JPWO2008117437A1 - Storage mechanism for switchgear - Google Patents

Abstract

An accumulator mechanism for a switchgear capable of disconnecting and reengaging power transmission with an unnecessary structure of high precision parts is obtained. When the closing spring 22 is stored, the main gear 5 is rotated by the storing motor 3 via the output gear 16 and the intermediate gear 33. When the storing of the closing spring 22 is completed, the toothless portion 34 of the gear A is connected to the gear A. The meshing with the intermediate gear 33 is released, and the meshing between the intermediate gear 33 and the external teeth 35 of the gear B is continued. When the switchgear is turned on, the gear A is rotated by the release of the closing spring 22. Then, the claw 41 of the gear A and the inner teeth 36 of the gear B are engaged so that the phases of the teeth of the gear A and the outer teeth 35 of the gear B are the same, and the intermediate gear 33 is connected to the outer teeth 35 of the gear A and the gear B. Was made to mesh.

Description

  The present invention relates to a mechanism for storing a closing spring that causes a power switching device such as a circuit breaker or a switch to perform a closing operation.

  When a switching device such as a circuit breaker is turned on, a spring is used to make the moving operation, more specifically, the moving contact approaching the fixed contact constituting the contact (main contact) as steep as possible. There is something that uses the accumulated power of. In this kind of switchgear, before performing the closing operation, the closing spring is stored by compression or tension and restrained in this state, and upon closing, the closing spring is released by releasing the restraint. The contact charging lever linked to the contact is operated by the stored force of the spring to move the movable contact at high speed.

  As the energy storage mechanism for storing the closing spring, various configurations have been proposed together with the energy release mechanism. FIG. 7 is a side cross-sectional view showing a main part of the energy storage mechanism disclosed in Patent Document 1. As shown in FIG.

  The energy storage mechanism includes a main shaft 1, an energy storage shaft 2, and an energy storage motor 3 that are supported in parallel and substantially parallel to a common support frame 4. The main shaft 1 is fitted and held with a large gear 5 at a projecting end to one side of the support frame 4 and a closing cam 6 in the middle thereof, and these rotate around the axis as the main shaft 1 rotates. .

  A crankpin 7 projects from the outer surface of the large gear 5 at a position deviated by an appropriate length from the axis of the main shaft 1. One end of a presser rod 8 is connected to the crank pin 7, and the other end of the presser rod 8 is inserted and supported by a spring plate 9. The spring plate 9 is, for example, a fixed plate integrally protruding on the outside of the support frame 4, and a closing spring between the spring plate 9 and the presser plate 10 fixed to the middle part of the presser rod 8. 22 is interposed.

  The closing spring 22 is compressed between the spring plate 9 and the presser plate 10 when the projecting position of the crankpin 7 approaches the spring plate 9 by the rotation of the large gear 5 as shown in the figure. And accumulated. This stored state is maintained by restraining the rotational position of the large gear 5 by restraining means (not shown). When this restraint is released, the spring force of the closing spring 22 is applied to the presser plate 10, the presser rod 8 and the crank. It acts on the large gear 5 via the pin 7, and the main shaft 1 rotates at a high speed together with the large gear 5.

  On the inner side of the support frame 4, a contact input lever 11 is pivotally supported via a support shaft 12 projecting from one surface thereof. The other surface of the contact closing lever 11 supports a roller 13 that is in rolling contact with the outer cam surface of the closing cam 6, and the contact closing lever 11 rotates by the operation of the roller 13 that follows the cam surface. Accordingly, it swings around the support shaft 12 and is linked to a contact (not shown) so as to perform a closing operation by this swing.

  The accumulator shaft 2 includes a transmission gear 14 that is integrally fixed to a projecting end of the support frame 4 toward one side, and a drive that is loosely fitted between the transmission gear 14 and the outer surface of the support frame 4. A gear 15 is provided. The transmission gear 14 is meshed with a large gear 5 fixed to the shaft end of the main shaft 1, and the drive gear 15 is meshed with an output gear 16 fitted to the output end of the accumulator motor 3.

  The accumulator motor 3 is a geared motor configured to decelerate and take out the rotation of the motor main body 3a by a reduction gear 3b connected to the output side thereof. The output gear 16 is fitted to the output shaft 17 of the reduction gear 3b, and a one-way clutch 18a that allows only one-way rotation is interposed between the output shaft 17 and the housing of the reduction gear 3b. ing.

  The drive gear 15 meshed with the output gear 16 is stored so as to be slidable in the relative rotation and axial direction via a one-way clutch 18b and a pawl clutch 19 which are fitted and held in a hole penetrating the shaft. It is externally fitted to the urging shaft 2 and is urged toward the transmission gear 14 by a push spring 20 interposed between the outer surface of the support frame 4. The one-way clutch 18b attached to the drive gear 15 allows the rotation in the same direction as the one-way clutch 18a provided in the reduction gear 3b, and the rotation of the drive gear 15 by the transmission from the output gear 16 is an inner claw clutch. 19, while slipping is generated with respect to rotation in the reverse direction from the claw clutch 19 side.

  The drive gear 15 is normally pressed against the transmission gear 14 by the spring force of the pressing spring 20 that is elastically contacted to one side, and rotates integrally with the transmission gear 14 by the engaging action of the pawl clutch 19. In this engaged state, when the main shaft 1 and the large gear 5 are at the rotational positions shown in the figure, and the closing spring 22 is in the stored state, the crank pin 7 is substantially opposed to the other side of the large gear 5 in the radial direction. The driving protrusion 15 is pressed by the protruding pressing protrusion 21, and the driving gear 15 is released by moving away from the transmission gear 14 against the spring force of the pressing spring 20.

  In the conventional energy storage mechanism configured as described above, when the restriction of the large gear 5 is released from the state shown in the figure, the large gear 5 is moved in a predetermined direction (the input spring 22 by releasing the energy storage force of the input spring 22. The rotation is transmitted to the contact closing lever 11 through the closing cam 6, and the contact closing lever 11 is swung at a high speed to insert a contact (not shown). .

  In such a closing operation, the rotation of the large gear 5 is transmitted to the transmission gear 14 meshing therewith, and the accumulator shaft 2 rotates. The rotation direction at this time is the one-way clutch 18b included in the drive gear 15. The drive gear 15 does not rotate, and the rotational force is not transmitted to the output shaft 17 of the accumulator motor 3.

  The rotation of the large gear 5 due to the release of the closing spring 22 continues beyond a predetermined rotational position (top dead center) due to its own inertia, and during this time, the closing spring 22 is stored, so that the large gear 5 And the main shaft 1 tries to reverse after exceeding the top dead center. However, this reverse force is transmitted to the one-way clutch 18b included in the drive gear 15 via the transmission gear 14, and is transmitted to the drive gear 15 when the one-way clutch 18b is engaged, and further applied via the output gear 16. As a result of engagement with the one-way clutch 18a that is transmitted to the output shaft 17 of the motor 2 and interposed in the output shaft 17, the reverse rotation is prevented, and the large gear 5 is constrained to the rotational position beyond the top dead center. The

  When the accumulator motor 3 is rotationally driven after such an input state is obtained, this rotation is transmitted to the drive gear 15 via the output gear 16 fitted to the output shaft 17, and the pawl clutch 19. The large gear 5 which is transmitted to the transmission gear 14 via the gear and meshes with the transmission gear 14 rotates. By this rotation, the presser rod 8 connected to the crankpin 7 is pushed down, and the closing spring 22 is compressed between the presser plate 10 and the spring plate 9 to obtain the stored state shown in the figure, and the next closing operation. Is possible. The rotation of the large gear 5 due to the rotation of the accumulator motor 3 stops when the pressing protrusion 21 presses the drive gear 15 at a predetermined rotation position and the engagement of the pawl clutch 19 is released, and this rotation position. Is maintained by restraining the large gear 5 by the restraining means described above.

Japanese Patent Laid-Open No. 11-40010

  In the conventional energy storage mechanism configured as described above, in order to store the closing spring 22, the output gear 16 is rotated by the energy storage motor 3 that is a drive source or manual rotation, and the rotation is driven by the drive gear 15. , The transmission spring 14 transmitted to the transmission gear 14 and the large gear 5 and connected to the large gear 5 is stored. After the energy accumulation of the closing spring 22 is completed, the drive gear 15 is moved by the pressing protrusion 21 attached to the large gear 5 and the pawl clutch 19 is disconnected to prevent excessive energy accumulation. Further, after the closing operation, the pawl clutch 19 is reconnected by the push spring 20. The one-way clutch prevents the large gear 5 from reversing.

However, in order to satisfy these functions, the pressing protrusion 21 of the large gear 5 and the drive gear 15 are in contact with each other, and dimensional accuracy is required so that the pawl clutch 19 is disconnected. There was a problem that the shape had to be made highly accurate.
The present invention has been made to solve the above-described problems, and an object of the present invention is to provide an accumulator mechanism for a switchgear that can disconnect and reengage power transmission with an unnecessary structure of high-precision parts. To do.

  The accumulator mechanism of the switchgear according to the present invention includes a closing cam that operates to close the contact of the switchgear and a crank portion that is linked to the closing spring, and is rotated by an accumulator motor or a manual force. A main gear that stores the closing spring by the action of the part, rotates in the same direction as the stored state by releasing the closing spring, and causes the opening / closing device to perform a closing operation by the action of the closing cam; A gear A having a toothless part, a gear B having external teeth and internal teeth that have the same diameter and tooth period as those of the gear A, and that are healthy, and are fixed integrally with the gear A. The claw engages with the internal teeth of the gear B only when the rotation direction of the disc rotates in one direction. So that the teeth and the outer teeth of the gear B can be rotated in phase. The main gear formed, the output motor rotated by the accumulator motor or the output shaft of manual force, and the intermediate gear meshing with the output gear and the gear A of the main gear and the external teeth of the gear B A gear, and when storing the closing spring, the main gear is rotated via the output gear and the intermediate gear by the storing motor or manual force, and when the storing of the closing spring is completed, the gear A The meshing between the gear A and the intermediate gear is released at the missing tooth portion, and the meshing between the intermediate gear and the external teeth of the gear B is continued. The gear A rotates due to the release, the claws of the gear A and the internal teeth of the gear B are engaged, and the phases of the teeth of the gear A and the external teeth of the gear B are made the same. And the intermediate gear meshes with the external teeth of the gear B. That.

According to the energy storage mechanism of the switchgear of the present invention, when the closing spring energy storage is completed, the meshing with the intermediate gear is released at the toothless portion of the gear A. Can be separated. Further, when the gear A and the intermediate gear are reengaged in the charging process, the gear A and the gear B are engaged with the claws and the internal teeth, and the teeth of the gear A and the external teeth of the gear B are in phase. Since it is later, re-engagement can be easily achieved with an unnecessary structure of high-precision parts.
Other objects, features, aspects and advantages of the present invention will become more apparent from the following detailed description of the present invention with reference to the drawings.

It is a sectional side view which shows the principal part of the energy storage mechanism of the switchgear by Embodiment 1 of this invention. It is a figure explaining the main structures of the energy storage mechanism of the switchgear in FIG. It is a figure explaining the structure by disassembling the main gear according to the first embodiment. It is a figure explaining the engagement and rotation of the gear C and the gear B by Embodiment 1. FIG. It is a figure explaining operation | movement of the energy storage mechanism of the switchgear by Embodiment 1. FIG. It is a figure explaining operation | movement of the energy storage mechanism of the switchgear by Embodiment 1. FIG. It is a sectional side view which shows the principal part of the accumulating mechanism of the conventional switchgear.

Embodiment 1 FIG.
FIG. 1 is a side sectional view showing a main part of an energy storage mechanism of a switchgear according to Embodiment 1 of the present invention. FIG. 2 is a diagram illustrating the main configuration of the energy storage mechanism of the opening / closing device, and is a diagram illustrating the energy storage completion state of the closing spring. In each figure, the same numerals indicate the same or corresponding parts. This energy storage mechanism includes a main shaft 1, a rotary shaft 25, and an output shaft 17 that are supported in parallel and substantially parallel to each other on a common support frame 4. The main shaft 1 is fitted with a main gear (large gear) 5 at the projecting end to one side of the support frame 4, and a closing cam 6 is fitted and held in the middle thereof. Rotate to.

  On the outer surface of the main gear 5, a crankpin 7 projects from a crank portion that is eccentric from the axis of the main shaft 1 by an appropriate length. One end of a presser rod 8 is connected to the crankpin 7. When the presser rod 8 is pushed down, the closing spring 22 is compressed and stored in the same manner as in FIG. 7. As the main shaft 1 rotates, the crank portion of the main shaft 1 moves up and down, and the closing spring 22 is released and stored.

  When the projecting position of the crankpin 7 comes close to the closing spring 22 due to the rotation of the main gear 5, the closing spring 22 is compressed and stored. This stored state is maintained by restraining the rotational position of the main gear 5 by the restraining means 27 (FIG. 6). When this restraint is released, the spring force of the closing spring 22 is applied to the presser rod 8 and the crank pin. 7 acts on the main gear 5 and the main shaft 1 rotates at a high speed together with the main gear 5.

  A contact closing lever 11 is pivotally supported inside the support frame 4 via a support shaft 12 provided on one surface thereof. One end of the contact closing lever 11 supports a roller 13 that is in rolling contact with the cam surface on the outer periphery of the closing cam 6, and the contact closing lever 11 responds to the rotation of the closing cam 6 by the operation of the roller 13 that follows the cam surface. It swings around the support shaft 12, and is linked to the contact point 28 so as to perform a closing operation by this swing. In FIG. 2, a link mechanism 29 for operating the contact 28 is connected to the contact closing lever 11, 30 is a support shaft, 31 is an open spring, and 32 is a contact pressure spring.

  The output shaft 17 is rotated by the accumulator motor 3 serving as a driving force, the output gear 16 fitted and held on the output shaft 17 is rotated, and the rotation is transmitted to the intermediate gear 33 and the main gear 5. The closing spring 22 connected to is stored. Instead of the accumulator motor 3, the output shaft 17 may be rotated with a manual force using a wrench or the like.

  FIG. 3 is a diagram for explaining the structure by disassembling the main gear 5 according to the first embodiment. The main gear 5 is composed of a gear A, a gear B, and a gear C having the same diameter and the same tooth period, and is disposed coaxially and overlapped with the gear B interposed between the gear A and the gear C. The gear A has a missing tooth portion 34a in which some of the teeth are cut out. The gear B has a ring shape having external teeth 35 and internal teeth 36, and the external teeth 35 are healthy with no missing teeth, and the internal teeth 36 are healthy with all teeth, but the rotational direction of the gear B (gear A The inclination of the inner teeth 36 according to the relative rotation direction) is provided. The gear C has a shape in which a large-diameter gear plate 37 and a small-diameter disk 38 are bonded together. The gear of the large-diameter gear plate 37 has the same missing tooth portion 34b at the same phase as the gear A, and has a small diameter at the center. The disc 38 is fitted into the inner diameter portion of the inner tooth 36 of the gear B to support the gear B.

  The toothless portion 34a of the gear A and the toothless portion 34b of the gear C are arranged in the same phase on the circumference, and the gear A and the gear C are fixed integrally and fitted to the main shaft 1 in a state where the tooth phases are matched. Has been. The gear B is sandwiched between the gear A and the gear C, and is supported by the small-diameter disk 38 of the gear C. When the gear B does not engage with the gear A and the gear C, a floating gear that is rotatable with respect to the gear A and the gear C It has become. In this example, grooves 39a and 39b are formed at both ends of the diameter of the small-diameter disk 38 of the gear C, and the return spring 40 presses (attaches) the grooves 39a and 39b to the outside (anti-center direction). Claws 41a and 41b are provided. Inclinations at the tips of the claws 41a and 41b are provided with respect to the rotational direction of the gear C (relative rotational direction with respect to the gear B).

  The gear A, the gear B, and the gear C of the main gear 5 are thus configured, and the engagement and rotation of the gear B with respect to the gear A and the gear C will be described next. FIG. 4 is a diagram for explaining the engagement and rotation of the gear C and the gear B. The gear C is fixed integrally with the gear A, and the gear A is omitted. In FIG. 4, (a), (b), (c), (d), (e), and (f) have passed in this order. (A) is a case where the gear C is rotated by the initiative, and in a state where the claw 41a of the gear C is pressed by the return spring 40 and engaged with the internal teeth 36 of the gear B, the inclination and the inner The teeth 36 are steep with respect to each other, and this engagement cannot be released. The gear C and the gear B are integrated with each other and the gear B rotates together with the gear C. In the state where the claw 41 of the gear C is engaged with the internal teeth 36 of the gear B (the state shown in FIG. 4A), the teeth of the gear C and the teeth of the gear B are configured to be in phase. .

  FIG. 4B shows a case where the gear C is restrained and the gear B continues to rotate due to inertia of a drive source (described later). In this case, since the gear B rotates mainly, the slack of the claw 41a and the slant of the internal teeth 36 come into contact with each other, and the claw 41a is pushed in the center direction to escape, so that the engagement is released. Therefore, the gear B can rotate with respect to the gear C. The same state is continued from FIGS. 4C and 4D, and the state where the claw 41a is gradually pushed toward the center is shown. .

  FIG. 4 (e) shows a case where the gear B remains and the gear C, which has been released from restraint, starts to rotate again (in the initial stage). As the gear C rotates, the claw 41 b is pressed outward by the return spring 40 and extends into the internal teeth 36. In FIG. 4F, the gear C further rotates, the claw 41b engages with the internal teeth 36, and the gear B starts rotating together with the gear C. In a state where the claw 41b of the gear C is engaged with the internal teeth 36 of the gear B, the inclination of the claw 41b and the inclination of the internal teeth 36 both abruptly abut each other, and this engagement cannot be released. The gear B rotates together with the gear C together with the gear B. Similarly, when the claw 41 of the gear C is engaged with the internal teeth 36 of the gear B (the state shown in FIG. 4F), the teeth of the gear C and the teeth of the gear B are in phase.

In the above description, the gear of the large-diameter gear plate 37 of the gear C of the main gear 5 has the same diameter as the gear A and has the same missing tooth portion 34b at the same phase as the gear A. However, the entire circumference may be a missing tooth portion without teeth. In short, the gear B is sandwiched between the gear A and the gear C and supported by the small-diameter disk 38 of the gear C. When the gear B is not engaged with the gear A and the gear C, the gear B is rotatable with respect to the gear A and the gear C. It only has to be a floating gear. In this case, the intermediate gear 33 can mesh with the gears A and B of the main gear 5, but naturally does not mesh with the gear C.
Further, the gear C of the main gear 5 is provided with the small-diameter disk 38. However, even if the small-diameter disk 38 having the groove 39 and the claw 41 is attached and fixed to the gear A, the same operation can be performed.

  Referring to FIG. 1, an intermediate gear 33 in which a large-diameter gear 42 and a small-diameter gear 43 are integrally formed meshes with the output gear 16, and the main gear 5 has its gear A, gear B, and gear C. After the power storage of the closing spring 22 is completed, the intermediate gear 33 is disconnected from the gear A and the gear C by the toothless portion 34 of the gear A and the gear C. For this reason, after the energy accumulation of the closing spring 22 is completed, the intermediate gear 33 is separated from the gear A and the gear C of the main gear 5 so that the driving force of the energy accumulation motor 3 is not transmitted to the gear A and the gear C of the main gear 5. Separated. This prevents excessive storage.

  The intermediate gear 33 that meshes with the output gear 16 has a one-way clutch (reverse rotation prevention mechanism) 18 that is fitted and held in a hole that passes through the shaft center portion. While the rotation of the intermediate gear 33 by transmission from the output gear 16 is transmitted to the main gear 5, rotation in the reverse direction from the main gear 5 side is prevented. A one-way clutch (reverse rotation prevention mechanism) that allows only one-way rotation is further interposed between the output shaft 17 of the output gear 16 and the housing that supports the output shaft 17, so that the one-way clutch 18 described above. May be allowed to prevent rotation in the reverse direction from the main gear 5 side.

  Next, operation of the energy storage mechanism will be described. FIGS. 5 and 6 are diagrams for explaining the operation of the energy storage mechanism of the switchgear according to Embodiment 1, and FIGS. 6 (a), (b), and (c) following FIGS. 5 (a) and 5 (b). The operation of one rotation of the main gear 5 is shown as a whole. In addition, the solid line arrow in FIG. 5, FIG. 6 shows the rotation direction of a gearwheel. FIG. 5A shows the middle of the spring energy accumulation, and the driving force of the output gear 16 rotates the main gear 5 via the intermediate gear 33. The intermediate gear 33 meshes with the gear A and the gear B of the main gear 5 to rotate the main gear 5, pushes down the crank portion, and stores the closing spring 22.

  FIG. 5B shows a bottom dead center state of the main gear 5, and the intermediate gear 33 meshes with the main gear 5 in front of the toothless portion 34 of the gear A. FIG. 6A shows a state where the energy accumulation is completed. At this time, since the intermediate gear 33 has reached the toothless portion 34 of the gear A of the main gear 5, the meshing between the intermediate gear 33 and the gear A is released, and the driving force of the output gear 16 is transmitted to the gear A. Without inertia, the inertia of the energy storage motor is not transmitted to the gear A. The stored state of the closing spring 22 is maintained by restraining the rotational position of the gear A by the restraining means 27. Regardless of the restrained state of the gear A, the intermediate gear 33 continues to mesh with the gear B, so that the gear B is further rotated by the inertia of the accumulator motor.

When this restriction is released, the spring force of the closing spring 22 acts on the gear A via the presser rod 8 and the crank pin 7, and the main shaft 1 starts to rotate at a high speed together with the gear A of the main gear 5. Then, as the gear A rotates, the claw 41 starts to engage with the inner teeth 36 of the gear B, and when engaged (engaged), the external tooth 35 phase of the gear B and the tooth phase of the gear A are The gears B and A start to rotate together. Since the intermediate gear 33 originally meshed with the external teeth 35 of the gear B, the gear A (gear A beyond the tooth missing portion) and the intermediate gear 33 in phase with the external teeth 35 of the gear B Rotates with smooth re-engagement without hitting. FIG. 6B shows the middle of charging. In FIG. 6B, the white arrow indicates the direction in which the closing spring 22 is released. In this manner, the contact of the switchgear is turned on by the action of the making cam 6 accompanying the rotation of the main shaft 1 of the main gear 5.
At this time, the small-diameter gear 43 of the intermediate gear 33 also rotates. However, since the one-way clutch 18 is provided at the axial center of the intermediate gear 33, the small-diameter gear 43 is idled and the intermediate gear 33 has a large diameter. The gear 42 and the output gear 16 do not rotate.

  The rotation of the main gear 5 due to the release of the closing spring 22 continues beyond a predetermined rotational position (top dead center) due to its own inertia, and during this time, the closing spring 22 is stored, so the main gear 5 and the main shaft 1 tries to reverse after exceeding the top dead center. However, this reverse force is blocked by the one-way clutch 18 provided in the intermediate gear 33. As a result, the main gear 5 is restrained at the rotational position beyond the top dead center. FIG. 6C shows a state where the main gear 5 is prevented from rotating in reverse. In FIG. 6C, the upper white arrow indicates the direction in which the main gear 5 is going to reverse, and the lower white arrow indicates the releasing direction of the closing spring 22.

  When the storage of the closing spring 22 is started again after the closing, the intermediate gear 33 is already engaged with the gear A and the gear B of the main gear 5, so that the driving force of the output gear 16 passes through the intermediate gear 33. It is transmitted to the gear A and the gear B of the main gear 5, and the closing spring 22 is stored.

  In the energy storage mechanism configured as described above, the engagement of the gear A and the intermediate gear 33 is released by the toothless portion 34 of the gear A when the energy storage of the closing spring 22 is completed. In addition, power transmission can be separated with a simple structure that does not require high-precision parts.

  In the opening process of the contact of the switchgear, the claw 41 starts to engage with the internal teeth 36 of the gear B as the gear A rotates, and when engaged, the phase of the external teeth 35 of the gear B and the teeth of the gear A The gear B and the gear A start to rotate together with the phases being matched. Since the intermediate gear 33 originally meshed with the external teeth 35 of the gear B, the gear A (the gear A beyond the tooth missing portion) and the intermediate gear 33 that are in phase with the external teeth 35 of the gear B and the intermediate gear 33 re-smoothly. It can mesh and rotate.

  It should be noted that various modifications or changes of the present invention can be realized by related skilled engineers without departing from the scope and spirit of the present invention, and are not limited to the respective embodiments described in this specification. Should be understood.

Claims (5)

A closing cam connected to the closing spring; and a crank portion connected to the closing spring, which is rotated by an accumulator motor or a manual force, and the closing spring is stored by the action of the crank portion. On the other hand, a main gear that is rotated in the same direction as when accumulating by the release spring of the closing spring and causes the opening / closing device to perform a closing operation by the action of the closing cam, the gear A having a toothless portion, A gear B having external teeth and internal teeth having the same tooth cycle as that of the gear A and having all teeth healthy, and a disk having a pawl fixed integrally with the gear A and biased outward. The claw engages with the internal teeth of the gear B only when the rotation direction of the disk is one-way rotation, and the phases of the teeth of the gear A and the external teeth of the gear B are the same when engaged. The main gear configured to be able to rotate,
An output gear rotated by the accumulator motor or an output shaft of manual force;
An intermediate gear that meshes with the output gear and meshes with the gear A of the main gear and the external teeth of the gear B;
At the time of accumulating the closing spring, the main gear is rotated through the output gear and the intermediate gear by the accumulating motor or manual force,
When the energy storage of the closing spring is completed, the meshing between the gear A and the intermediate gear is released at the toothless portion of the gear A, and the meshing between the intermediate gear and the external gear of the gear B is continued. And
When the switchgear is turned on, the gear A rotates due to the release spring of the closing spring, and the claw of the gear A and the inner teeth of the gear B are engaged, so that the teeth of the gear A and the outer side of the gear B are engaged. An energy storage mechanism for an opening / closing device in which the phases of teeth are the same, and the intermediate gear is engaged with the external teeth of the gear A and the gear B.   The energy storage mechanism of the switchgear according to claim 1, wherein the intermediate gear or the output gear is provided with a reverse rotation prevention mechanism for preventing rotation of the main gear in a direction opposite to the rotation direction.   When the disc fits into the inner diameter part of the inner teeth of the gear B and supports the gear B with the disc, and the pawl does not engage with the inner teeth of the gear B, The energy storage mechanism of the switchgear according to claim 1, wherein the gear B can rotate.   The main gear is provided with the same gear C as that of the gear A with a diameter, a tooth period, and a toothless portion, and the gear B supported by the disk is interposed between the gear A and the gear C. The accumulator of the switchgear according to claim 3, wherein the gear A, the disc, and the gear C are integrally fixed in a state where phases of the toothless portion of the gear A and the toothless portion of the gear C are matched. mechanism.   The disc of the main gear is provided with a guide groove for the claw, and the claw guided by the guide groove is urged outward by a spring. The accumulator mechanism of the switchgear according to item.

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