WO2013042687A1 - 開閉装置の操作機構、及び開閉装置 - Google Patents
開閉装置の操作機構、及び開閉装置 Download PDFInfo
- Publication number
- WO2013042687A1 WO2013042687A1 PCT/JP2012/073925 JP2012073925W WO2013042687A1 WO 2013042687 A1 WO2013042687 A1 WO 2013042687A1 JP 2012073925 W JP2012073925 W JP 2012073925W WO 2013042687 A1 WO2013042687 A1 WO 2013042687A1
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- Prior art keywords
- lever
- latch
- roller
- spring
- shaft
- Prior art date
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
- H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
- H01H33/02—Details
- H01H33/46—Interlocking mechanisms
- H01H33/50—Interlocking mechanisms for interlocking two or more parts of the mechanism for operating contacts
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- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
- H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
- H01H33/02—Details
- H01H33/28—Power arrangements internal to the switch for operating the driving mechanism
- H01H33/40—Power arrangements internal to the switch for operating the driving mechanism using spring motor
Definitions
- Embodiments of the present invention relate to a power switchgear installed in a substation or switchgear and an operation mechanism thereof.
- a switchgear with a current interrupting function is called a load switch, disconnector, circuit breaker, etc., depending on its purpose of use and required function. This is common in that the current is cut off and switched on.
- Examples of the operation mechanism for bringing the contact point into and out of contact include a mechanism using a hydraulic operation force that provides a large output and a mechanism using a medium / low output spring operation force.
- An operation mechanism using a hydraulic operation force is generally called a hydraulic operation mechanism, and an operation mechanism using a spring operation force is generally called a spring operation mechanism.
- a spring operation mechanism capable of interrupting an accident current or the like with a small operation force is increasingly used.
- a gas circuit breaker capable of interrupting ultra-high voltage is required to have a high-speed operation performance of two-cycle interruption.
- Two-cycle interruption means that the current is interrupted within the time corresponding to two cycles of alternating current.
- the operation performance is generally about three-cycle disconnection, Realization was not easy.
- Patent Documents 1 to 3 The first conventional example of an opening / closing device employing such a spring operation mechanism is disclosed in Patent Documents 1 to 3.
- the urging force of the blocking spring is held by a latch mechanism including an latch, an open prop (open locking lever), and a catch via an output lever.
- the plunger by causing a current to flow through the solenoid actuator, the plunger operates the catch, the engagement between the catch and the prop is disengaged, the engagement between the output lever and the latch is disengaged, the output lever rotates, The blocking operation is performed by releasing the blocking spring.
- Patent Document 4 is cited as a second conventional example of an opening / closing device employing such a spring operation mechanism.
- a tripping lever and a holding lever are arranged to hold the biasing force of the cutoff spring, and the holding lever is not the force of the cutoff spring during the cutoff operation, but an acceleration spring. It adopts a structure that is operated by the force of and releases the force of the blocking spring.
- the release of the breaking spring is composed of three actions: a catching action by energizing a solenoid, an open action, and a contact separating action including the breaking spring.
- the horizontal axis is the time axis, and the vertical axis is the stroke of each part.
- the lowermost curve shows the waveform of the trip current, on top of which is the catch operating curve, on top of which is the stroke of the open and shut springs.
- the uppermost part shows the energization signal of the contact in the arc extinguishing chamber of the gas circuit breaker.
- T1 is the time from when the current is passed through the solenoid to the start of the catch and the operation of the open prop.
- T2 is the time from the start of the operation of the open prop to the start of the operation of the blocking spring.
- T3 indicates the time from the start of the operation of the cutoff spring until the opening point is reached.
- the spring force of the interrupting spring is determined from the moving part weight of the arc extinguishing chamber, the opening speed, and the driving energy, there is a limit to the time reduction of T3.
- Examples of the method for shortening T2 include a method of reducing the weight of the open prop and increasing the holding force for holding the blocking spring. Thereby, it can be operated at high speed.
- the holding force increases, it is necessary to increase the size of the open prop to improve the strength, and there is a limit to reducing the weight. Therefore, there is a limit to speeding up by increasing the holding force. Further, by increasing the holding force, a large force also acts on the engaging portion between the open prop and the catch, the catch becomes larger, and a solenoid having a large electromagnetic force is required to operate the catch.
- the tripping hook is operated by the electromagnet, the reset lever, the acceleration spring and the holding lever are operated almost simultaneously, and the tripping lever and the cutoff spring are It consists of three operations that operate simultaneously.
- the force required for the operation of the holding lever is reduced by setting the direction of the holding force of the shut-off spring as the rotation center of the holding lever.
- the movement of the holding lever included in the second operation is accelerated by an acceleration spring to shorten the operation time.
- the stability is insufficient in maintaining the spring force of the blocking spring. That is, first, since the direction of the pressure applied to the portion where the tripping lever and the holding lever are engaged is set to the direction of the rotation center of the holding lever, the tripping lever is forced by the forced excitation to the holding lever by external vibration. May rotate in the shut-off operation direction and operate even without a shut-off command. Second, the direction of the applied pressure is not stable because of the deformation of the engagement surface between the roller and the holding lever arranged on the trip lever, and the applied pressure is not stable. In the case of acting in the direction of the shut-off operation, there is a possibility that the trip lever will come off without inputting the shut-off command. Thirdly, in the closing operation, it is sufficiently conceivable that the holding lever operates in the cutoff direction by the impact force when the roller pushes the holding lever back and re-engages, and does the blocking operation without a blocking command.
- the opening time could not be shortened sufficiently, and the stability of holding the spring force of the breaking spring might be insufficient.
- Embodiments of the present invention have been proposed in order to solve the above-described problems, and provide an opening / closing device and an operation mechanism thereof that can reduce the opening time while stably maintaining the spring force of the breaking spring.
- the purpose is to do.
- the operation mechanism of the switchgear is an operation mechanism that switches between interruption and application of current by moving the movable contact to and away from the opposing contact.
- a main lever that is separated from the opposing contact; (3) The main lever and one end are connected, and a sub-lever that can rotate around the other end is provided. (4) The other end of the sub-lever is fixed and a sub-shaft capable of rotating the shaft is provided.
- One end is fixed to the sub-shaft, and a roller is attached to the other end, and has a single latch lever that can rotate about the one end by receiving axial rotation of the sub-shaft.
- It has a single latch portion that is rotatably supported and has an end portion interposed on the movement trajectory of the roller to suppress the rotation of the latch lever when in the input state.
- a weight lever having at one end a weight that can come in contact with and separate from the end of the latch portion.
- a return spring is attached to the other end of the weight lever and presses the weight against the end so as to maintain the end of the latch on the movement locus of the roller.
- the actuator includes an actuator that retracts the latch portion from the movement locus of the roller by rotating the latch portion by pushing away the weight.
- the switchgear according to the embodiment is a switchgear that switches between a cut-off state and an on-state of current, and has the following characteristics. (1) It has a counter contact and a movable contact that can be moved toward and away from each other. (2) It has a cutoff spring that is released when it shifts from the input state to the cutoff state. (3) While being rotatably supported, one end is connected to the blocking spring, the other end is connected to the movable contact, and the movable contact is rotated by receiving the release of the blocking spring. A main lever that is separated from the opposing contact; (4) The main lever and one end are connected, and a sub-lever that can rotate around the other end is provided.
- the other end of the sub-lever is fixed, and a sub-shaft capable of rotating the shaft is provided.
- One end is fixed to the sub-shaft, and a roller is attached to the other end, and has a single latch lever that can rotate around the one end under the axial rotation of the sub-shaft.
- It has a single latch portion that is rotatably supported and has an end portion interposed on the movement locus of the roller to suppress the rotation of the latch lever when in the inserted state.
- a weight lever having at one end a weight that can come in contact with and separate from the end of the latch portion.
- a return spring is attached to the other end of the weight lever and presses the weight against the end so as to maintain the end of the latch on the movement locus of the roller.
- An actuator is provided that retracts the latch unit from the movement locus of the roller by rotating the latch unit by pushing away the weight.
- 2nd Embodiment it is a figure which shows the positional relationship of the latch lever at the time of injection
- FIG. 1 is a cross-sectional view illustrating an example of an opening / closing device according to the present embodiment.
- the switchgear 1 is a gas circuit breaker that cuts off or puts in an electric current by bringing a contact point into and out of the arc extinguishing gas 2.
- a facing contact 4 a and a movable contact 4 b are disposed opposite to each other in a metal or glass sealed container 3.
- the hermetic container 3 is filled with an arc extinguishing gas 2.
- the arc extinguishing gas 2 is a gas excellent in arc extinguishing performance and insulation performance, for example, sulfur hexafluoride gas (SF 6 gas), but air or carbon dioxide having a global warming potential smaller than that of SF 6 gas. , Oxygen, nitrogen, or a mixed gas thereof.
- SF 6 gas sulfur hexafluoride gas
- Oxygen, nitrogen, or a mixed gas thereof is a gas excellent in arc extinguishing performance and insulation performance.
- the opposing contact 4a and the movable contact 4b are conductors that function as electrical contacts.
- the opposing contact 4a and the movable contact 4b can be moved toward and away from each other.
- the movable contact 4 b is connected to the operation mechanism 10 provided in the sealed container 3.
- the operating mechanism 10 pushes the movable contact 4b in the direction of the opposed contact 4a
- the movable contact 4b comes into contact with the opposed contact 4a
- the switchgear 1 moves to a current input state
- the operating mechanism 10 moves in a movable manner.
- the switchgear 1 moves to a current interruption state.
- FIG. 2 is an exploded configuration diagram illustrating an example of the operation mechanism 10.
- the operation rod 5 is a rod-like member fixed to the rear end of the movable contact 4b, and pushes and pulls the movable contact 4b by receiving a driving force.
- the operation rod 55 is arranged coaxially with the movable contact 4b and the opposed contact 4a, and is slidable in this axial direction.
- the main lever 11 is connected to the operation rod 5 via a link 6.
- the rear end of the operation rod 5 and one end of the link 6, and the main lever 11 and the other end of the link 6 are connected so as to be rotatable around a common pin.
- the main lever 11 is formed by extending three arms radially, and has a rotation axis orthogonal to the extending direction of the arms at the radial center of the arm.
- the position of the main lever 11 is fixed by a rotation axis, but the main lever 11 can rotate around the rotation axis.
- the main lever 11 and the link 6 are connected at the tip of the first arm which is one of them.
- the second arm which is another one of the main lever 11, is positioned in the counterclockwise direction from the first arm when the direction in which the first arm is separated from the movable contact 4b is clockwise.
- the second arm is connected to a cutoff drive source.
- the cutoff drive source includes a cutoff spring 12 that generates an operation driving force that cuts off the current, a damper 17 that attenuates vibration of the cutoff spring 12, a piston 17a that regulates the extension range of the cutoff spring 12, and a cutoff
- the link 15 is configured to transmit the urging force of the spring 12 to the main lever 11.
- the blocking spring 12 is a compression coil spring that is released in the extending direction.
- the blocking spring 12 is installed in a housing 14 in which the main lever 11 is accommodated. One end of the blocking spring 12 is fixed to the housing 14 and the other end is floating.
- the damper 17 is filled with fluid, and one end is fixed to the floating end of the blocking spring 12.
- a plate-like spring receiver 16 is provided at the floating end of the blocking spring 12.
- One end of the damper 17 is fixed to the bottom surface of the spring receiver 16 and extends inward along the axis of the blocking spring 12.
- a piston 17 a is provided on the upper surface of the spring receiver 16.
- the piston 17 a is in contact with the end surface of the housing 14 in which the blocking spring 12 is accommodated, thereby restricting the extension range of the blocking spring 12.
- the link 15 extends from the inside to the outside along the axis of the blocking spring 12 and extends to the second arm of the main lever 11.
- the other end of the link 15 and the tip of the second arm are rotatably connected by a common pin 11a.
- the link 16 extends to the first arm side.
- a sub-lever 71 is connected to a third arm, which is another main lever 11, via a link 80.
- the tip of the third arm and one end of the link 80, and one end of the sub lever 71 and the other end of the link 80 are rotatably connected by a common pin.
- the other end of the sub lever 71 is fixed to a sub shaft 70 extending in a direction orthogonal to the extending direction of the lever.
- the sub shaft 70 is supported by a bearing (not shown) so as to be rotatable. However, the arrangement position is fixed.
- the operation mechanism 10 can start the blocking operation by switching the sub shaft 70 from the rotation suppression state to the rotatable state.
- the operation mechanism 10 includes a latch mechanism for switching between a rotation suppression state and a rotatable state of the sub shaft 70.
- FIG. 3 The detailed structure of the latch mechanism is shown in FIG. As shown in FIG. 3, in addition to the sub lever 71, a latch lever 72 is fixed to the sub shaft 70.
- the latch lever 72 extends in a direction orthogonal to the subshaft 70, and a cylindrical roller 72a protruding from the side surface of the lever is rotatably fitted to the tip of the latch lever 72.
- the latch lever 72 When the latch lever 72 is latched, the sub shaft 70 is in a rotation restrained state, and when the latch of the latch lever 72 is released, the sub shaft 70 is in a rotatable state.
- a latch portion 91 that latches the latch lever 72 is present on the roller 72a side of the latch lever 72.
- the latch lever 72 is provided on a locking lever 91e whose arrangement position is fixed so as not to rotate.
- the latch portion 91 has a rotating shaft 100 at one end and is fixed in position by the rotating shaft 100, but is rotatable around the rotating shaft 100.
- the latch portion 91 extends so as to be interposed at one point (hereinafter referred to as a latch point) on the movement locus of the roller 72 a of the latch lever 72.
- the latch portion 91 has a flat portion 102 at the end extending to the latch point.
- the flat surface portion 102 exists in the direction in which the roller 72a of the latch lever 72 moves during the blocking operation, and is substantially orthogonal to the movement locus of the roller 72a. When the latch portion 91 exists at the latch point, the flat surface portion 102 comes into contact with the roller 72a of the latch lever 72 and prevents the latch lever 72 from rotating.
- the plane portion 102 is further formed so that the rotation axis 100 of the latch portion 91 exists on the perpendicular line when a virtual perpendicular perpendicular to the plane is considered. Therefore, the rotational force of the latch lever 72 is converted into a vector from the flat surface portion 102 toward the rotation shaft 100, and hardly acts on the rotation direction of the latch portion 91.
- the latch portion 91 is provided with a roller receiver 103 adjacent to the flat portion 102.
- the roller receiver 103 extends substantially perpendicular to the flat surface portion 102.
- the roller receiver 103 receives the latch lever 72 when the latch lever 72 returns to the latch point during the closing operation of the opening / closing device 1.
- Such a latch portion 91 is swung by the solenoid actuator 21 via a link mechanism.
- This link mechanism includes a tripping link 53 that is connected to the latch portion 91, and a tripping lever 54 that is connected to the tripping link 53 and that is swung by the solenoid actuator 21.
- trip link 53 One end of the trip link 53 is rotatably connected to the latch portion 91 with a pin. At the other end of the tear-off link 53, a long hole 53a having a long side along the extending direction is provided.
- the trip lever 54 has a rotating shaft in the middle, and is provided with a roller pin 54b at one end. The trip lever 54 is connected to the trip link 53 by the roller pin 54 b slidably fitted in the elongated hole 53 a of the trip link 53.
- the plunger 21a of the solenoid actuator 21 is in contact with the trip lever 54.
- the contact position of the plunger 21a is opposite to the roller pin 54b installation side across the rotation shaft. Further, when the plunger 21a is pushed out by the solenoid actuator 21, the plunger 21a is in contact with the tripping lever 54 so as to rotate the tripping lever 54 clockwise.
- the clockwise direction in the trip lever 54 is a direction in which the trip link 53 moves to the side opposite to the latch portion 91.
- the latch mechanism includes a counterweight 93 that assists the rotation suppression by the latch 91.
- the counterweight 93 portion includes a counterweight lever 92, a counterweight 93, and a return spring 94.
- the counterweight lever 92 has a dogleg shape and is provided with a rotating shaft 91a at the bent portion.
- the first arm extending from the rotation shaft 91 a extends to the back surface of the roller receiver 103 provided at the tip of the latch portion 91.
- a cylindrical counterweight 93 is fixed to the tip of the first arm.
- One end of a return spring 94 is fixed to the second arm extending from the rotation shaft 91a. The return spring 94 is biased so that the counterweight 93 contacts the latch portion 91.
- e1 is a restitution coefficient between the latch portion 91 and the roller 72a of the latch lever 72
- e2 is a restitution coefficient between the latch portion 91 and the counterweight lever 92.
- the equivalent mass m1 of the latch part 91 in the equivalent mass model is a value obtained by dividing the moment of inertia around the rotation axis 100 of the latch part 91 by the square of the distance from the rotation axis 100 to the contact point of the counterweight 93.
- the counterweight lever 92 has an equivalent mass m2 including the counterweight lever 92 and the counterweight 93.
- a stopper pin 90 a that can be engaged with the counterweight lever 92 is provided between the counterweight lever 92 and the latch portion 91.
- the stopper pin 90a restricts the rotation range of the counterweight lever 92. Therefore, the swing range of the latch portion 91 that receives the rotational force from the counterweight lever 92 is restricted by the stopper pin 90a.
- the operation mechanism 10 further includes a closing mechanism for bringing the movable contact 4b into contact with the opposing contact 4a.
- a closing spring 13 is provided on the upper surface of the housing 14.
- the closing spring 13 is a compression coil spring.
- the closing spring 13 has one end fixed to the upper surface of the housing 14 and the other end floating.
- the closing spring 13 is biased in the extending direction.
- a plate-like spring receiver 18 is provided at the floating end of the closing spring 13, and a pin 18 a orthogonal to the extending direction of the closing spring 13 is fixed to the spring receiver 18.
- One end of a rod-shaped link 83 is rotatably connected to the pin 18a on the spring receiver 18.
- An input lever 82 is connected to the link 83.
- the closing lever 82 is rotatably connected to the other end of the link 83.
- the closing lever 82 is fixed to the closing shaft 81.
- the input shaft 81 has a fixed arrangement position, but can rotate freely.
- the input shaft 81 is rotatably supported by the rotation axis of the main lever 11 and extends in parallel along the sub shaft 70.
- a cam 84 is fixed to the input shaft 81.
- the cam 84 has a fan shape and has a cam surface in an arc portion. The distance between the cam surface and the shaft fixed to the input shaft 81 continuously increases. Considering one imaginary line extending radially from the axis of the cam 84, the distance from the axis of the cam 84 to the intersection of the imaginary line and the cam surface increases as the closing shaft 81 rotates counterclockwise. I will do it.
- a cam lever 73 is fixed to the sub shaft 70 so as to face the cam 84.
- One end of the cam lever 73 is fixed to the sub shaft 70, and the other end has a roller 73a that slides on the cam surface. Therefore, when the closing shaft rotates counterclockwise, the cam lever 73 receives a rotational force from the cam surface in the clockwise rotation direction.
- the closing lever 82 is held by a latch mechanism.
- the closing lever 82 is provided with a claw 82b.
- the semi-cylindrical member 62 engages with the claw 82b so as to be able to contact and separate.
- the semi-cylindrical member 62 is movable in a direction orthogonal to the flat surface extending in the axial direction. When the heights of the long sides of the claw 82b and the flat surface are the same, the semi-cylindrical member 62 abuts the claw 82b. When the height of the circumferential surface is the same as that of 82b, it is separated from the claw 82b.
- a moving force is applied to the semi-cylindrical member 62 by the solenoid actuator 22.
- the semi-cylindrical member 62 is provided with a protrusion 62a in a direction parallel to the flat surface and orthogonal to the axis.
- the protrusion 62 a is in contact with the plunger 22 a of the solenoid actuator 22 at the bottom located on the circumferential surface side of the semi-cylindrical member 62. Therefore, when the plunger 22a is pushed out, the semi-cylindrical member 62 moves upward, the engagement between the claw 82b and the semi-cylindrical member 62 is released, and the closing lever 82 can be rotated.
- a return spring 62b that is urged in the extension direction is fixed to a surface of the protrusion 62a opposite to the surface on which the plunger 22a abuts.
- the main lever 11 receives a torque for separating the movable contact 4b from the opposing contact 4a by the blocking spring 12.
- the rotation of the latch lever 72 is restricted by the latch portion 91, the sub shaft 70 to which the latch lever 72 is fixed cannot be rotated, and the sub lever 71 fixed to the sub shaft 70 cannot be rotated. It has become. For this reason, the main lever 11 connected to the sub lever 71 cannot be rotated, and the current application state is maintained.
- FIGS. 4 is a block diagram showing the latch mechanism immediately after the start of shut-off
- FIG. 5 is a block diagram showing the latch mechanism in the middle of shut-off
- FIG. 6 is an exploded block diagram showing the entire operation mechanism 10 in the middle of shut-off. is there.
- the solenoid actuator 21 pushes the plunger 21a outward.
- the trip lever 54 that is in contact with the plunger 21a is rotated clockwise.
- the roller pin 54b provided at the tip of the trip lever 54 slides along the long hole 53a of the trip link 53 toward the end, and contacts the inner surface of the long hole 53a.
- the trip link 53 is pulled by the trip lever 54 that has fallen clockwise, and moves to the side opposite to the latch portion 91.
- the latch portion 91 pushes back the counterweight 93 on the back surface and starts to rotate counterclockwise around the rotation axis.
- the plane portion 102 moves so as to push the roller 72a of the latch lever 72, and the engagement relationship is maintained. Further, when the latch portion 91 is rotated, the flat portion 102 is separated from the latch point and separated from the roller 72a. The restraint of the latch lever 72 is released by the separation between the flat portion 102 and the roller 72a.
- the blocking spring 12 is extended, the link 15 lifts the second arm of the main lever 11, and thereby the main lever 11 rotates clockwise.
- the first arm falls down clockwise, and the link 6 and the operating rod 5 connected to the first arm move to the opposite side to the opposed contact 4a.
- the link and the operation rod 5 move, the movable contact 4b is separated from the opposing contact 4a.
- the latch lever 72 rotates, and the shut-off operation ends, the latch portion 91 is rotated to the same position as the loaded state by the counterweight lever 92 by the return spring. Therefore, it is pushed out by the counterweight lever 92, and the position almost the same as the input state, that is, the flat portion 102 returns to the vicinity of the latch point.
- the pull-out link 53 and the pull-out lever 54 are also returned to substantially the same position as in the closed state when the plunger is retracted.
- FIG. 7 is a block diagram showing the closing mechanism immediately after the start of loading
- FIG. 8 is a block diagram showing the latch mechanism and the cam mechanism immediately after the starting of loading
- FIG. 9 is a block diagram showing the latch mechanism in the middle of loading
- FIG. 10 is a block diagram showing a latch mechanism immediately before completion of charging
- FIG. 11 is a schematic diagram showing an equivalent mass model.
- the first arm of the main lever 11 swings in a direction approaching the opposing contact 4a and pushes the link and the operating rod 5 toward the opposing contact 4a.
- the link and the operating rod 5 are pushed out to the opposing contact 4a side, the movable contact 4b fixed to the tip of the operating rod 5 comes into contact with the opposing contact 4a.
- the roller 72a of the latch lever 72 first comes into contact with the arm portion of the latch portion 91 that has been restored by the return spring 94, and pushes the latch portion 91 counterclockwise. Go. Then, when the roller 72a of the latch lever 72 is located at the latch point, as shown in FIG. At this time, since the latch portion 91 is disengaged from the latch lever 72, the latch portion 91 starts the returning operation in the clockwise direction together with the counterweight lever 92.
- the latch portion 91 collides with the roller 72 a of the latch lever 72 at the roller receiver 103 and abuts against the flat portion 102.
- the roller 84a of the latch lever 72 and the roller 72a of the latch lever 72 are disengaged from each other so that the contact between the cam 84 and the cam lever 73 is released. Although it tries to rotate clockwise, it is sufficiently faster that the roller receiver 103 of the latch portion 91 collides with the inertial force.
- FIG. 11 shows an equivalent mass model when the latch portion 91 and the latch lever 72 collide.
- the latch lever 72 can be considered as a fixed wall 303.
- the equivalent mass model 301 of the latch portion 91 having the equivalent mass m1 and the equivalent mass model 302 of the counterweight lever 92 having the equivalent mass m2 move together. Therefore, each moves toward the fixed wall at a speed v1.
- the latch portion 91 and the counterweight lever 92 are set so as to satisfy the following expression (1). m2 ⁇ ⁇ e1 / (1 + e2 + e1 ⁇ e2) ⁇ ⁇ m1 (1)
- the latch mechanism that regulates the current interruption operation has only one engagement relationship, and specifically, the engagement between the latch lever 72 and the latch portion 91. It is only a joint relationship. For this reason, the current interruption operation is performed by sequentially performing a total of two operations, that is, the operation of releasing the engagement between the latch lever 72 and the latch portion 91 and the operation of the interruption spring 12.
- the conventional breaking operation by the breaking spring 12 was composed of a total of three actions of the catch stroke, the open prop stroke, and the stroke of the breaking spring 12, but in this embodiment, it can be completed with two actions.
- the opening time from the start of driving of the actuator is shortened. Specifically, the same effect as that obtained by eliminating the time T2 of the open prop stroke is obtained.
- the spring operating mechanism 10 can be prevented by preventing disengagement due to the collision between the latch portion 91 and the latch lever 72 in the current input operation.
- the operation reliability is improved.
- the engagement surface between the latch portion 91 and the latch lever 72 is a flat surface, and the rotation axis of the latch portion 91 is provided on a perpendicular line perpendicular to the flat surface. It becomes difficult to act in the direction of rotation. Therefore, the size of the latch portion 91 can be reduced, the force when the latch portion 91 is pulled off from the latch lever 72 can be minimized, and the solenoid actuator can also be reduced in size.
- FIG. 12 is a configuration diagram showing a latch mechanism according to the second embodiment.
- a return spring 91 c is fitted to the rotation shaft of the latch portion 91.
- the return spring 91c is a torsion spring.
- the arm of the torsion spring extends in a direction in which the latch portion 91 is separated from the latch lever 72 and is in contact with the stopper pin on the outside. Therefore, the torsion spring always applies an urging force so that the latch portion 91 is interposed on the movement path of the roller of the latch lever 72, and the latch portion 91 is difficult to be separated from the latch lever 72.
- another stopper pin 90a is provided in the vicinity of the other arm of the return spring 91c to restrict the clockwise rotation range of the latch portion 91.
- FIG. 13 is a diagram showing the positional relationship among the latch lever 72, the latch portion 91, and the counterweight lever 92 during the closing operation in the second embodiment.
- the response speed of the latch portion 91 becomes slow due to the presence of the return spring 91c, and the counterweight lever 92 is It rebounds from the reaction of the collision and leaves the latch portion 91.
- the presence of the return spring 91c further improves the effect of preventing the rotation of the latch lever 72 by the latch portion 91, and more effective disengagement of the latch lever 72 from the latch portion 91 in the closing operation. Can be prevented.
- FIG. 14 is a perspective view showing a latch portion 91 and a counterweight lever 92 according to the third embodiment.
- the operating mechanism 10 includes a plurality of counterweight levers 92.
- Each of the counterweight levers 92 has a counterweight 93 attached to one end, and the other end is biased by each return spring 94.
- the plurality of counterweight levers 92 are different in the weight of the counterweight 93 or the elastic coefficient of the return spring, or both. Therefore, when the counterweight lever 92 rebounds from the latch portion 91 in the closing operation, the return timing of each counterweight lever 92 to the latch portion 91 is shifted. Accordingly, the restraining force against the rebound of the latch portion 91 from the latch lever 72 works intermittently, and the disengagement between the latch lever 72 and the latch portion 91 is further effectively prevented.
- FIG. 15 is an enlarged configuration diagram showing the tip of the latch portion 91 according to the fourth embodiment.
- a pin 97 is erected on the side surface of the counterweight 93 at the tip of the counterweight lever 92.
- the pin 97 extends perpendicular to the rotation direction of the latch portion 91.
- a ring 98 is fitted on the pin 97.
- the inner diameter of the ring 98 is larger than the diameter of the pin 97, and the ring 98 is movable in the radial direction of the pin 97.
- the ring 98 has substantially the same outer diameter as the counterweight 93.
- the ring is countered according to the inertial force.
- the weight lever 92 moves in the direction opposite to the rebound direction and collides with the pin. Therefore, the latch portion 91 is prevented from being separated from the latch lever 72 by the inertia force of the ring 98. Therefore, in the fourth embodiment, the disengagement between the latch portion 91 and the latch lever 72 is further prevented.
- FIG. 16 is a configuration diagram of a latch mechanism according to the fifth embodiment.
- a vibration absorbing member 95 is adhered to the roller receiver 103 of the latch portion 91 on the collision surface with the roller 72a.
- the vibration absorbing member 95 is made of a material having high vibration absorption such as a polymer material.
- the lever is fixed to the latch portion 91, and the rotation of the latch portion 91 is locked by pressing the locking member 91e, and the pressing of the locking member 91e is applied by the solenoid actuator 91f or Even in the releasing method, the counterweight lever 92 can be provided on the back surface of the latch portion 91.
- the counterweight 93 may have a circular cross-sectional shape or other shapes, and the same effect can be obtained in both cases.
- the compression coil spring is used for the cutoff spring 12, the closing spring 13, and other return springs.
- other elastic elements such as a spring coil spring, a disc spring, a spiral spring, and a leaf spring are used.
- An air spring or a tension spring can also be used.
- the tip of the latch portion 91 is formed by a convex arc surface, and the center position of the arc surface is substantially coincided with a straight line connecting the center of the roller in the throwing state and the rotation axis center of the latch portion 91, so that the latch portion
- the time for disengaging 91 and the latch lever 72 is shortened, and the opening time can be shortened.
- the stopper pin 90c that engages with the return spring 91c fixed to the latch portion 91 and the stopper pin 90a that restricts the clockwise rotation of the latch portion 91 are provided. You may make it share one.
- the present invention can be applied to a switchgear 1 of a type using a so-called dual motion mechanism that drives the opposing contact 4a to the opposite side of the movable contact 4b to improve the relative opening speed. is there.
Landscapes
- Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)
- Gas-Insulated Switchgears (AREA)
- Feeding, Discharge, Calcimining, Fusing, And Gas-Generation Devices (AREA)
- Trip Switchboards (AREA)
Abstract
Description
(1)前記投入から前記遮断に移行するときに放勢される遮断用バネを有する。
(2)回転可能に軸支されるとともに、一端が前記遮断用バネと連結され、他端が前記可動接点と連結され、前記遮断用バネのバネ力を受けて回転することで前記可動接点を前記対向接点から引き離すメインレバーを有する。
(3)前記メインレバーと一端が連結され、他端を中心に回転可能なサブレバーを有する。
(4)前記サブレバーの前記他端を固定し、軸回転可能なサブシャフトを有する。
(5)一端が前記サブシャフトに固定され、他端にローラが取り付けられ、前記サブシャフトの軸回転を受けて前記一端を中心に回転可能な単数のラッチレバーを有する。
(6)回転可能に軸支され、前記投入の状態にあるときには端部が前記ローラの移動軌跡上に介在して前記ラッチレバーの回転を抑止する単数のラッチ部を有する。
(7)前記ラッチ部の前記端部に接離可能なウェイトを一端に有するウェイトレバーを有する。
(8)前記ウェイトレバーの他端に取り付けられ、前記ローラの移動軌跡上に前記ラッチ部の前記端部を維持させるように、前記ウェイトを前記端部に押しつける復帰バネを有する。
(9)前記ウェイトを押し退けて前記ラッチ部を回転させることで、前記ラッチ部を前記ローラの移動軌跡上から待避させるアクチュエータを有する。
(1)相対的に接離可能な対向接点及び可動接点を有する。
(2)前記投入状態から前記遮断状態に移行するときに放勢される遮断用バネを有する。
(3)回転可能に軸支されるとともに、一端が前記遮断用バネと連結され、他端が前記可動接点と連結され、前記遮断用バネの放勢を受けて回転することで前記可動接点を前記対向接点から引き離すメインレバーを有する。
(4)前記メインレバーと一端が連結され、他端を中心に回転可能なサブレバーを有する。
(5)前記サブレバーの前記他端を固定し、軸回転可能なサブシャフトを有する。
(6)一端が前記サブシャフトに固定され、他端にローラが取り付けられ、前記サブシャフトの軸回転を受けて前記一端を中心に回転可能な単数のラッチレバーを有する。
(7)回転可能に軸支され、前記投入状態にあるときには端部が前記ローラの移動軌跡上に介在して前記ラッチレバーの回転を抑止する単数のラッチ部を有する。
(8)前記ラッチ部の前記端部に接離可能なウェイトを一端に有するウェイトレバーを有する。
(9)前記ウェイトレバーの他端に取り付けられ、前記ローラの移動軌跡上に前記ラッチ部の前記端部を維持させるように、前記ウェイトを前記端部に押しつける復帰バネを有する。
(10)前記ウェイトを押し退けて前記ラッチ部を回転させることで、前記ラッチ部を前記ローラの移動軌跡上から待避させるアクチュエータを有する。
(構成)
図1は、本実施形態に係る開閉装置の一例を示す断面図である。開閉装置1は、消弧性ガス2内で接点を接離させることで、電流を遮断又は投入させるガス遮断器である。この開閉装置1には、金属製又は硝子製の密閉容器3内に対向接触子4aと可動接触子4bとが対向配置されている。密閉容器3内には、消弧性ガス2が充填されている。消弧性ガス2は、消弧性能及び絶縁性能に優れたガスであり、例えば六フッ化硫黄ガス(SF6ガス)であるが、SF6ガスよりも地球温暖化係数の小さい空気、二酸化炭素、酸素、窒素、またはそれらの混合ガス等であってもよい。
サブシャフト70は、図示しない軸受けに支持されて軸回転可能となっているが、配置位置は固定されている。
e1は、ラッチ部91とラッチレバー72のローラ72aとの反発係数であり、e2は、ラッチ部91とカウンターウェイトレバー92の反発係数である。それぞれの衝突が完全弾性衝突の場合には、e1=e2=1であるため、以下式(2)が成り立つ。
m2≧1/3×m1・・・(2)
このような操作機構10による開閉装置1の遮断動作について図4乃至6を参照しつつ説明する。図4は、遮断開始直後のラッチ機構を示す構成図であり、図5は、遮断途中のラッチ機構を示す構成図であり、図6は、遮断途中の操作機構10全体を示す分解構成図である。
次に、このような操作機構10による開閉装置1の投入動作について図7乃至11を参照しつつ説明する。図7は、投入開始直後の投入機構を示す構成図であり、図8は、投入開始直後のラッチ機構及びカム機構を示す構成図であり、図9は、投入途中でのラッチ機構を示す構成図であり、図10は、投入完了直前でのラッチ機構を示す構成図であり、図11は、等価質量モデルを示す模式図である。
v2/v1=-e1・・・(3)
m1・v2+m2・v1=m1・v3+m2・v4・・・(4)
(v3-v4)/(v2-v1)=-e2・・・(5)
-e1・v1・m1+(v1+e2・v1+e1・e2・v1)・m2
=v3・m1+v3・m2・・・(6)
m2≧{e1/(1+e2+e1×e2)}×m1・・・(1)
以上のように、本実施形態の開閉装置1によれば、電流遮断動作を規制するラッチ機構は、ただ一つの係合関係を有し、具体的にはラッチレバー72とラッチ部91との係合関係のみである。そのため、ラッチレバー72とラッチ部91との係合を引き外す動作と、遮断用バネ12の動作の計2動作が順次行われることにより、電流遮断動作は行われる。このように、従来の遮断用バネ12による遮断動作は、キャッチストロークとオープロップストロークと遮断用バネ12のストロークの計3動作より成り立っていたものが、本実施形態では2動作で完遂できるため、アクチュエータの駆動開始からの開極時間が短縮化される。具体的には、オープロップストロークの時間T2が排除されたのと同じ効果が得られる。
次に、第2の実施形態に係る開閉装置1の操作機構10について図12及び13を参照して詳細に説明する。尚、第1の実施形態と同一箇所については同一符号を付して詳細な説明を省略する。
次に、第3の実施形態に係る開閉装置1の操作機構10について図14を参照して詳細に説明する。尚、第1の実施形態と同一箇所については同一符号を付して詳細な説明を省略する。
次に、第4の実施形態に係る開閉装置1の操作機構10について図15を参照して詳細に説明する。尚、第1の実施形態と同一箇所については同一符号を付して詳細な説明を省略する。
次に、第5の実施形態に係る開閉装置1の操作機構10について図16を参照して詳細に説明する。尚、第1の実施形態と同一箇所については同一符号を付して詳細な説明を省略する。
本明細書においては、本発明に係る複数の実施形態を説明したが、これらの実施形態は例として提示したものであって、発明の範囲を限定することを意図していない。具体的には、第1乃至第5の実施形態を全て又はいずれかを組み合わせたものも包含される。以上のような実施形態は、その他の様々な形態で実施されることが可能であり、発明の範囲を逸脱しない範囲で、種々の省略や置き換え、変更を行うことができる。これらの実施形態やその変形は、発明の範囲や要旨に含まれると同様に、特許請求の範囲に記載された発明とその均等の範囲に含まれるものである。
また、第2の実施形態では、ラッチ部91に固定された復帰バネ91cと係合するストッパーピン90cと、ラッチ部91の時計回りの回転を規制するストッパーピン90aとをそれぞれ設けているが、一つに兼用させるようにしてもよい。
2 消弧性ガス
3 密閉容器
4a 対向接触子
4b 可動接触子
5 操作ロッド
6 リンク
10 操作機構
11 メインレバー
11a ピン
12 遮断用バネ
13 投入用バネ
14 ハウジング
14a ハウジング上面
15 リンク
16 バネ受け
17 ダンパー
17a ピストン
18 バネ受け
18a ピン
21 ソレノイドアクチュエータ
21a プランジャ
22 ソレノイドアクチュエータ
22b プランジャ
53 引き外しリンク
53a 長穴
54 引き外しレバー
54b ローラピン
62 半円柱部材
62a 突起物
62b 復帰バネ
70 サブシャフト
71 サブレバー
71a ピン
72 ラッチレバー
72a ローラ
73 カムレバー
73a ローラ
80 リンク
82 投入レバー
82a ピン
82b ツメ
83 リンク
84 カム
90 係止レバー
90a ストッパーピン
90b ピン
90c ストッパーピン
91 ラッチ部
91a 回転軸
91b ピン
91c 復帰バネ
91d レバー
91e 係止レバー
91f ソレノイドアクチュエータ
92 カウンターウェイトレバー
93 カウンターウェイト
94 復帰バネ
95 振動吸収部材
97 ピン
98 リング
100 回転軸
101 中心軸
102 平面部
103 ローラ受け
301 ラッチ部の等価質量モデル
302 カウンターウェイトレバーの等価質量モデル
303 ラッチレバー
Claims (16)
- 対向接点に対して可動接点を接離させることで、電流の遮断と投入とを切り替える開閉装置の操作機構であって、
前記投入から前記遮断に移行するときに放勢される遮断用バネと、
回転可能に軸支されるとともに、一端が前記遮断用バネと連結され、他端が前記可動接点と連結され、前記遮断用バネのバネ力を受けて回転することで前記可動接点を前記対向接点から引き離すメインレバーと、
前記メインレバーと一端が連結され、他端を中心に回転可能なサブレバーと、
前記サブレバーの前記他端を固定し、軸回転可能なサブシャフトと、
一端が前記サブシャフトに固定され、他端にローラが取り付けられ、前記サブシャフトの軸回転に受けて前記一端を中心に回転可能な単数のラッチレバーと、
回転可能に軸支され、前記投入の状態にあるときには端部が前記ローラの移動軌跡上に介在して前記ラッチレバーの回転を抑止する単数のラッチ部と、
前記ラッチ部の前記端部に接離可能なウェイトを一端に有するウェイトレバーと、
前記ウェイトレバーの他端に取り付けられ、前記ローラの移動軌跡上に前記ラッチ部の前記端部を維持させるように、前記ウェイトを前記端部に押しつける復帰バネと、
前記ウェイトを押し退けて前記ラッチ部を回転させることで、前記ラッチ部を前記ローラの移動軌跡上から待避させるアクチュエータと、
を備えること、
を特徴とする操作機構。 - 前記ラッチ部は、
前記ローラの移動軌跡上に介在する端部に設けられ、前記ローラと当接する平面と、
前記平面と直交する仮想線上に設けられた回転軸と、
を有し、
前記投入の状態では、前記ローラの移動力を前記平面によって前記回転軸に向かう力に変換することで、前記ラッチレバーの回転を更に抑止すること、
を特徴とする請求項1記載の操作機構。 - 前記ラッチ部と連結し、前記アクチュエータの駆動力を受けて前記ラッチ部を前記ローラの移動軌跡から引き外すように移動可能な引き外しリンク機構と、
前記ラッチ部の端部を前記ローラの移動軌跡上へ付勢する復帰バネと、
を更に備え、
前記アクチュエータは、前記復帰バネに抗して前記リンク機構を移動させること、
を特徴とする請求項1又は2記載の操作機構。 - 前記引き外しリンク機構は、
前記ラッチ部に配置されたピンと、
一端が前記ピンに軸支され、他端に長穴を有するリンクと、
前記長穴内を摺動可能なピンが一端に設けられたレバーと、
を有し、
前記アクチュエータは、前記レバーの他端と当接するプランジャを有するソレノイドアクチュエータであり、
前記プランジャで前記レバーの他端を押し出すと、前記レバーの先端が引き倒され、前記リンクが前記レバーの先端に引きずられ、前記ラッチ部が前記ウェイトを押し退けて回転して前記ローラの移動軌跡から待避すること、
を特徴とする請求項3記載の操作機構。 - 前記ラッチ部の等価質量m1と前記ウェイトレバーの等価質量m2は、
前記ラッチレバーと前記ラッチ部の反発係数をe1、前記ラッチ部と前記ウェイトレバーの反発係数をe2とすると、
m2≧{e1/(1+e2+e1×e2)}×m1であること、
を特徴とする請求項1乃至4の何れかに記載の操作機構。 - 前記ウェイトを有する前記ウェイトレバーと前記ウェイトの前記復帰バネは、それぞれ複数設けられていること、
を特徴とする請求項1乃至5の何れかに記載の操作機構。 - 前記複数のウェイトは、重量が異なること、
を特徴とする請求項6記載の操作機構。 - 前記ウェイトの前記復帰バネは、弾性係数が異なること、
を特徴とする請求項6又は7に記載の操作機構。 - 前記ラッチ部の端部を前記ローラの移動軌跡上に復帰させる復帰バネを更に備えること、
を特徴とする請求項1乃至8の何れかに記載の操作機構。 - 前記ウェイトに配設されるピン体と、
前記ピン体の外径よりも大きい内径と、前記ウェイトの外径と同程度の外径を有し、前記ピン体に遊貫されたリングと、
を有すること、
を特徴とする請求項1乃至9の何れかに記載の操作機構。 - 前記ラッチ部の前記端部に設けられる振動吸収材を更に備えること、
を特徴とする請求項1乃至10の何れかに記載の操作機構。 - 前記サブシャフトに固定されたカムレバーと、
前記サブシャフトと並行に配設される投入シャフトと、
前記投入シャフトに固定され、前記カムレバーとカム面が当接する投入カムと、
一端が前記投入シャフトに固定され、前記投入シャフトを軸回転させる投入レバーと、
前記投入レバーの他端にリンク機構を介して取り付けられ、前記投入の状態に移行するときに前記投入レバーを回転させるように付勢する投入用バネと、
を備えること、
を特徴とする請求項1乃至11の何れかに記載の操作機構。 - 前記投入レバーの先端に配置されたツメと、
前記ツメと係合する半円柱部と、
前記半円柱部を前記ツメと係合させる方向に付勢するバネと、
前記バネの付勢に抗して、前記半円柱部を前記ツメから離間させる方向に移動させるアクチュエータと、
を備えること、
を特徴とする請求項12記載の操作機構。 - 電流の遮断状態と投入状態とを切り替える開閉装置であって、
相対的に接離可能な対向接点及び可動接点と、
前記投入状態から前記遮断状態に移行するときに放勢される遮断用バネと、
回転可能に軸支されるとともに、一端が前記遮断用バネと連結され、他端が前記可動接点と連結され、前記遮断用バネの放勢を受けて回転することで前記可動接点を前記対向接点から引き離すメインレバーと、
前記メインレバーと一端が連結され、他端を中心に回転可能なサブレバーと、
前記サブレバーの前記他端を固定し、軸回転可能なサブシャフトと、
一端が前記サブシャフトに固定され、他端にローラが取り付けられ、前記サブシャフトの軸回転を受けて前記一端を中心に回転可能な単数のラッチレバーと、
回転可能に軸支され、前記投入状態にあるときには端部が前記ローラの移動軌跡上に介在して前記ラッチレバーの回転を抑止する単数のラッチ部と、
前記ラッチ部の前記端部に接離可能なウェイトを一端に有するウェイトレバーと、
前記ウェイトレバーの他端に取り付けられ、前記ローラの移動軌跡上に前記ラッチ部の前記端部を維持させるように、前記ウェイトを前記端部に押しつける復帰バネと、
前記ウェイトを押し退けて前記ラッチ部を回転させることで、前記ラッチ部を前記ローラの移動軌跡上から待避させるアクチュエータと、
を備えること、
を特徴とする開閉装置。 - 前記ラッチ部は、
前記ローラの移動軌跡上に介在する端部に設けられ、前記ローラと当接する平面と、
前記平面と直交する仮想線上に設けられた回転軸と、
を有し、
前記投入状態では、前記ローラの移動力を前記平面によって前記回転軸に向かう力に変換することで、前記ラッチレバーの回転を更に抑止すること、
を特徴とする請求項14記載の開閉装置。 - 前記ラッチ部の等価質量m1と前記ウェイトレバーの等価質量m2は、
前記ラッチレバーと前記ラッチ部の反発係数をe1、前記ラッチ部と前記ウェイトレバーの反発係数をe2とすると、
m2≧{e1/(1+e2+e1×e2)}×m1であること、
を特徴とする請求項14又は15記載の開閉装置。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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BR112014006016A BR112014006016A2 (pt) | 2011-09-20 | 2012-09-19 | mecanismo para operar aparelho de distribuição e aparelho de distribuição |
CN201280031199.3A CN103620718A (zh) | 2011-09-20 | 2012-09-19 | 开关装置的操作机构及开关装置 |
US14/345,850 US20140231391A1 (en) | 2011-09-20 | 2012-09-19 | Switchgear operating mechanism and switchgear |
EP12832901.8A EP2760039A1 (en) | 2011-09-20 | 2012-09-19 | Switchgear operating mechanism and switchgear |
IN3040DEN2014 IN2014DN03040A (ja) | 2011-09-20 | 2012-09-19 |
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JP2011204024A JP2013065480A (ja) | 2011-09-20 | 2011-09-20 | 開閉装置の操作機構、及び開閉装置 |
JP2011-204024 | 2011-09-20 |
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WO2013042687A1 true WO2013042687A1 (ja) | 2013-03-28 |
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PCT/JP2012/073925 WO2013042687A1 (ja) | 2011-09-20 | 2012-09-19 | 開閉装置の操作機構、及び開閉装置 |
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US (1) | US20140231391A1 (ja) |
EP (1) | EP2760039A1 (ja) |
JP (1) | JP2013065480A (ja) |
CN (1) | CN103620718A (ja) |
BR (1) | BR112014006016A2 (ja) |
IN (1) | IN2014DN03040A (ja) |
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Cited By (1)
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CN105849844A (zh) * | 2013-12-26 | 2016-08-10 | 三菱电机株式会社 | 旁通开关 |
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JP6781514B2 (ja) | 2016-04-22 | 2020-11-04 | 株式会社日立製作所 | ガス遮断器、及びガス絶縁開閉装置用遮断器 |
CN108190162A (zh) * | 2018-01-29 | 2018-06-22 | 深圳喜倍士咖啡有限公司 | 一种液体抽取装置 |
KR102256452B1 (ko) * | 2020-01-21 | 2021-05-27 | 선도전기주식회사 | 가스 절연 개폐 장치용 레버 구동 구조 |
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- 2011-09-20 JP JP2011204024A patent/JP2013065480A/ja not_active Withdrawn
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2012
- 2012-09-19 EP EP12832901.8A patent/EP2760039A1/en not_active Withdrawn
- 2012-09-19 BR BR112014006016A patent/BR112014006016A2/pt not_active Application Discontinuation
- 2012-09-19 IN IN3040DEN2014 patent/IN2014DN03040A/en unknown
- 2012-09-19 CN CN201280031199.3A patent/CN103620718A/zh active Pending
- 2012-09-19 WO PCT/JP2012/073925 patent/WO2013042687A1/ja active Application Filing
- 2012-09-19 US US14/345,850 patent/US20140231391A1/en not_active Abandoned
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JP3497866B2 (ja) | 1997-08-26 | 2004-02-16 | 株式会社日立製作所 | 遮断器 |
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Also Published As
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IN2014DN03040A (ja) | 2015-05-08 |
EP2760039A1 (en) | 2014-07-30 |
BR112014006016A2 (pt) | 2017-04-04 |
JP2013065480A (ja) | 2013-04-11 |
CN103620718A (zh) | 2014-03-05 |
US20140231391A1 (en) | 2014-08-21 |
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