JPS6333562B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a high-speed hydraulic operating device used, for example, in power switches and disconnectors.

Figure 1 is a piping diagram showing a normal high-speed hydraulic operating device used in power shields and disconnectors, where 1 is the contact part of the power shield and 2 is the point of contact of the power shield and disconnector. 1 is an operating rod for operating, 3 is a piston connected to this operating rod 2, 4 is an operating hydraulic cylinder housing this piston 3, 5 is an accumulator for storing high pressure oil, 6 is an oil filter, a safety valve, Oil pump section equipped with a check valve, etc., 7 is a closing electromagnetic coil, 8 is a closing valve, 9 is a tripping electromagnetic coil, 10 is a tripping valve, 11 is an auxiliary oil supply valve, 11a is an auxiliary oil supply and auxiliary oil supply valve 12 is the main input valve,
12a is the operation valve of the main input valve, 13 is the main oil drain valve, 1
4 is an oil tank provided adjacent to the main oil drain valve 13;
15 is a high pressure oil pipe, and 16 is a low pressure oil pipe.

Next, the operation will be explained.

After increasing the oil pressure, a closing signal is sent with the contact part 1 of the breaker in the tripped state, and when the closing electromagnetic coil 7 is energized, the auxiliary closing valve 8 is opened and the high pressure oil flows through the tripping valve 10. The oil is sent through the oil, and the operation valve 11
A is moved to open the auxiliary oil supply valve 11, and high-pressure oil is sent to the upper part of the main oil drain valve 13, and the operation valve 12a of the main input valve 12 provided inside the main oil drain valve 13 is moved. By moving and opening the main input valve 12, high pressure oil is supplied from the accumulator 5 to the lower part of the operating hydraulic cylinder 4, and the piston 3 is moved upward to open the operating rod 2 connected to the piston 3. Turn on contact part 1 of the breaker by operating .

Next, in the case of tripping, as shown in Fig. 1, a tripping signal is sent when the comb or disconnector is in the closed state, and when the tripping electromagnetic coil 9 is energized, the auxiliary oil drain valve 10 is opened. This opens the operation valve 11a, and at the same time closes the auxiliary oil supply valve 11, and the high-pressure oil that was being sent to the upper part of the main oil drain valve 13 through this auxiliary oil drain valve 10 and piping is drained, and this causes the main input valve 12 is closed, the main oil drain valve 13 is opened by the upper high pressure oil in the cylinder 4, and the high pressure oil is discharged into the oil tank 14. At the same time, high pressure oil is released into the upper chamber 21 of the cylinder. The breaker 1 is supplied with oil from the pump generator 5, moves the piston 3 downward, and operates the operating rod 2 connected to the piston 3.
It is operated by tripping.

However, in recent years, such hydraulic operating devices have been used for high-voltage, large-capacity gas cylinders and disconnectors because of the quick response of the oil, the ability to easily increase pressure, and the ability to reduce the size of the mechanism. It is used as a high-speed operating device. However, since high-pressure oil is used and operation is performed at high speed, the shock generated when operating the piston inside the cylinder is also large and may damage the equipment. For this reason, a shock absorber is usually provided to cushion the shock. This shock absorber is installed, for example, in the middle or at the end of the operating rod that protrudes outside the cylinder, but this makes the entire operating device large and complicated, and also increases the economic cost, so it is generally installed inside the cylinder. Many are equipped with a shock absorber.

That is, FIGS. 2 to 4 show operating hydraulic cylinders in conventional hydraulic operating devices.
4 is the piston and cylinder shown in FIG.
Numeral 3a is a protrusion whose area for receiving hydraulic pressure is changed so that the piston 3 can move from side to side in the figure, and it goes without saying that the portion 3a is further connected to the operating rod 2. Reference numeral 17 denotes a cover, which has a hole 17a that fits into the protrusion 3b of the piston 3, and an inlet/outlet 1 for high-pressure oil.
7b. Reference numeral 21 denotes high-pressure oil that is constantly supplied from the accumulator 5 as shown in FIG. 1, and presses the piston 3 to the right in FIG. 2. Reference numeral 22 denotes high-pressure oil that is fed from the accumulator 5 via the main input valve 12 and drained from the oil drain valve 13, as shown in FIG. When oil is supplied, the piston 3 is pushed to the left in FIG. Reference numeral 23 designates a buffer chamber that is formed on the right side of the piston 3 and changes with the movement of the piston when the protrusion 3b of the piston 3 is fitted into the fitting hole 17a of the cover.

Next, the operation will be explained.

Figure 2 shows that in Figure 1, the main oil drain valve 13 is opened by the tripping signal of the breaker, the high pressure oil 22 in the cylinder 4 is drained, and the high pressure that constantly pressurizes the upper part of the piston 3 is shown. The piston is operated at a high speed by the oil 21, and the contact portion 1 of the shear breaker is tripped, and furthermore, the piston operated at a high speed is about to produce a buffering effect by the buffer device provided at its end. It is a diagram. That is, when the protrusion 3b provided on the right side of the piston 3 fits into the hole 17a provided in the cover 17, a buffer chamber 23 is created between the piston and the cover. However, the piston uses high pressure oil 2
Since the oil is moving rightward at high speed with the hydraulic pressure of 1, the buffer chamber 23 becomes smaller.
This acts as a repulsive force that pushes the piston back toward the left, thereby dampening the movement of the piston. However, since there is a small gap between the protrusion 3b and the hole 17a of the cover for fitting, the high pressure oil in the buffer chamber 23 is gradually discharged, and the piston moves to the final position shown in FIG. do.

Next, FIG. 4 shows that in FIG. 1, the main input valve 12 is opened by the input signal from the breaker, and the high-pressure oil stored in the accumulator 5 is sent to the cylinder 4 from the inlet/outlet 17b of the cover. Hydraulic pressure is applied to the end surface of the protruding portion 3b of the piston to move the piston to the left. Note that when the protrusion 3b protrudes from the fitting hole 17a of the cover, the hydraulic area is equal to that of the buffer chamber 2.
Since the end face of the piston forming part 3 also receives pressure, the operating force of the piston increases rapidly and moves leftward at high speed.

In the conventional device configured as described above, the protrusion 3b at the end of the piston is used to form a shock absorber, so the piston protrusion 3b,
Unless the fitting with the fitting hole 17a is released, the only pressure receiving part for high pressure oil is the end face of the piston protrusion, and as the buffer chamber 23 expands, high pressure oil will also not enter the protrusion and the fitting hole. Since the movement is performed gradually from the gap, it is impossible to perform the initial movement of the piston at high speed. To deal with this, the pressure receiving area of the protrusion 3b may be increased, but this has the drawback that the effect of the shock absorbing device cannot be expected.

In order to solve this drawback, structures shown in FIGS. 5 to 7 have been proposed as a conventional means. This is an addition to the above-mentioned shock absorbing device with a structure for improving the initial operation of the piston. Note that the same reference numerals in the drawings as in the conventional device (FIG. 2) refer to the same constituent members, and the explanation thereof will be omitted. 17c supplies high pressure oil 2 to the buffer chamber 23.
This is a bypass circuit for sending oil 2, and a part thereof includes a ball 24 that is constantly pressed by a spring 25, and has the function of a check valve. Note that the end of the spring 25 is held in contact with the plug 26.

Next, the operation is basically the same as that shown in FIGS. 2 to 4 described above, but the operation according to the improved structure described above is as follows.

That is, FIG. 5 is a diagram in which the piston 3 is operated in conjunction with the tripping of the cutter and the shock absorber at the right end begins to operate, but in this case, the high pressure oil in the buffer chamber 23 flows through the bypass circuit 17c. It tries to be discharged, but the ball 24 acts as a check valve and is not discharged. Therefore, it goes without saying that the shock absorber operates in the same manner as in the prior art.

Note that since FIG. 6 corresponds to FIG. 3 described above, the explanation thereof will be omitted.

Next, FIG. 7 is a diagram showing an initial state in which the operating piston is operated to the left in conjunction with the closing of the breaker.
That is, the pressure of the high-pressure oil 22 fed through the main injection valve 12 is applied to the ball 24 of the bypass circuit 17c.
The ball 24 is pushed down as shown in the figure, and high pressure oil is sent to the bypass circuit 17c as shown by the arrow and enters the buffer chamber 23.
The end face of the piston 3 that makes up the piston 3 also receives pressure, which helps the piston move to the left, and the pressure receiving area for moving the piston from the beginning of the piston's movement is larger than before. , will be moved at high speed.

However, in the conventional hydraulic operating device shown in FIGS. 5 to 7 described above, if a certain degree of initial high-speed operation of the piston is required, only one bypass circuit is required; If it is used for high voltage and large capacity,
Not only does such a structure have to be provided at multiple locations on the circumference of the cover 17, resulting in an extremely complicated structure, but since balls, springs, etc. are used, holes must be provided that communicate with the outside of the cover. Moreover, although this hole is fitted with a plug or the like, it can also become a place where oil can leak, resulting in a lack of reliability.

This invention attempts to eliminate the above-mentioned drawbacks of the prior art. A floating ring provided for buffering is provided with one or several communicating holes in the axial direction, and the communicating holes are closed during the buffering action. It comes into contact with the end face of the cover and acts as a check valve, and when the piston is operated in the anti-buffer direction, the high-pressure oil sent moves the ring and is also sent to this hole, causing pressure to be received by the end face of the piston. The present invention aims to provide a hydraulic operating device capable of moving a piston at high speed.

That is, although FIGS. 8 to 10 all show one embodiment of the present invention, the same reference numerals as those in the conventional system (FIG. 5) described above refer to the same constituent members, and the explanation thereof will be omitted. 27 is a cover according to the present invention, a ring 28 is housed in this cover 27, and the length of the fitting surface with this ring is the same as that of the ring 28.
It is made longer than the width of 8 by the dimension "A" in the figure, so that the ring can move in the axial direction. The high pressure oil inlet/outlet 27a of this cover 27 is connected to the ring 2.
The inner diameter of the ring 28 is larger than the inner diameter 28a of the ring 28 so that the end face of the ring 8 serves as a pressure receiving surface and receives high pressure oil. The ring 28 also has a hole 28a into which the protrusion 3b of the piston 3 fits,
One or more communication holes 28b are provided, one communicating with the inside of the buffer chamber 23 and the other corresponding to the inner end surface of the cover 27, for communicating high-pressure oil. Moreover, the inner diameter of the cylinder 4 is the same as that of the ring 2.
8, and the end of this cylinder 4 serves as a stopper that restricts movement of the ring in the direction of the piston.

Next, the operation will be explained.

Similar to FIG. 5, FIG. 8 shows that the main oil drain valve 13 opens in response to the trip signal shown in FIG. 21, the piston is moved at high speed and the contact part 1 of the breaker is tripped, and the piston, which has been moved at high speed, is about to create a buffering effect by the shock absorber provided at its end. be. That is, when the protrusion 3b provided on the right side of the piston 3 fits into the hole 28a provided in the ring 28, a buffer chamber 23 is created between the piston and the ring. Therefore, the piston 3 is moved at high speed by the high pressure oil 2.
1, the buffer chamber 23 becomes smaller, the oil in this buffer chamber 23 is compressed, and as the pressure increases, the ring 28, which freely moves in the axial direction, is covered. The ring 28 is brought into close contact with the end face of the cover 27, and the communication hole 28 of this ring 28 is brought into close contact with the end face of the cover 27.
The drained oil from b is stopped and functions as a check valve. Therefore, the oil in the buffer chamber 28 compressed in this manner buffers the movement of the piston against the repulsive force that tends to push the piston 3 back to the left, as shown in FIG. In addition, after the buffer is used, as time passes, oil is gradually drained from the small gap between the mating surface and the contact surface, and the piston moves to its final position as shown in Figure 9. be.

Next, FIG. 10 shows that, similarly to FIG. When higher pressure oil is sent from the oil inlet/outlet 27a of the cover 27, the end face of the protrusion 3b of the piston 3 and the partial end face 27b of the ring 28
Piston 3 and ring 28 due to the hydraulic pressure applied to
Both move to the left, so the high-pressure oil is also sent to the buffer chamber 23 through the communication hole 28b of the ring 28, and pressurizes the entire right end surface of the piston, causing the piston to move leftward at high speed. It means moving.

As described above, in the hydraulic operating device of the present invention, the protrusion 3 of the piston 3 is located between the piston 3 in the cylinder 4 and the cover 27 having the high pressure oil inlet/outlet 27a.
A movable ring 28 forming a buffer chamber 23 is housed in the ring 28, and a communication hole 28b is formed in the ring 28 to guide high pressure oil flowing from the high pressure oil inlet/outlet 27a to the buffer chamber 23. ,
This is designed to increase the speed of the piston at the initial stage of movement, and its structure, processing, and assembly work are extremely simple and inexpensive compared to conventional pistons. It has the excellent effect of providing a highly reliable hydraulic operating device that can sufficiently cope with high-speed operation accompanying the increase in high voltage and capacity. In the above-mentioned embodiment, a communication hole 28b was provided in the ring 28, but it goes without saying that the same effect can be achieved even if a vertical groove is provided in place of the communication hole. do not have.

[Brief explanation of the drawing]

Fig. 1 is a piping diagram showing a normal high-speed hydraulic operating device, Fig. 2 is a sectional view showing a conventional operating hydraulic cylinder, Figs. 3 and 4 are explanatory diagrams of its operation, and Fig. 5 is Further, FIGS. 6 and 7 are cross-sectional views showing other conventional operating hydraulic cylinders, and FIG. 7 are explanatory views of their operation. FIG. 8 is a cross-sectional view of a hydraulic cylinder showing an embodiment of the present invention. FIG. and FIG. 10 are explanatory diagrams of the operation. In the drawing, 3 is a piston, 3b is a protrusion, 4 is an operating hydraulic cylinder, 23 is a buffer chamber, 27 is a cover, 27a is a high pressure oil inlet/outlet, 28 is a ring, 28
b is a communicating hole. Note that the same reference numerals in the figures indicate the same or corresponding parts.

Claims (1)

[Claims] 1. An operating hydraulic cylinder whose one end opening is closed by a cover having a high-pressure oil inlet/outlet, which is housed in the operating hydraulic cylinder so as to be able to reciprocate, and has a distal end on the side of the cover facing the high-pressure oil inlet/outlet. an operating piston having a small-diameter protrusion;
The operation piston is housed in a buffer chamber formed between the operating piston and the cover so as to be movable in the axial direction, and is connected to a ring hole that is closed by the fitting of the protrusion when the piston moves in the buffer direction. A ring having a communication hole that is closed by the above, and a pressure-receiving surface that receives the high-pressure oil and applies a moving force toward the piston when the high-pressure oil is supplied from the high-pressure oil inlet/outlet; A hydraulic operating device comprising a stopper that restricts movement beyond the buffer chamber toward the piston.