JPS6116410Y2 - - Google Patents

Description

[Detailed description of the invention] The present invention is an actuator that uses hydraulic pressure or other fluid pressure sources, and is capable of controlling the stroke position of two forward stages and two reverse stages based on a simple structure with a single cylinder. Concerning what has been done.

In conventional hydraulic actuators, etc., in order to obtain stroke position control for two forward stages and two reverse stages, two cylinders are used in combination, or a stopper structure is combined, and in either case, mechanisms and devices are required. This is disadvantageous in that it complicates the overall structure and increases its size.

The present invention eliminates such drawbacks and uses a single cylinder piston and piston rod to provide two forward motions.
The position control of the gear and two reverse gears can be performed reliably and easily, and its features are as follows:
A large-diameter pressure chamber and a small-diameter pressure chamber are provided in the cylinder body in the axial direction through the wall, and the large-diameter pressure chamber and the small-diameter pressure chamber are connected to each other through insertion holes at both ends in the axial direction. A hollow piston having a communicating inner chamber is provided to be slidable in the axial direction, and a piston rod is provided in the inner chamber of the hollow piston in the middle of the piston rod and can be engaged with both ends of the hollow piston 2 in the axial direction. The engagement traveling portion is provided to be slidable in the axial direction, and one end of the piston rod is slidably protruded outward from one end of the cylinder body through one insertion hole of the hollow piston in the axial direction. The other end of the hollow piston is inserted through the other insertion hole 2 of the hollow piston, and is slidably penetrated through the cutting wall in the axial direction to protrude into the small diameter pressure chamber. and a supply/discharge port is provided at the end of the small-diameter pressure chamber on the side opposite to the farm wall so as to communicate with each pressure chamber.

The present invention will be described in detail below based on the illustrated embodiment. In FIG. Supply and discharge ports 7 and 8 are provided at the front and rear of the pressure chamber 4, and a supply and discharge port 9 is provided at the rear of the pressure chamber 5. A piston 2 is housed inside the front pressure chamber 4 so as to be able to move forward and backward, and the piston 2 is a hollow piston as shown in the figure.The hollow part is an inner chamber 2a, and both front and rear ends of the inner chamber 2a will be described later. Piston rod 3 insertion hole 2
b, 2b. The piston rod 3 is inserted through the pressure chamber 4 at the front of the rear pressure chamber 5, the inner chamber 2a of the piston 2, and the insertion hole 1a formed at one end of the cylinder body 1 so as to be able to move forward and backward. In the middle of the piston 3, there is provided an engagement traveling part 3a which is slidably housed in the inner chamber 2a of the piston 2 and which is engaged with both the front and rear ends of the inner chamber 2a. In order to control the supply and discharge of fluid pressure, such as hydraulic pressure, to the pressure chambers 4 and 5, a hydraulic circuit 10 is provided as shown in the figure. Solenoid on-off valve 11,
12, an electromagnetic opening/closing valve 13 for controlling switching to the supply/discharge port 9 of the pressure chamber 5 is interposed, and 14 is an engagement traveling portion 3 of the piston 2 and the piston rod 3.
A sealing material provided on each outer peripheral surface of a, 15
is the insertion hole 1 of the piston rod 3 of the cylinder main body 1
a and the sealing material provided in the insertion hole 6a of the piston rod 3 in the farm wall 6, and in the piston 2 piston rod 3, the pressure receiving surface _A1 of the piston 2 and the pressure receiving surface _A3 of the piston rod 3 are shown.
and the pressure receiving surface A ₂ of the engagement traveling portion 3a,
The relationships are set as A ₁ >A ₃ >A ₂ > and A ₁ −A ₂ >A ₃ .

FIG. 2 shows an example of the use of the actuator of the present invention (using hydraulic pressure) with the structure shown in the embodiment of FIG. 22 is reciprocated between the first punch 25 and the second punch 26, and the billet 23 in the bolster 22 is processed and formed as required by both punches 25 and 26. The knockout member is shown.

Before explaining the operation of the actuator of the present invention shown in Figures 1 and 2, the contents of conventional actuators for the same purpose will be briefly described. Figures 3, 4 and 5 show some representative examples, each of which uses a plurality of cylinders 16, 17. That is, the two cylinders 16, 17 each have pistons 18, 19 connected to rods 18a, 18b, and
In the actuator shown in FIG. 3, the two cylinders 16 and 17 are arranged in series, and the movement of the piston 19 on the cylinder 17 side causes the movement of the piston 18 on the cylinder 16 side by the rod 19a.
8, the advancement of the rod 18a 2
In the actuator of FIG. 4, the cylinder 16 is connected to the rod 19a of the piston 19 on the cylinder 17 side, so that the movement of the piston 18 in the position shown in the figure in the cylinder 16 causes the rod 18a to move, and the movement of the cylinder 16 via the rod 19a caused by the movement of the cylinder 19 on the cylinder 17 side also causes the rod 18a to move forward and backward in two steps. In the actuator of FIG. 5, the cylinders 16 and 17 are arranged in parallel separately, and a stopper 2 is provided on part of the rod 18a of the piston 18 on the cylinder 16 side.
0, and rod 1 in cylinder 17 is provided.
By making the rod 18a correspond to the piston 19 of the cylinder 17, the movement of the rod 18a of the piston 18 on the cylinder 16 side is caused by the accompanying movement of the stopper 20 of the rod 19a of the piston 19 of the cylinder 17.
The piston 18 and rod 18a are moved again by the actuator 6, so that the rod 18a moves forward and backward in two stages. In each figure, δ ₁ indicates the first stage stroke, δ ₂ indicates the second stage stroke, and δ ₃ indicates the full stroke. As is clear from the figures, these conventional actuators require both cylinders 16 and 17, which increases the space occupied and places restrictions when they are incorporated into the target facility or device, and also leads to a complication of the structure and operation, including the fluid pressure piping, and an increase in cost.

On the other hand, the actuator of the present invention has the first and second actuators.
In the figure, the effects of the two forward speeds and the two reverse speeds are obtained as follows. That is, FIG. 1 shows the state of the piston rod 3 at its most advanced position, and FIG. 2 shows the starting position of the piston rod 3. From this state, the piston rod 3 moves forward to the first stage ( _stroke ), in order to obtain the piston rod 3 by setting SOLF in the electromagnetic on-off valve 13 in the hydraulic circuit 10 to the ON position and sending pressure oil into the pressure chamber 5 through the valve 13 in FIG. moves until its engagement traveling part 3a is locked with the front end of the inner chamber 2a of the hollow piston 2, and the amount of forward force at this time is equal to the pressure receiving surface described earlier, assuming that the oil pressure is PKg/ ^cm2 .
Under the setting relationship of A ₁ , A ₂ , A _{3 ,} (A ₃ − _{A 2} )×
It is P. At this time, the engaging section 3 of the inner chamber 2a
The oil that has been on the front side of point a is discharged to the outside from the insertion hole 2b and the supply/discharge port 7 via the relief valve 30. Also, in this case, the power of A ₃ ×P is also possible by turning on SOLF.D. In the example of use shown in FIG. 2, this first stage advance (stroke δ ₁ ) causes the piston rod 3 to move from the bolster 2 at the position shown in the figure.
2 is moved directly below the first punch 25, and the required press forming is performed using the same punch 25.

Next, in order to provide the second stage advance (stroke δ ₂ ) to the piston rod 3, the circuit 1 in FIG.
0, the SOLF of the electromagnetic on-off valve 11 is set to the ON position, the pressure oil in the pressure chamber 4 is discharged from the port 7, and the SOLF of the electromagnetic on-off valve 13 is set to the ON position again to supply pressure oil into the pressure chamber 5. According to
The piston rod 3 accompanies the piston 2 through the engagement movement between the engagement movement portion 3a and the inner chamber 5a, and performs the second stage of advancement. The forward force at this time is
A ₃ ×P. In the usage example in Figure 2, this second
The bolster 2 accommodates the billet 23 which has been subjected to the primary processing by the first punch 25 by advancing in stages.
2 is sent directly under the next second punch 26, and the punch 26 performs the required secondary processing. FIG. 1 shows the second stage forward position (most forward position), and from this state the piston rod 3 moves to the second stage by the first stage retreat and the second stage retreat.
Returning to the position shown in the figure, for the first stage of retraction (stroke δ ₂ ), the SOLF of the electromagnetic on-off valve 11 at turn 10 in FIG. Pressure oil is supplied into the pressure chamber 4, and at the same time the electromagnetic on-off valve 12 is
By turning SOLF to the ON position and discharging the pressure oil in the _pressure chamber 4 on the rear end side of the piston 2 from the port 8, the first stroke of _{the stroke δ 2 is} A stage retreat is obtained, and the piston 2 is moved into the inner chamber 2.
The piston rod 3 is moved back along with it via the a-engaging moving portion 3a, and the piston 2 is located at the rear end of the pressure chamber 4 and stops there. The oil in the pressure chamber 5 is discharged from the supply/discharge port 9 via the relief valve 31 . Second
In the illustrated example, the bolster 22 containing the billet 23 that has been processed and formed by the second stage punch 26 is moved back to the first stage punch 25 position. Next, the second stage retreat (stroke δ
₁ ), set SOLB.SOLC of the electromagnetic on-off valves 11 and 12 to the on position in Fig. 1,
In addition to supplying and discharging pressurized oil into the pressure chamber 4, the SOLF in the electromagnetic on-off valve 13 is set to the ON position to drain the pressure oil in the pressure chamber 5, so that the engagement traveling portion 3a in the inner chamber 2a of the piston 2 is Through the pressurization of the pressure oil supplied to the pressure chamber 4, the piston rod 3 moves until its engagement traveling portion 3a is locked to the rear end of the inner chamber 2a, thereby increasing the stroke δ ₁
The second stage of retraction is obtained by the amount of retraction force A ₁ ×P, and in the example of use in FIG.
The piston rod 3 returns to the position shown, and the billet 23 that has been processed and formed is taken out from the bolster 22 by the knockout member 24.

The use shown in FIG. 2 is, of course, only one example, and is suitable as a fluid pressure actuator in various facilities, machines, and devices by controlling the stroke position of the piston rod 3 in two stages each in front and rear, for a total of four stages. It can be used for

According to the actuator of the present invention, a large-diameter pressure chamber 4 and a small-diameter pressure chamber 5 are provided in the axial direction within the cylinder body 1 via the partition wall 6, and the large-diameter pressure chamber 4 is provided with a A hollow piston 2 having an inner chamber 2a communicating with a large-diameter pressure chamber 4 through insertion holes 2b, 2b at both ends is provided to be slidable in the axial direction, and a piston rod is inserted into the inner chamber 2a of the hollow piston 2. 3 is provided in the middle of the hollow piston 2 and is capable of engaging with each end of the hollow piston 2 in the axial direction. The other end of the piston rod 3 is slidably protruded in the axial direction, and the other end of the piston rod 3 is slidably penetrated in the axial direction through the partition wall 6 through the other insertion hole 2b of the hollow piston 2, and inserted into the small diameter pressure chamber 5. The cylinder body 1 is provided with a pressure chamber 4, which communicates with both axial ends of the large-diameter pressure chamber 4 and the end of the small-diameter pressure chamber 5 opposite to the partition wall 6, respectively. Since the supply/discharge ports 7, 8, and 9 are respectively provided in the piston, the cylinder body 1, the hollow piston 2, and the piston rod 3 with the engaging traveling portion 3a are sufficient as the constituent members, and the required structure is therefore extremely simple. The actuator can be made more compact. As a result, the space it occupies is small, and it can be easily incorporated into the target equipment or equipment, making it advantageous in terms of cost. Along with this, the fluid pressure circuit system and switching valves have also been simplified.
It is easy to operate, there is no wasted movement of the piston rod 3 during forward and backward movement in two forward stages, and two reverse stages, and it can be used particularly effectively in a case where the total stroke _δ3 is relatively small. It has great advantages as an actuator.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional front view of an embodiment of the actuator of the present invention with the piston rod at its most forward position, Fig. 2 is an explanatory view of an example of the use of the actuator, and Fig.
FIG. 5 is an explanatory diagram of examples of conventional actuators of the same type. 1... Cylinder body, 2... Piston, 2a...
...Piston inner chamber, 3...Piston rod, 3a...
...Engaging section, 4...Pressure chamber, 5...Pressure chamber, 6
...Cut wall, 7, 8, 9... Supply/discharge port, 10...
Hydraulic circuit, 11, 12, 13...electromagnetic on-off valve.

Claims (1)

[Scope of utility model registration request] A large-diameter pressure chamber 4 and a small-diameter pressure chamber 5 are provided in the cylinder body 1 in the axial direction with a partition wall 6 interposed therebetween.
A hollow piston 2 having an inner chamber 2a communicating with a large-diameter pressure chamber 4 through a hole b is provided to be slidable in the axial direction, and a piston rod 3 is provided midway within the inner chamber 2a of the hollow piston 2. And hollow piston 2
Engagement traveling parts 3a which can be engaged with each other in the axial direction are provided so as to be slidable in the axial direction, and one end of the piston rod 3 is inserted into one insertion hole 2 of the hollow piston 2.
The piston rod 3 is slidably protruded outward from one end of the cylinder body 1 in the axial direction through the hollow piston 2, and the other end of the piston rod 3 is inserted through the other insertion hole 2b of the hollow piston 2 into the wall 6 in the axial direction. The cylinder body 1 is provided with two axially opposite ends of the large-diameter pressure chamber 4 and a small-diameter pressure chamber 5 which are slidably penetrated and protruded into the small-diameter pressure chamber 5 .
Each pressure chamber 4, 5 is located at the end opposite to the farm wall 6.
A fluid pressure actuator characterized in that supply/discharge ports 7, 8, and 9 are respectively provided so as to communicate with the fluid pressure actuator.