JPS5939202Y2 - Air-hydraulic conversion intensifier - Google Patents

Description

[Detailed description of the invention] In order to operate driven devices (hereinafter referred to as "driven devices") such as hydraulic clamp devices that operate reliably and are easy to handle with inexpensive air pressure, air pressure is created using a large diameter cylinder and piston. An air-hydraulic conversion pressure intensifier that generates high-pressure hydraulic pressure in a secondary pressure chamber formed by a plunger fixed to the side opposite to the primary pressure chamber side of the piston and a small-diameter cylinder. has been known for a long time, but in these pressure intensifiers,
In order to increase the hydraulic pressure at the end of the operating stroke of the driven device, the diameter of the plunger must be made relatively small, which reduces the amount of oil supplied and limits the number of connected driven devices and the operating stroke. have

In order to eliminate the above-mentioned drawbacks, the present invention prefills the primary pressure chamber with hydraulic oil in an amount greater than the amount required to operate the driven device, and until the driven device reaches the end of its operating stroke. , the hydraulic oil is supplied to the driven device through a passage provided in the piston and plunger of the pressure intensifier, and the passage is closed after the driven device reaches the end of its working stroke, thereby producing a pressure booster similar to that of a conventional pressure intensifier. This is designed to generate high hydraulic pressure in the secondary pressure chamber.

That is, the air-hydraulic conversion pressure intensifier according to the present invention has a piston and a plunger of the pressure intensifier that have a passage leading from the primary pressure chamber to the secondary pressure chamber, and that the pressure is maintained while the hydraulic pressure in the pressure intensifier is lower than the set pressure. It moves in the direction of opening the passage under the force of the setting spring, and when the hydraulic pressure in the pressure intensifier reaches the set pressure or higher, it receives the hydraulic pressure from the primary pressure chamber or secondary pressure chamber. By providing a valve body that moves in the direction of closing the passage against the force of the pressure setting spring, high hydraulic pressure can be obtained by the same action as a conventional air-hydraulic conversion pressure intensifier, and the amount of supplied oil can be reduced. can be easily enlarged as needed.

Next, drawings showing embodiments of the present invention will be described.

The large diameter cylinder 1 and piston 2 form a primary pressure chamber 3.

A plunger 4 is provided integrally with the piston 2 on the side opposite to the primary pressure chamber side of the piston 2, and the plunger 4 is connected to the secondary pressure chamber 6 together with a small diameter cylinder 5 fixed to the large diameter cylinder 1. form.

The primary pressure chamber 3 is provided with an air pressure supply lower, and the secondary pressure chamber 6 is provided with an oil inlet/outlet 8. A cavity 9 surrounded by the piston 2, plunger 4, and cylinder 1 is provided with an opening 10. Open to atmospheric pressure.

A valve body 11 is housed within the piston 2 and is pressed against a surface 13 by a pressure setting spring 12 .

In this state, the primary pressure chamber 3 and the secondary pressure chamber 6 are
4. A pressure setting spring 12 that communicates with the valve hole 15 and the through hole 16 to form a passage leading from the primary pressure chamber to the secondary pressure chamber.
The cavity 17 in which the is housed is opened to atmospheric pressure via the cavity 9 by the through hole 18.

In the embodiment shown in FIG. 1, the hydraulic pressure in the primary pressure chamber 3 is guided through the through hole 19 so as to push the valve body 11 against the pressure setting spring 12.

In the embodiment shown in FIG. 2, the hydraulic pressure in the secondary pressure chamber 6 is guided through the through hole 16 so as to push the valve body 11 against the pressure setting spring 12.

When the driven device connected to the oil inlet/outlet 8 reaches the end of its operating stroke, the hydraulic pressure in both the secondary pressure chamber and the primary pressure chamber increases, so the hydraulic pressure led to the valve body is increased by the pressure in the primary pressure chamber or the secondary pressure chamber. Although it is possible to take the oil from either side, taking it from the secondary pressure chamber has the advantage of reducing the amount of oil leaking from the valve body, and the driven device is subject to temporary resistance during the operating stroke. If the pressure in the secondary pressure chamber exceeds the resistance, the valve body moves in the direction of opening the passage again and transfers the hydraulic fluid in the primary pressure chamber to the secondary pressure chamber. It has the advantage of being able to supply

The piston return spring 20 is provided to return the piston 2 to a predetermined position when the pressure in the primary pressure chamber is released to atmospheric pressure and to prevent the piston 2 from moving due to piping resistance or the like.

When hydraulic oil 21 is sealed in the primary pressure chamber and air pressure is supplied to the air pressure supply lower, the hydraulic oil 21 flows through the through hole 14, valve port 15, and through hole 1.
6 and flows into the secondary pressure chamber.

When the double-acting device connected to the oil inlet/outlet 8 reaches the operating stroke end, the pressure in the pressure intensifier increases, and when this pressure exceeds a preset pressure, the valve body 11 releases the pressure setting spring 12.
The valve body 11 moves against the force and blocks the space between the through holes 14 and 16.

In this state, the air pressure supplied to the primary pressure chamber pushes the piston 2 against the piston return spring 20, and pushes the piston 2 into the secondary pressure chamber 6.
generates a high hydraulic pressure corresponding to the area ratio of the piston and plunger.

When the supply of air pressure to the primary pressure chamber is stopped and the pressure in the primary pressure chamber is released to atmospheric pressure, the hydraulic pressure in the secondary pressure chamber also drops to near atmospheric pressure due to the pressure balance acting on both sides of the piston 2. , the valve body 11 is moved again to the surface 13 by the force of the pressure setting spring 12.
The valve 1'' 15 connects the through holes 14 and 16 with each other.

In this state, the hydraulic oil flowing into the secondary pressure chamber from the driven device that is returned by a return spring or other means passes through the through hole 16, the valve port 15, and the through hole 14, and is stored in the primary pressure chamber again. returns to the state before activation.

In the embodiment shown in FIG. 2, since the moving direction of the valve body 11 is arranged to match the sliding direction of the piston 2, it has the advantage that the device can be made compact and easy to manufacture. .

The protrusion 23 provided on the pressure setting spring receiver 22 is for regulating the amount of movement of the valve body 11, and since the pressure setting spring receiver 22 is screwed onto the piston 2, the pressing force of the pressure setting spring is limited. Can be easily adjusted.

In the embodiment shown in FIG. 2, since the sliding direction of the piston 2 is vertical, there is no possibility that the hydraulic fluid may get mixed into the device, especially in the secondary pressure chamber 6, the through hole 16, the valve hole 15, and the through hole 14. Air can be easily separated.

As is clear from the above explanation, most of the amount of oil supplied to the driven device is stored in the primary pressure chamber, and the volume of the primary pressure chamber can be easily increased. Therefore, according to the present invention, it is possible to obtain an extremely right-acting pneumatic-hydraulic conversion intensifier when a double-acting device with a large operating stroke is operated by pneumatic pressure or when many driven devices are operated by one pressure intensifier.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional view showing one embodiment of the present invention, and FIG. 2 is a vertical cross-sectional view showing another embodiment of the present invention. 1... Large diameter cylinder, 2... Screw I
・N, 4...Plunger, 5...Small diameter cylinder, 3...Curved primary pressure chamber, 6...Secondary pressure chamber, 12...・Pressure setting spring, 11...
Valve body.

Claims (1)

[Claims for Utility Model Registration] 1. A pressure intensifier consisting of a piston that slides in a large diameter primary pressure chamber and a plunger that slides in a small diameter secondary pressure chamber is fixed to one side of the piston that slides in a large diameter primary pressure chamber. 2 from the primary pressure chamber
A passage leading to the secondary pressure chamber and a valve body receiving the force of a pressure setting spring in the direction of opening the passage and receiving the hydraulic pressure of the primary pressure chamber or the secondary pressure chamber in the direction of closing the passage are provided, 1. A pneumatic-hydraulic conversion pressure intensifier characterized by being provided with a spring that returns the piston and plunger to their original positions when the piston and plunger are released. 2. The pneumatic-hydraulic conversion pressure intensifier according to claim 1 of the registered utility model, characterized in that the sliding direction of the piston and the moving direction of the valve body are made to coincide with each other. 3. The pneumatic-hydraulic conversion pressure intensifier according to claim 1 or 2, characterized in that the sliding direction of the piston is vertical.