and the first synchronization claw 131 and the second synchronization claw 132 are rotatably disposed on the large gear 107 so as to be swingable. Attached to the synchronized shaft 133.
In addition, a first return spring 135 and a second return spring 136 are disposed on the first synchronization pawl 131 and the second synchronization pawl 132 so as to be able to return, respectively, and the first return spring 135 and the second return spring 136 are provided. Of the first return spring 135 and the second return spring 136 are respectively in contact with the first synchronization pawl 131 and the second synchronization pawl 132, respectively. The first return spring 135 and the second return spring 136 are brought into contact with the other side and rotate around the synchronization shaft 133 in the radial direction of the large gear 107, but the tooth shapes of the first synchronization pawl 131 and the second synchronization pawl 132. However, the position of the large gear 107 is regulated by a pin 134 attached to the large gear 107 at a position where the tooth profile of the large gear 107 is the same as the pitch circle.

  For this reason, when the small gear 105 rotates counterclockwise and the first teeth 131a on the side away from the synchronization shaft 133 of the first synchronization pawl 131 also mesh and press the tooth surface, the relationship between the pressure angles of the contact tooth surfaces Therefore, the counterclockwise rotational moment acts on the first synchronizing claw 131, and the clockwise rotation about the synchronizing shaft 133 disengages from the small gear 105 to rotate the large gear 107. Absent.

  On the other hand, when the large gear 107 rotates counterclockwise, the first teeth 131a on the side of the first synchronization pawl 131 away from the synchronization shaft 133 mesh with the small gear 105, and the pressing force acting on the first teeth 131a. Acts as a rotational moment for rotating the first synchronizing claw 131 counterclockwise, but the second synchronizing claw 132 is constrained by a pin 134 in the radial direction of the large gear 107 and rotates around the synchronizing shaft 133. Since this is not possible, the posture of the second synchronization pawl 132 remains the same as shown, and the small gear 105 rotates.

  Next, the energy storage operation will be described with reference to FIGS. When the rotation of the large gear 107 advances in the counterclockwise direction and the power supply of the electric motor 101 is stopped by the limit switch 122 at the position where the closing spring rod 113 exceeds the thought point, the rotational force of the output gear 102 of the electric motor 101 is rotated after inertia. Although no force is generated, a force that rotates the large gear 107 counterclockwise is exerted via the closing spring rod 113 due to the force of the closing spring 116, so that the large gear 107 rotates counterclockwise as shown in FIG. However, the small gear 105 rotates clockwise to disengage from the large gear 107, and the first tooth 131 a of the first synchronization pawl 131 is pushed by the tooth tip of the small gear 105, and the spring force of the first return spring 135 is pushed. In contrast, the first synchronization pawl 131 rotates counterclockwise about the synchronization shaft 133 as a fulcrum. Further, when the large gear 107 rotates counterclockwise, the small gear 105 rotates clockwise due to inertia as shown in FIG. 11, and the first teeth 131 a of the first synchronization pawl 131 are moved by the first return spring 135. The closing latch pin 125 and the closing latch 124 which are returned by the spring force and meshed between the teeth of the small gear 105 and rotatably mounted on the large gear 107 are engaged with each other, and the energy storage of the closing spring 116 is completed.

Next, the input operation will be described with reference to FIGS. When an electrical command is input to the making coil 123 that drives the making trigger 126, the making coil 123 is excited, the making trigger 126 rotates counterclockwise, and the making latch 124 and the making latch pin 125 are disengaged. Thus, the large gear 107 rotates counterclockwise by the force of the closing spring 116. As shown in FIG. 12, the small gear 105 is not rotating, and after meshing with the third tooth 132a of the second synchronization pawl 132, the large gear 107 further rotates counterclockwise, not shown. However, the third tooth 132a of the second synchronizing claw 132 is pushed by the tooth tip of the small gear 105 and the second synchronizing claw 132 counterclockwise with the synchronizing shaft 133 as a fulcrum against the spring force of the second return spring 136. Rotate in the direction. Further, when the large gear 107 rotates counterclockwise, the small gear 105 meshes with the second teeth 131b of the first synchronization pawl 131 (not shown). At this time, the third teeth 132 a of the second synchronization pawl 132 are restored by the spring force of the second return spring 136.
When the large gear 107 further rotates counterclockwise, the small gear 105 is disengaged from the second teeth 131b of the first synchronization pawl 131 as shown in FIG. The meshing of the large gear 107 and the small gear 105 is restored, and the small gear 105 is also rotated in the clockwise direction to start storing energy.

  An accumulator shaft 104 having a small gear 105 attached to the tip is provided with a middle gear 103 incorporating a one-way clutch (not shown) that meshes clockwise but does not mesh counterclockwise. For this reason, the accumulator shaft 104 with the large gear 107 and the small gear 105 attached thereto rotates, but the load of the gear train below the intermediate gear 103 is not transmitted. Therefore, since the rotational inertia of the gear train below the middle gear 103 is not a load, the potential energy of the closing spring 116 is effectively converted into the kinetic energy of the closing operation, and a predetermined closing speed can be obtained.

  Next, the accumulating operation will be described. A one-way clutch (not shown) fixed to the frame of the motor 101 is provided so that the shaft on which the output gear 102 of the motor 101 is attached is constrained to rotate clockwise and can rotate freely counterclockwise. ing.

The intermediate gear 103 meshes with the output gear 102 of the electric motor 101. When electric energy is injected into the motor 101, the output gear 102 of the motor 101 rotates counterclockwise. The intermediate gear 103 engaged with the output gear 102 rotates in the clockwise direction. However, when a one-way clutch (not shown) built in the intermediate gear 103 rotates in the clockwise direction, the intermediate gear 103 is engaged with the accumulator shaft 104, and the accumulator shaft 104. Also rotate clockwise.
Since the load of the closing spring 116 is acting on the intermediate gear 103, counterclockwise rotational torque acts, and the clockwise rotational torque of the output gear 102 of the motor 101 acts, but the rotation is restricted by a one-way clutch. Therefore, the output gear 102 does not rotate clockwise.

Due to the counterclockwise rotation of the output gear 102 of the electric motor 101, the intermediate gear 103 rotates clockwise, and the intermediate gear 103 has a built-in one-way clutch that meshes with the energy storage shaft 104 in the clockwise direction. The small gear 105 attached to the shaft 104 and the accumulator shaft 104 also rotates in the clockwise direction.
Due to the clockwise rotation of the small gear 105, the large gear 107 rotates counterclockwise, and the closing spring rod 113 rotatably attached to the large gear 107 moves upward. A closing spring 116 is attached by a closing spring seat 115. The opposite end of the closing spring 115 of the closing spring 116 is in contact with the frame 117. Due to the upward movement of the closing spring rod 113, the closing spring seat 115 also moves upward.
As a result, the closing spring 116 is compressed. The structure is such that the counterclockwise rotation of the large gear 107 proceeds to perform an accumulating operation, the closing latch pin 125 and the closing latch 124 are engaged, and the operation of maintaining the storing force of the closing spring 116 is repeated.

  As described above, according to the present invention, the third tooth of the second synchronizing pawl 132 disposed in the notch portion 130 provided in the missing tooth portion 107a of the large gear 107 due to the rotation of the large gear 107 when being turned on. Since the collision between the gear 132a and the small gear 105 is a collision by rotating the tooth of the large gear 107 by one pitch, the impact between the teeth and the teeth is low and the impact force is small. Thus, it is possible to provide a switchgear with a high reliability and a low number of gears, with little wear on the gears.

Embodiment 2. FIG.
A second embodiment of the present invention will be described with reference to FIG. In the first embodiment described above, the notch 130 formed in the toothless portion 107a of the large gear 107 is configured as a concave groove at the central portion in the plate thickness direction of the large gear 107, and is configured as the concave groove. Although the case where the first synchronization claw 131 and the second synchronization claw 132 are arranged in parallel in the notch portion 130 is shown, in the second embodiment, the missing tooth portion 107a of the large gear 107 is shown. A notch portion 230 and a notch portion 231 are formed on both surfaces, a first synchronization claw 131 is provided in the notch portion 230, and a second synchronization claw 132 is provided in parallel in the notch portion 231. Thus, the same effects as those of the first embodiment described above can be obtained. Further, the notch portion 230 and the notch portion 231 of the second embodiment can be formed more easily than the notch portion 130 of the first embodiment described above.

Embodiment 3 FIG.
A third embodiment of the present invention will be described with reference to FIG. In the first embodiment described above, the notch 130 formed in the toothless portion 107a of the large gear 107 is configured as a concave groove at the central portion in the plate thickness direction of the large gear 107, and is configured as the concave groove. Although the case where the first synchronization claw 131 and the second synchronization claw 132 are arranged in parallel in the notch portion 130 is shown, in the third embodiment, the missing tooth portion 107a of the large gear 107 is shown. The notch part 232 is formed on one side surface, and the first synchronizing claw 131 and the second synchronizing claw 132 are arranged in parallel in the notch part 232, and the same effect as in the first embodiment described above. Play. Further, the cutout portion 232 of the third embodiment can be formed more easily than the cutout portion 130 of the first embodiment described above.

Embodiment 4 FIG.
Embodiment 4 of the present invention will be described with reference to FIG. In the figure, the large gear 107 has a notch 130 (not shown) similar to that of the first embodiment described above, and the notch 130 has at least two second gears having the same shape as the tooth profile of the large gear 107. A first synchronizing claw 131 (not shown) having one tooth 131a and a second tooth 131b is disposed, and one between the first tooth 131a and the second tooth 131b of the first synchronizing claw 131 (not shown). One pitch is missing.

  Further, in the notch portion 130 formed in the missing tooth portion 107a of the large gear 107, the first synchronizing claw 131 is disposed in parallel with the first synchronizing claw 131 between the first tooth 131a and the second tooth 131b. A second synchronization claw 132 (not shown) having third teeth 132a is disposed at the missing tooth position, and the first synchronization claw 131 and the second synchronization claw 132 are arranged on the large gear 107 so as to be swingable. A first return spring 135 and a second return spring are attached to a synchronous shaft 133 (not shown) that is rotatably arranged, and can be returned to the first synchronous claw 131 and the second synchronous claw 132, respectively. A spring 136 is provided, and the other ends of the first return spring 135 and the second return spring 136 are fixed to the notch portion 130 of the large gear 107 on the bottom side.

  Further, the first return spring 135 and the second return spring 136 have the first synchronization claw 131 and the second synchronization claw 132 rotate around the synchronization shaft 133 in the radial direction of the large gear 107, but the first synchronization claw 131. And the position of the second synchronous claw 132 is regulated by a pin 134 that is pivotally attached to the large gear 107 so that the tooth profile of the large gear 107 is the same as that of the large gear 107. The accumulator shaft 104 with the small gear 105 meshing with the large gear 107 is pivotally supported by a bearing box 138 disposed on one side of the operation mechanism frame 137 so as to be rotatable with respect to the bearing.

  In the other operation mechanism frame 137, the accumulator shaft 104 rotates freely in the clockwise direction in the bearing box 139 constrained to rotate around the accumulator shaft 104, but constrains the rotation in the counterclockwise direction. The one-way clutch 140 is press-fitted, and bearings 141 are press-fitted on both sides of the one-way clutch 140 to stabilize the clutch function of the one-way clutch 140.

  An accumulator shaft 104 having a small gear 105 mounted at the tip is provided with an intermediate gear 103 having a built-in one-way clutch 142 that meshes clockwise but does not mesh counterclockwise. For this reason, the accumulator shaft 104 with the large gear 107 and the small gear 105 attached thereto rotates, but the load of the gear train below the intermediate gear 103 is not transmitted. The accumulator shaft 104 meshes with the output gear 102 of the electric motor 101. Unlike the above-described first embodiment, the output gear 102 of the electric motor 101 does not include a one-way clutch.

Next, the operation will be described. When electric energy is injected into the motor 101, the output gear 102 of the motor 101 rotates counterclockwise.
The intermediate gear 103 engaged with the output gear 102 rotates in the clockwise direction. However, since the load of the closing spring 116 is applied to the intermediate gear 103, the counterclockwise rotational torque is applied to the output of the electric motor 101. Although the clockwise torque acts on the gear 102, the output gear 102 does not rotate in the clockwise direction because it is constrained by the rotation by the one-way clutch. As the output gear 102 of the electric motor 101 rotates counterclockwise, the intermediate gear 103 rotates clockwise, and the intermediate gear 103 has a built-in one-way clutch 142 that meshes with the accumulator shaft 104 in the clockwise direction. The small gear 105 attached to the force shaft 104 and the energy storage shaft 104 also rotates in the clockwise direction.

The rotation of the small gear 105 in the clockwise direction causes the large gear 107 to rotate in the counterclockwise direction, and the closing spring rod 113 that is rotatably attached to the large gear 107 moves upward to store the closing spring 116. It is the same as that of Embodiment 1 mentioned above, and abbreviate | omits illustration below. When electrical energy is applied to the making coil 123 from the outside, the making coil 123 is excited, the making latch 124 rotates counterclockwise, and the making latch 124 also rotates counterclockwise to disengage from the making latch pin 125. The large gear 107 on which the closing latch pin 125 is rotatably mounted starts to rotate counterclockwise.
At this time, since the small gear 105 can freely rotate in the clockwise direction, the small gear 105 meshes with the teeth of the second synchronizing claw 132, and then meshes with the teeth near the synchronizing shaft 133 of the first synchronizing claw 131. Rotates counterclockwise. The large gear 107 meshes with the teeth of the large gear 107, and the large gear 107 and the small gear 105 are rotated by the closing spring 116.

  The input cam 108 fixed to the cam shaft 106 rotates together. The closing cam 108 returns the driving lever 11 in the open position to the closing position against the rotational force of the opening spring 121 and closes the movable electrode 5. After the large gear 107 has rotated counterclockwise, after passing further below the lower point and further rotating counterclockwise, the rotational force of the closing spring 116 works to rotate the large gear 107 clockwise, but meshes with the large gear 107. The accumulator shaft 104, which is attached to the small gear 105, is constrained to rotate clockwise by a one-way clutch in the bearing housing 139. Therefore, the clockwise rotation of the large gear 107 is constrained and the insertion is completed. To do. The opening operation after the completion of the insertion is the same as that of the first embodiment described above, and a description thereof will be omitted.

  It should be noted that within the scope of the present invention, the embodiments can be freely combined, or the embodiments can be appropriately modified or omitted.

  The present invention can reduce the electromagnetic force of the electromagnetic switch from the initial position of the operating mechanism of the switch to the vicinity of the contact of the pinion gear with the ring gear, and can improve the electromagnetic force after the contact It is suitable for realizing the operation mechanism.

DESCRIPTION OF SYMBOLS 5 Movable electrode 11 Drive lever 101 Electric motor 102 Output gear 103 Medium gear 105 Small gear 107 Small gear 107 Large gear 107a Notch part 113 Closing spring rod 116 Closing spring 130 Notch part 131 1st synchronous claw 131a 1st tooth 131b 2nd tooth 132 Second synchronous claw 132a Third tooth

Claims (6)

  A driving lever that drives a switch that opens and closes an electric circuit; and an operating unit that operates the driving lever. The operating unit includes a motor that generates rotational energy, and a first that transmits rotational energy of the motor. A transmission mechanism; a second transmission mechanism that is engaged with the first transmission mechanism and partially formed with a missing tooth portion; an energy storage mechanism that is coupled to the second transmission mechanism; A notch portion in which a toothless portion of the transmission mechanism is formed, and is provided with one side pivotably supported by the notch portion, and has at least two first teeth and second teeth, One pitch between the first tooth and the second tooth has a first synchronizing claw configured as a missing tooth, and the cutout portion is arranged in parallel with the first synchronizing claw and swings on one side. A missing tooth position between the first tooth and the second tooth of the first synchronizing claw, which is freely supported. Switch operating mechanism, characterized in that it is composed of a second synchronization pawl having a third tooth.   2. The switch operating mechanism according to claim 1, wherein the notch portion is configured as a concave groove portion at a central portion in a plate thickness direction of a tooth portion of the second transmission mechanism vehicle.   2. The switch operating mechanism according to claim 1, wherein the notch portions are formed on both surfaces of the notch portion of the second transmission mechanism vehicle. 3.   2. The switch operating mechanism according to claim 1, wherein the notch is formed on one side surface of the notch portion of the second transmission mechanism vehicle.   The switch operating mechanism according to claim 1, wherein the electric motor is equipped with clutch means capable of transmitting rotational energy in only one direction.   2. The switch operating mechanism according to claim 1, wherein the first transmission mechanism is equipped with clutch means capable of transmitting rotational energy in only one direction.