JPS60104875A - Electrically operated driving gear - Google Patents

Abstract

PURPOSE:To decrease an error of play in a rotary angle of a clutch mechanism and surely perform the opening and closing by automatic control, by setting the rotary angle of the play of the clutch mechanism to almost an angle multiplying reduction ratio of the final stage reduction gear to 90 deg.. CONSTITUTION:A clutch mechanism, having play of a rotary angle between a reduction gear wheel 23 in the front stage and a reduction pinion 24 in the final stage, provides a disk 26 in the reduction pinion 24 in final stage, and this disk forms in its one side a peripheral groove 27. While the reduction gear wheel 23 in the front stage provides a protrusive part 28 engaging with internal end parts 27a, 27b in both sides of the peripheral groove 27 further freely moving in the peripheral groove 27. The play of the rotary angle in the peripheral groove 27 is set to almost an angle multiplying reduction ratio of the reduction gear in the final stage to 90 deg..

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an electric drive device for driving devices such as ball valves, butterfly valves, etc., which open and close by rotating approximately 90 degrees.

Conventionally, devices of this type are known in which a clutch mechanism is provided on the axis of the output shaft, and this clutch mechanism transmits the drive of the motor to the output shaft and also allows single manual operation. Many methods have been proposed for this clutch mechanism, but all of them have drawbacks such as increasing the size of the clutch mechanism and increasing the overall clutch performance of the PA product. A clutch mechanism was proposed in which a 90-degree groove is formed on one side of the output shaft axis, and a bottle that moves within this groove is fixed to the other shaft, so that the idle rotation angle is approximately 90 degrees. ing.

This clutch mechanism is prone to errors in the free rotation angle between the pin and the 90-degree groove provided on the axis of the output shaft, making it difficult to open and close equipment such as ball valves, and the clutch mechanism is rigid and large. Since the two-clutch mechanism requires a latch mechanism, the structure of the two-clutch mechanism tends to increase in size, and there is a drawback that the entire device cannot be manufactured in a single unit.

For this reason, those skilled in the art will be able to automatically open and close devices such as ball valves while minimizing errors in the idle rotation angle in this type of clutch mechanism.

In addition, there has been a strong demand for the development of an electric drive device that can be operated more easily with two manual operations and that can be provided at a lower cost.

In view of the above-mentioned circumstances, the present inventor has aimed to provide a new and useful electric drive device that solves all of the conventional problems at once.

An embodiment of the present invention will be described below based on the drawings.

Fig. 1 is a longitudinal sectional view showing the electric drive device according to the present invention, Fig. 2 is a plan view showing the clutch mechanism shown in the above, and Fig. 3 is the electric drive device shown in Fig. 1 with the cover removed. FIG.

Reference numeral 1 in the figure is a base of the electric drive device. A support plate 3 is provided on this base 1 via two or more holding rods 2, and the upper part of this support plate 3 is connected to an electric mechanism such as a motor. Part A is designated as part A, and the lower part is designated as gear mechanism space B. In the electrical mechanism part A,
A motor 4 and a limit switch mechanism (described later) are installed, and a gear mechanism space B is provided with a deceleration mechanism and a clutch mechanism, respectively.

5 is a pinion provided on the motor shaft, 6 is an intermediate shaft provided in gear mechanism space B, 7 is an output shaft separate from the intermediate shaft 6,
A control rod 8 is provided at the upper end of this output shaft 7, either integrally or separately. This control rod 8 extends to the space of the electric mechanism part A such as a motor, and the above-mentioned limit/throat switch mechanism is provided near the top of this control rod 8.

This limit switch mechanism has two limits 7 on the support plate 3.
Two rings 11, 12 are fitted onto the control rod 8, and the rings 1L1 are stacked and fixed together.
2 is adjustably fixed to the control rod 8 described above with screws 13 and 14. Furthermore, protrusions 15 and 16 are provided on the outer periphery of the ring 11 at positions facing each other, and protrusions 17 and 18 are provided on the outer periphery of the ring 12 at positions 90 degrees apart from the protrusions 15 and 16 of the ring 11. , as the control rod 8 rotates, the protrusions 15 to 18 have a 9° 10 rim.
It is provided to turn the motor 4 on and off.

Next, we will explain the reduction mechanism and clutch mechanism.
19 is a large gear rotatably provided on the fixed shaft 6; 20 is a small gear that rotates integrally with the large gear 19; the large gear 19 meshes with the pinion 5; the small gear 20 is rotatable on the control rod 8; 22 is a small gear that rotates integrally with the large gear 21.

23 is a front stage reduction large gear rotatably installed on the intermediate shaft 6,
This front-stage reduction gear 23 meshes with the small float 22 described above.

24 is a final stage reduction pinion rotatably or fixedly provided on the intermediate shaft 6. This pinion 24 and the large gear 23 are provided on the same axis, and the pinion 24 is attached to the output shaft. 7
It meshes with the final stage reduction large gear 25 which is fixed integrally or separately to.

A clutch mechanism having an idle rotation angle is provided between the front stage reduction gear 23 and the final stage reduction gear 24, which are provided on the same axis. Alternatively, a disk 26 fixed as a separate body is provided, and one side of this disk 26 has two circumferences! On the other hand, the front stage reduction gear 23 is provided with a protrusion 28 that engages with both inner ends 27a and 27b of the circumference a27 and moves freely within the circumferential groove 27. The circumferential groove 27 may be provided on the first-stage reduction gear 23 and the protrusion 28 may be provided on the disc 26 of the final-stage reduction gear 24. Alternatively, instead of the circumferential groove 27,
Two pins may be provided circumferentially.

The idle rotation angle of the circumferential groove 27 described above must be approximately 90 degrees multiplied by the reduction ratio of the final stage reduction gear. That is, in the two examples, since the reduction ratio of the final stage reduction small gear 24 and the final stage reduction large gear 25 is 1:3, the angle of the circumferential groove 27, which is the idle rotation angle, is 270 degrees.

Further, as another example, if the reduction ratio of the final stage reduction small gear 24 and the final stage reduction large gear 25 is 1:2, 2 circumferences 42
The angle 7 is 180 degrees, and the reduction ratio in the present invention is not limited at all.

In addition, 29 in 5 figures is Space Heak, 30 is Hair Ring, 3
1 is a key, 32 is the lower end of the output shaft 7 formed into a square cross section for inserting a connector (not shown) for connecting to equipment such as a ball valve, and 2 is a spout hook for manual operation ( (not shown) is a ridge on the connector. 33 is a cover.

Next, the operation of the above embodiment will be explained.

First, when the power is turned on and an operation switch (not shown) is turned on, the motor 4 is driven and the large gear 19 and small float 2o are rotated via the pinion 5, and then the large gear 21 on a separate shaft is rotated.
is transmitted to the small float 22, and is then transmitted to the front stage reduction large gear 23 meshing with the small float 22 while being decelerated.

Next, the rotation is transmitted to the front stage reduction gear 23 and the final stage reduction gear 24 by a clutch mechanism, and this rotation is output from the final stage reduction gear 25 which meshes with the final stage reduction gear 24 to the output IF[l! 7.

That is, the protrusion 28 fixed to the first stage reduction gear 23 engages with one inner end 27a of the circumferential groove 27 formed in the disc 26 of the fifth final stage reduction gear 24, and the final stage reduction gear 24 is rotated. Rotate. In this case, the reduction ratio between the final stage reduction gear 24 and the final stage reduction large gear 25 is 1:3, so when the final stage reduction gear 24 rotates approximately 270 degrees, the final stage reduction gear 25 rotates approximately 270 degrees. As the output shaft 7 rotates approximately 9 degrees with the rotation, the ball of a ball valve, for example, rotates from an open (or closed) state to a closed (or open) state, and the ring 11 provided on the control rod 8 rotates. The protrusion 15 contacts the Ramin 1 switch 9, turns off the limit switch 9, and the drive of the motor 4 is stopped. The limit switches 9 and 1o are
It is always on and turns off only when it comes into contact with the protrusions 15 to 18 that are angled at 90 degrees to reliably stop the drive of the motor 4, so it is possible to automatically open and close devices such as ball valves. .

Next, when manual operation is required, such as in the case of a power outage, or when you want to perform manual operation after turning off the power, apply a spanner to the wrench section (not shown) of the connector, and connect the output shaft 7 to the second When rotated clockwise in the figure, the final stage reduction gear 2 meshing with the final stage reduction gear 25
4 and disk 26 rotate in a counterclockwise direction. In this case 1
The circumferential groove 27 of the disk 26 is rotated approximately 270 degrees in the counterclockwise direction in FIG.
7 b engages with the protrusion 28 and stops, and at the same time, the 1st final stage reduction large gear 25 also rotates 90 degrees and stops, so it can be manually operated independently of the motor and gears, such as the balls of the 2-ball valve. 6'("It can actually be opened and closed manually.

Further, the rotation angle of the circumferential groove 27 is not limited to 2270 degrees, but is an angle obtained by multiplying approximately 90 degrees by the reduction ratio of the final stage reduction gear. , 1:2, the rotation angle of 1 circumferential groove 27 is approximately 1
It is 80 degrees.

Although the embodiments have been described above, the present invention has a speed reduction mechanism consisting of a motor and two or more sets of gears, and is used to drive devices such as ball valves, butterfly valves, cocks, etc. that rotate approximately 90 degrees to open and close. In an electric drive device, the final stage reduction gear that meshes with the final stage reduction gear fixed to the output shaft and the front stage reduction gear which is to give the rotation transmitted from the above motor to the final stage reduction gear are coaxially aligned. A clutch mechanism with an idle rotation angle is provided between them.

Since this is an electric drive device in which the idle rotation angle of the clutch mechanism is approximately 90 degrees multiplied by the reduction ratio of the final stage reduction gear, the idle rotation angle is approximately 90 degrees multiplied by the reduction ratio of the final stage reduction gear. Since the reduction ratio of the gear is twice as large, the error of the rotation angle by 2M has an extremely small effect on the rotation angle of the output shaft. Since the rotational force to be generated is small by the reduction ratio of the final stage reduction gear, this clutch mechanism can be light, thin, short, and small, and the material and material of the clutch mechanism can be reduced accordingly.
There are excellent effects such as the cost of processing, assembly, etc. can be reduced, and the space occupied by the two-clutch mechanism is reduced, making the entire device more compact, thereby reducing the cost of the entire device.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and FIG. 1 is a longitudinal sectional view of an electric drive device according to the present invention. FIG. 2 is a plan view showing the final stage reduction gear portion of the same as above, and FIG. 3 is a plan view of the same device with the cover removed. 1...Base, 4...Motor, 7...Output shaft. 8...Control rod, 9.10...Rimisoto switch. 15 to 18...Protrusions. 23... Front stage reduction gear. 24...Final stage reduction gear. 25...Final stage reduction gear. 26... Disk, 27... Circumferential groove. 28... Protrusion. Figure 1 Figure 2 Figure 3

Claims (1)

[Claims] Comprising a motor and a speed reduction mechanism consisting of two or more sets of gears,
In an electric drive device for driving equipment such as ball valves, back-fly valves, cocks, etc. that rotate approximately 90 degrees to open and close, the final stage reduction gear meshes with the final stage reduction gear fixed to the output shaft, and The small gear is arranged on the same axis as the pre-stage reduction large gear which gives the rotation transmitted from the motor mentioned above to the small gear, and there is an idle rotation angle between them. A clutch mechanism is provided, and the idle rotation angle of the clutch mechanism is approximately 90 degrees.
An electric drive device characterized in that the angle is obtained by multiplying the reduction ratio of the final stage reduction gear by the reduction ratio of the final stage reduction gear.