JPS60195818A - Spring actuator for switch - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] The present invention relates to an improvement in a spring operating device for a switch.

Figure 1 shows an exploded view of an example of a conventional spring operating device.
Shown in closed circuit position. In this position, the fixed contact 2 and the movable contact 6 of the switch are in contact, and the energization path is connected to the terminal 4,
The fixed contact 2, the movable contact 3, the sliding contact 5, and the terminal 6 are closed by paths. The movable contactor 6 is an insulating rod 7f
It is connected to the output lever 9 of the operating device via the link device 8, and is stably maintained in the closed circuit position by abutting against the circuit closing side stopper 10.

An engaging portion 16 provided with a pawl 14 is fixed to the output lever shaft 12. The left side contact surface 14-1 of the pawl 14 is opposed to the output side contact surface 15 of the driver 15 that approaches and separates. -1, the closed circuit position is maintained. The drive element 15 has a key hole 16 at its rotation center, and the output end 17-1 of the drive shaft 17, which is integrally fixed to the spring lever F-18 and serves as the axis of rotation, is inserted into this key hole 16. Because it is inset,
The spring lever and the driver are integrated, and in the closing position, the spring lever 18 is located at the position shown in the bin 18-Oit A, and the compression spring 19 is driven (Ill' spring receiver 20 is pivotally connected to this). The force of the spring 190 is transmitted via the spring lever 18 to the output lever 9 via the drive shaft 17, the contact surface 15-1 of the driver 15, the contact surface 14-1 of the pawl 14, and the output lever shaft 12, and this The rat is brought into pressure contact with the stopper 10 and kept at that level at all times while the switch 1 is closed.

To open the disconnector 1, the drive motor 21 rotates the worm 22, which is integral with the worm wheel 26, so that the worm wheel 26 rotates in the direction of arrow C. Then, the pawl 26-1 protruding from the end face of the worm wheel 26 rotates in the direction of arrow O and comes into contact with the pawl 15-6 of the driver 15, and when the rotation continues in the same direction, the driver 15 has its contact surface 15-1 separated from the contact surface 14-1 of the claw 14 of the engaging portion 16, and the output end 17-1 fitted into the key hole 16 of the driver 15 connects the drive shaft 17.
The spring lever 1 is integrated with the worm wheel and the UM mover.
8 in a counterclockwise direction from position A to position B.

At this time, the spring 19 connects to the pivot pin 19-2 on the fixed support side,
When the turning ship advances to the position where the pin 18-1 of the spring lever 18 and the drive shaft 17 are aligned in a straight line,
Energy is stored while being compressed.

As soon as the spring 19 passes through the dead center, the spring 19 is released, and the spring lever 18 is pushed further counterclockwise by the spring force, causing the drive shaft 17 to rotate the driver 15. As the contact surface 15-2 of the driver moves, the contact surface 15-2 of the driver touches the claw 1 of the engaging portion 16.
4 and rotates counterclockwise together. Therefore, the output lever shaft 12 and the output lever 9 fixed thereto rotate counterclockwise, and the movable contact 6 is pulled up and separated from the fixed contact 2 via the link device if8 and the insulating rod 7. and continue the operation 0
Ru.

When the movable contactor 6 reaches the open position, the output lever 9 comes into contact with the open-circuit side stopper 11 and stops rotating.
, spring lever 18, drive shaft 17, driver 1
5 and its contact surface 15-2, the contact surface 14-2 of the pawl 14, and the output lever shaft 12, thereby maintaining the output lever 9 in pressure contact with the open-side stopper 11.

Such a conventional example has the following disadvantages.

1) The center axis of the spring 19 is in the closed position and the open position, and the cell is connected to the OE line in FIG. 1 and 0-FIJj! I come to. oV
This is the fixed side fulcrum of the i spring. In other words, since the angle of θ1 is oscillated, a triangle '(f-section) with the oscillation angle θl between the two sides whose side length is between the fulcrum O and the drive shaft center P is used for this purpose. A space having the width of the outer diameter is necessary for rocking, and it is impossible to share this space with other members or elements, which greatly hinders miniaturization of the entire operating device.

2) The fulcrum 0 needs to have a structure that firmly supports the reaction force of the spring 19 without bending, and for this purpose, the spring reaction force F when the circuit is closed in the direction of 0-E is used as a reinforcing structure for the framework of the operating device.
Support for 1, maximum spring reaction force F in the direction of 0-P
It is necessary to ensure rigidity in six directions, including support for 2 and support for the spring reaction force F' when the circuit is opened in the 0-F direction, and for this reason, the framework must be arranged in such a way as to combine reinforcing materials in different directions. It is uneconomical.

The present invention aims to eliminate the above-mentioned disadvantages and provide additional advantages to provide a compact, robust, high-power actuator.

Hereinafter, the present invention will be explained with reference to the drawings. FIG. 2 is a diagram showing essential parts of one embodiment of the present invention. In the figure, spring 19
By attaching a guide roller 61 to the spring bearing 20 on the movable side of the 70-roller 61 and incorporating it into the linear guide 60, the spring 19 expands and contracts on the linear axis.
6 are all pivoted, and the other end is pivoted at the pin 18-1 of the spring lever 18. That is, the spring force is transmitted via the spring link 66, and the only part that swings due to the rotation of the spring lever 18 is the spring link 66. By employing the spring link 66 in this manner, the following effects can be obtained, and in addition to solving the above-mentioned disadvantages, additional advantages can be obtained.

1) Since the spring itself does not swing, a large triangular swing space is not required, and only a small bar-shaped space created by a short pie link is required. The spring link occupies a much smaller cross-sectional area than a spring, and the above-mentioned space can be narrower, so it greatly contributes to improving the overall space factor of the m-production N9.

2) Since the spring does not swing significantly, the direction of the reaction force on the fixed side is constant, and it is only necessary to ensure the rigidity of the frame in that direction, and unnecessary reinforcing materials can be omitted, so the overall structure Dimensions can be made smaller and more economical.

6) If the angle of the spring lever 18 is MeθO at the starting point where the spring lever 18 passes the dead center and the driver starts transmitting its motion, then the deviation f&or° as the main part of the starting torque that the spring force gives to the center of the drive shaft at that time is In the following example, L! It is. (See Fig. 6 (A1)) On the other hand, in the case of the present invention in which the spring lever 18 is set sufficiently short, the deflection becomes L2 as shown in Fig. 6 (A1), and a large starting torque is obtained for the same spring force. Therefore, the effect is large, and since it is possible to drive moving parts with heavy loads, particularly favorable characteristics can be obtained as a high-output actuator.

FIG. 4 shows another embodiment. In the same figure, the linear guide 60 in FIG. 2 is replaced with a guide link 64 pivoted by a fixed pin 65, and the spring 19 is made to move as close to a straight line as possible using a part of the arc of the tip drawn by the swinging of the guide link 64. 18. This shows that it can be replaced with a more economical link device than the DiiMI Guide, which takes into consideration the following.

FIG. 5 shows a further embodiment in which the guide link 34 in FIG. It is pivoted to the pin 68 of the controller and can be arranged almost parallel to the spring lever 18 and the spring link 66, so that the overall longitudinal dimension of the operating device can be reduced. It can be greatly reduced and has a compact structure. The guide lever 36 is a crank with an angle Hv like a Bergfunk type, and the spring 19'& spring lever 1
Of course, it can be made at any angle with respect to 8.

FIG. 6 shows another embodiment in which the spring 19 in FIG. 5 is replaced by a tension spring 41. In the case of a relatively small output type, the buckling required in the case of a compression spring can be prevented. No consideration is required and it is more economical. Of course, this can be similarly applied to the case of a linear guide as shown in FIG.

The present invention is not limited to the above-mentioned method of transmitting driving force using claws, but also transmits driving force by a lobe 18A-3 directly attached to the spring lever 18A coming into contact with the contact surface 15A-2 of the driver 15A, as shown in FIG. May be used to communicate.

That is, the drive motor 71 rotates the hoisting lever 74 via the worm 72 and the worm wheel 76, and the bottle 7 passes through the hoisting lever 74.
Press 5 to compress and store the spring 19. Bottle 75 is spring 1
9, the spring 19 is released and the lobe 18A-3 contacts the contact surface 15A-1 or 15A of the driver 15A.
-2 comes into contact. The output lever shaft 12A is mounted on a keyhole 16 of the driver 15Δ, and when the driver 15 operates, the switch 1 is opened and closed via the entire output lever 9.

As described in detail above, the present invention has the full effect of providing a compact, robust, and large-output operating device.

[Brief explanation of the drawing]

Fig. 1 is an exploded perspective view of the urging device, Fig. 2 is a 1i11 side view showing the main parts of an embodiment of the invention, and Fig. 6 is a diagram showing the locus of the spring. The device shown in FIG. 1 and FIG. 6(b) show the device of the present invention.
The drawings are side views showing essential parts of different embodiments of the present invention, and FIG. 7 is an exploded perspective view showing an embodiment of the present invention. The same symbols in 1 indicate the same or corresponding parts. 1: Switch 18: Spring lever 19: Spring 60 Guide patent applicant Nissin Electric Co., Ltd. Representative Ue 1) Ku - Large Z Figure O 3 I, A) (υ) Large 4 Figure A 5 Eye direction A Flash 33 / 8F

Claims (2)

[Claims] (1) A guide or lever is provided to restrict the movable end of the spring to follow a straight or nearly straight trajectory, and a link is provided to the end directly or via the lever to apply the spring force to the other end. It is pivotally connected to a spring lever that transmits the link, and the link swings in different directions when the switch is in the closed position and the open position, so that the swing does not swing or swings only slightly when the spring expands and contracts. A spring operating device for a switch. (2) A link that restricts the movable end of the spring to pass along a W-line or nearly straight trajectory, and a link that restricts one end of the link that transmits the spring force of the spring to travel through the entire straight or nearly straight trajectory. 2. The spring operating device for a switch according to claim 1, wherein the link is supported by a fixing pin at the same point, and both links are fixed in a constant dimensional relationship so that they move as one.