JPH07332226A - Booster - Google Patents

Abstract

PURPOSE:To provide a booster devised to improve delivery efficiency. CONSTITUTION:A booster comprises a boosting chamber 3 having an inlet 1 and an outlet 2; a suction check valve 4 forward and backward movably inserted in the boosting chamber 3 and opening and closing the inlet 1; a delivery check valve 5 connected to an outlet 2; a plunger chamber 6 inserted in the suction check valve 4 from the opposite side of the inlet 1 and communicated with the inlet side part of the boosting chamber 3; a plunger 8 inserted in and retracted from the plunger chamber 6; and a reciprocating generating engine 10 to drive the plunger 8. A pressure fluid feed source is connected to the inlet 1 and an annular friction body 9 fitted in internally of the tip part of the plunger 7 is forced into contact with the peripheral surface of the plunger chamber 6 at a given contact pressure.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a pressure booster, and more particularly to a pressure booster capable of enhancing pressure boosting efficiency and discharge efficiency.

[0002]

2. Description of the Related Art Generally, in a factory, hydraulic pressure is used, for example, for clamping a formwork, a workpiece, etc. However, it is disadvantageous in terms of equipment cost to provide high-pressure hydraulic piping in the factory. Not only is it disadvantageous in terms of maintenance. In order to eliminate such a problem, in many factories, a high pressure oil is supplied only to a place where a high pressure oil is required by using a so-called pressure booster.

As shown in FIG. 3, for example, a conventional pressure booster has a cylindrical pressure boosting chamber 103 having an inlet 101 for sucking in hydraulic oil and an outlet 102 for discharging pressurized hydraulic oil. A suction check valve 104 for opening and closing 101 is inserted so as to be able to move forward and backward, and the outlet 102 is connected to a discharge check valve 105. The suction check valve 104 has a cylindrical plunger chamber 106 that is recessed from the side opposite to the inlet, and the plunger chamber 106 is always connected to the outlet 102 of the pressure boosting chamber 103 through a communication hole 107. .

In the plunger chamber 106, the plunger 10
8 is inserted so as to be able to move forward and backward, and as shown in FIG. 5, the plunger 108 retracts in the direction of expanding the volume of the plunger chamber 106, so that the internal pressure of the plunger chamber 106 is reduced and the inlet 101 of the inlet 101 is reduced. Hydraulic oil and plunger chamber 106
The suction check valve 104 is separated from the inlet 101 by the pressure difference from the internal pressure of the hydraulic pressure, and hydraulic oil is sucked into the pressure increasing chamber 103 from the inlet 101.

After this, as shown in FIG.
When 8 enters the plunger chamber 106, the plunger chamber 106
When the internal pressure of the chamber is increased, the suction check valve 104 is closed, and the plunger 108 further deeply enters the plunger chamber 106 as shown in FIG. 4, the plunger chamber 106 and the pressure increasing chamber 10 are
The hydraulic oil inside 3 is increased in pressure, and the discharge check valve is discharged from the outlet 102.
Open 105 and discharge to the load circuit.

The means for driving the plunger 108 is not particularly limited, but a reciprocating motion generating engine 110 driven by air taken out from a pressurized air pipe installed in the factory is often used. The reciprocating motion generating engine 110 is a cylindrical cylinder chamber 111 coaxial with the pressure increasing chamber 103 and the plunger chamber 106, and is inserted into the cylinder chamber 111 so as to be able to move forward and backward, and is integrally connected to the plunger 108. piston
112 and.

Further, the reciprocating motion generating engine 110 has a directional control valve 115 for switching and connecting the cylinder chamber 111 to a supply port 113 and an exhaust port 114 for pressurized air, and a directional control valve 115 for driving the directional control valve 115. And a pilot valve 116. This pilot valve 116 is driven by the piston 112,
Pilot pressure receiving chamber 11 defined below the directional control valve 115
7 is switched and connected to an exhaust passage 118 communicating with the supply port 113 and the exhaust port 114.

First, as shown in FIG. 3, the pilot valve 116 is moved upward to open the pilot pressure receiving chamber 117 in the supply port 11.
When the valve is connected to 3, the directional control valve 115 is driven upward by the internal pressure of the pilot pressure receiving chamber 117, and the supply port 113 is communicated with the cylinder chamber 111 via the directional control valve chamber 119, thereby applying pressure to the cylinder chamber 111. Compressed air is introduced and the piston 112 moves downward against the return spring 120.

As shown in FIG. 4, when the piston 112 descends by a certain amount or more, the pilot valve 116 is driven downward by the piston 112, and the pilot pressure receiving chamber 117 moves into the exhaust passage 11.
8 to communicate with the exhaust port 114, the directional control valve 115 moves downward due to the pressure of the pressurized air acting on the directional control valve 115 from the directional control valve chamber 119, and the cylinder chamber 111 communicates with the exhaust port 114. To be done. As a result, the cylinder chamber 111 is depressurized to the atmospheric pressure, and the piston 112 is driven upward by the elastic restoring force of the return spring 120, as shown in FIG.

When the piston 112 moves upward by a certain amount or more, the pilot valve 116 is driven upward by the piston 112, and the directional control valve 115 is switched to the position shown in FIG. 3 again. By repeating such a series of operations, the piston 112 reciprocates up and down, and the plunger 108
Will move back and forth in the plunger chamber 106 together with the piston 112.

When the internal pressure of the booster chamber 103 reaches a predetermined pressure, the plunger 108 is restricted from descending by the internal pressure of the plunger chamber 106, and the internal pressure of the plunger chamber 106 and the return spring
The total pressure with the pressure of 120 is from cylinder chamber 111 to piston 1
When balanced with the pressure acting on 12, piston 112 and plunger 108 stop. Then, the suction check valve 104 is biased to the closed position by the suction check valve spring 109.

In recent years, in order to achieve both miniaturization and high performance in pneumatic equipment, the air pressure is 25 to 50 kg / cm ² which is much higher than the conventional pressure of 5 to 8 kg / cm ^2.
It is required to pressurize to a certain degree, and it is difficult to increase the pressure to such a high pressure with a pressure booster that directly increases the pressure of hydraulic oil using a conventional reciprocating motion generating engine. Therefore, the inventor has found that compression of air, which is a compressible fluid, is much easier than compression of hydraulic oil, which is an incompressible fluid, and
Focusing on the fact that a working compressed fluid boosted to around 25 to 50 kg / cm ² can be easily obtained, air is compressed by a booster with the same structure as the conventional hydraulic compressor that is a non-compressed fluid. They tried to increase the pressure of air, which is a compressible fluid.

[0013]

However, in this conventional pressure booster, the inlet 101 of the pressure boosting chamber 103 is communicated with, for example, a hydraulic oil tank, so that when the cylinder chamber 111 is communicated with the exhaust port 114, A return spring 120 is needed to raise the piston 112 and the plunger 108,
This return spring 120 causes the piston 112 and the plunger 108 to
There is a problem in that the pressure increase efficiency is reduced due to resistance that increases the spring load due to an increase in deflection when the pressure is lowered.

Further, since the plunger chamber 106 has the suction check valve spring 109, the ratio of the void volume (waste volume) of the plunger chamber 106 to the stroke movement volume of the plunger 108 is large, and there is a problem that the discharge effect is reduced. The present invention has been made in view of the above circumstances, and an object thereof is to solve a technical problem of providing a pressure booster capable of enhancing discharge efficiency.

[0015]

SUMMARY OF THE INVENTION The present invention reciprocates a piston by alternately switching the supply and discharge of pressure fluid acting on the piston by means of a directional control valve. In order to achieve the above object, a pressure booster that reciprocates a plunger connected to the piston is performed by switching a pilot flow path by a pilot valve that is switched by a piston.

That is, the first booster according to the present invention is
A cylindrical pressure increasing chamber having an inlet and an outlet, an injection check valve for opening and closing the inlet and slidingly recessing the plunger from the side opposite to the inlet, a discharge check valve connected to the outlet, and a plunger. A cylindrical plunger chamber communicating with the inlet side portion of the pressure boosting chamber is formed in the injection check valve that is made to slide in, a pressurized fluid supply source is connected to the inlet, and the injection check valve is opened. , Pressurizing the plunger by injecting a pressurized fluid into the plunger chamber, whereby the reaction force applied to the piston and the supply and discharge of the pressure fluid acting on the piston by the directional control valve reciprocate the piston to increase the pressure. Characterize.

The second technical means according to the present invention is
A pressurized fluid supply source is connected to the inlet, and an annular friction body is externally fitted to one of the tip portion of the plunger and the peripheral surface of the plunger chamber, and the friction body is attached to the tip portion of the plunger at a predetermined contact pressure or It is characterized in that it is brought into contact with the inner peripheral surface of the injection check valve in the plunger chamber. Further, a third technical means according to the present invention is to connect a pressurized fluid supply source to the inlet, and replace the friction body with a latch member at one of the tip of the plunger and the peripheral surface of the plunger chamber. Provided,
The other side is provided with an engaging groove for engaging and disengaging the latch member.

[0018]

In the first pressure booster of the present invention, the pressurized fluid supply source is connected to the inlet, the injection check valve is opened and closed, and the pressurized fluid is caused to flow into the plunger chamber to press the plunger. Thus, the reaction force applied to the piston and the supply and discharge of the pressure fluid acting on the piston by the direction control valve reciprocate the piston to increase the pressure.

In the second pressure booster of the present invention,
It is generated between the friction chamber and the friction chamber of the suction check valve by bringing the friction body fitted on the tip of the plunger into contact with the plunger tip or the inner surface of the injection check of the plunger chamber with a predetermined contact pressure. Due to frictional force, the suction check valve moves back and forth in the pressure boost chamber in conjunction with the operation of the plunger,
As a result, the suction check valve opens and closes the inlet of the pressure boosting chamber.

Further, in the third pressure booster of the present invention, the suction check valve advances and retreats in the pressure boost chamber in conjunction with the operation of the plunger by the engagement of the latch member and the engagement groove, and the inlet of the pressure boost chamber. Will be opened and closed. And the first of the present invention
In the pressure booster, the plunger is urged in the direction to exit the plunger chamber by the pressurized air supplied from the inlet to the plunger chamber through the pressure boosting chamber, so that the plunger is urged in the direction to exit the plunger chamber. It is possible to omit the return spring, and it is possible to eliminate the decrease in pressure increasing efficiency due to the resistance of the return spring.

Further, in the second pressure booster and the third pressure booster of the present invention, the injection check valve spring can be omitted, the plunger can be brought into close contact with the inner circumference of the injection check valve, and the plunger chamber relative to the stroke movement volume of the plunger can be reduced. It is possible to reduce the ratio of the void volume (waste volume) of the above, and it is possible to eliminate the decrease in discharge efficiency.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A pressure booster according to an embodiment of the present invention will be specifically described below with reference to the accompanying drawings.
The present invention is not limited to this embodiment, but extends to the entire range of the technical idea truly intended by the present invention, which will be apparent from the entire description of the present specification and the accompanying drawings.

The pressure booster according to one embodiment of the present invention shown in each of the sectional views of FIGS. 1 and 2 includes a directional control valve 15 for alternately switching the supply and discharge of the pressure fluid acting on the piston 12, thereby allowing the piston 12 to move. The directional control valve 15 is reciprocated to switch the directional control valve 15 by reversing the reciprocating motion of the piston 12 to switch the pilot flow path 21 by the pilot valve 16 and the plunger 8 connected to the piston 12 is switched.
Injection check valve 4 for injecting the pressurized fluid flowing into the plunger chamber 6 from a certain direction, increasing the pressure, and discharging the fluid.
And a discharge check valve 5.

Further, a cylindrical pressure increasing chamber 3 having an inlet 1 and an outlet 2, an injection check valve 4 for opening and closing the inlet 1 and slidingly recessing the plunger 8 from the side opposite to the inlet 1.
A cylindrical plunger chamber 6 communicating with the inlet side portion of the pressure boosting chamber 3 is formed in an injection check valve 4 that slides into a discharge check valve 5 and a plunger 8 connected to the outlet 2. A pressurized fluid supply source is connected to the inlet 1, the injection check valve 4 is opened, pressurized fluid is caused to flow into the plunger chamber 6, and the plunger 8 is pressed, whereby the piston
Reaction force applied to 12 and piston by the direction control valve 15
The supply / exhaust of the pressure fluid acting on 12 causes the piston 12 to reciprocate, and the plunger 8 connected to the piston 12 reciprocates to increase the pressure.

At the tip of this plunger 8, for example, O
A friction body 9 made of a ring is fitted onto the outer periphery of the ring, and the friction body 9 is slidably brought into contact with the inner peripheral surface of the injection check valve 4 in the plunger chamber 6 at a predetermined contact pressure. This pressure booster includes a reciprocating motion generating engine 10 for driving the plunger 8. The reciprocating motion generating engine 10 has a reciprocating motion generating engine 10 except that the return spring 120 is omitted. It has the same structure as the generating engine 10.

That is, a cylindrical cylinder chamber 11 coaxial with the booster chamber 3 and the plunger chamber 6, and this cylinder chamber.
A piston 12 which is inserted into the shaft 11 so as to be able to move back and forth, and which is integrally connected to the plunger 8;
Pilot valve 16 for driving this directional control valve 15
With.

The pilot valve 16 is driven by the piston 12 to switch and connect the pilot pressure receiving chamber 17 defined below the direction control valve 15 to the exhaust port 18 communicating with the supply port 13 and the exhaust port 14. Is done. The inlet 1 of the pressure boosting chamber 3 and the supply port 13 of the reciprocating motion generating engine 10 are connected to a common or separate pressurized air supply source.

Reference numeral 19 is a directional control valve chamber that is always in communication with the supply port 13, and is connected to the cylinder chamber 11 or is disconnected from the cylinder chamber 11 depending on the position of the directional control valve 15. In this pressure intensifier, first, as shown in FIG. 1, the pilot valve 16 is raised and the pilot pressure receiving chamber 17
When the valve is connected to the supply port 13, the directional control valve 15 is driven upward by the internal pressure of the pilot pressure receiving chamber 17, and the supply port 13 is communicated with the cylinder chamber 11 via the directional control valve chamber 19. Pressurized air is introduced into 11 and piston
12 and the plunger 8 are moved downward against the internal pressure of the plunger chamber 7.

At the tip of the plunger 8, the plunger chamber 6
Since the friction body 9 that comes into contact with the inner peripheral surface of the container is contacted with a predetermined contact pressure, the injection check valve 4 descends as the plunger 8 descends, and the inlet 1 is closed. Therefore, there is no possibility that the discharge efficiency will decrease due to the closing delay of the injection check valve 4, and thereafter, when the plunger 8 further descends, the internal pressures of the plunger chamber 6 and the pressure boosting chamber 3 increase and the discharge check valve 5 opens. The air that has been valved and increased in pressure is discharged to the load circuit.

As shown in FIG. 2, when the piston 12 descends by a certain amount or more, the pilot valve 16 is driven downward by the piston 12, the pilot pressure receiving chamber 17 communicates with the exhaust port 14 through the exhaust passage 18, and the intake port 13 Is connected to the directional control valve chamber 19. As a result, the directional control valve 15 is moved downward by the internal pressure of the directional control valve chamber 19, and the cylinder chamber 11 is communicated with the exhaust port 14. This allows the cylinder chamber
The pressure of 11 is reduced to atmospheric pressure, and the internal pressure of the plunger chamber 6 drives the plunger 8 and the piston 12 upward.

What is important here is that the plunger 8 and the piston 12 are driven upward by the internal pressure of the plunger chamber 7, whereby the plunger 8 and the piston 12 are driven.
That is, the return spring for urging 12 upward is not necessary.
As a result, the resistance of the spring load, which unnecessarily increases due to the increase in the deflection of the return spring when the piston 12 and the plunger 8 descend, can be eliminated, and the pressure increasing efficiency can be improved.

When the piston 12 and the plunger 8 rise upward, the injection check valve 4 also rises along with the plunger 8, but at this time the discharge check valve 5 closes, so the pressure on the load circuit side decreases. That's not it. Also, since the fluid to be boosted in this booster is air,
It is especially suitable for use in textile factories, food factories, pharmaceutical factories, etc. where the use of oil is discouraged.

Further, although the plunger 8 is driven by the pneumatic reciprocating motion generating engine 10 in the above-described embodiment, for example, a hydraulic reciprocating motion generating engine in which pressure oil is used as a drive source instead of pressurized air is used. Drive the plunger 8 with the booster 3
A pressure oil supply source may be connected to the inlet of the. in addition,
In the above-described embodiment, the friction body 9 is externally fitted to the tip of the plunger 8 and the injection check valve 4 is driven by the frictional force of the friction body 9. However, instead of this friction body 9, the plunger 9 is replaced. 8, which is biased by a spring to support a ball that appears and disappears toward the peripheral surface of the plunger chamber 6 and a latch member such as a leaf spring that appears and disappears toward the peripheral surface of the plunger chamber 6,
An engagement groove for engaging and disengaging the latch member is formed on the circumferential surface of the plunger chamber 6, and the engagement check groove 4 is formed by these engagement grooves.
Can also be configured to be driven by the plunger 8.

Of course, the latch member may be provided so as to project and retract from the peripheral surface of the plunger chamber 6 toward the plunger 8, and the plunger 8 may be provided with an engaging groove for engaging and disengaging the latch member.

[0035]

As described above, according to the pressure booster of the present invention, the injection check valve is closed by the friction force of the friction member or the engagement of the latch member and the engaging groove with the lowering of the plunger. Since the valve is opened, the discharge efficiency will not be lowered due to the closing delay of the injection check valve.

Further, according to the pressure booster of the present invention, since the pressurized fluid supply source is connected to the inlet of the pressure boosting chamber, the pressurized fluid urges the plunger in the direction to leave the plunger chamber. To increase the boosting efficiency by omitting the return spring that biases the plunger in the direction of exiting the plunger chamber and reducing the resistance of the spring load that increases unnecessarily due to the increased deflection when the plunger enters the plunger chamber. Can be done.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a transition from an injection stroke to a discharge stroke according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view of the transition from the discharge stroke to the injection stroke according to the embodiment of the present invention.

FIG. 3 is a sectional view of a discharge process of a conventional example.

FIG. 4 is a sectional view of a discharge process of a conventional example.

FIG. 5 is a sectional view of a suction stroke of a conventional example.

[Explanation of symbols]

 1 ... Inlet 2 ... Outlet 3 ... Pressure boosting chamber 4 ... Injection check valve 5 ... Discharge check valve 6 ... Plunger chamber 8 ... Plunger 9 ... Friction body 10 ... Reciprocating motion engine 20 ... Discharge port

Claims (3)

[Claims] 1. A pilot which reciprocates the piston by alternately switching supply and discharge of a pressure fluid acting on the piston by a directional control valve, and the switching operation of the directional control valve is switched by the piston by reciprocating the reciprocating motion of the piston. In a pressure booster that reciprocates a plunger connected to the piston by switching a pilot flow path by a valve, a cylindrical pressure boosting chamber having an inlet and an outlet, and a slidable pressure boosting chamber. An injection check valve that opens and closes the inlet so that the plunger is recessed from the side opposite to the inlet, a discharge check valve that is connected to the outlet, and an injection check valve that slides the plunger into the injection check valve. A cylindrical plunger chamber communicating with the portion is formed, a pressurized fluid supply source is connected to the inlet, the injection check valve is opened, and the plunger chamber is opened. A pressure booster characterized in that a pressurized fluid is flown in to press the plunger, and the reaction force applied to the piston thereby causes the piston to reciprocate by the supply and discharge of the pressure fluid acting on the piston to increase the pressure. . 2. An annular friction body is externally fitted to one of the plunger tip and the peripheral surface of the plunger chamber, and is brought into contact with the plunger tip or the peripheral surface of the plunger chamber with a predetermined contact pressure of the friction body. The pressure booster according to claim 1, wherein: 3. A latch member is provided in place of one of the tip of the plunger and the peripheral surface of the plunger chamber, instead of the friction body.
The booster according to claim 1, wherein an engaging groove for engaging and disengaging the latch member is provided on the other side.