KR100210703B1 - Gas booster - Google Patents

Abstract

The first cylinder hole 7 for accommodating the first piston 8, the plunger hole 20 for accommodating the plunger 21, and the second cylinder hole 57 for accommodating the second piston in order from above. Install. The plunger 21 is fixed to the first piston 8. The cushion chamber 61 provided below the second piston 58 connects the outlet 25b of the second check valve 25 for gas discharge to the communication path 62. The movement of the second piston 58 upwards beyond the set amount is prevented by the stopper portion 64 provided on the circumferential wall of the second cylinder hole 57.

Description

Gas intensifier

1 to 3 show a first embodiment, in which FIG. 1 is a longitudinal sectional view of a gas intensifier.

2 is an explanatory view of the operation of the piston motor of the booster.

3 is an operation explanatory diagram of a gas pump of the intensifier.

4 shows a second embodiment and shows a part of the brake means of the first piston.

5 and 6 show a third embodiment, in which FIG. 5 corresponds to FIG. 4 above.

6 is a view corresponding to FIG. 2 above.

FIG. 7 shows the fourth embodiment and corresponds to FIG.

The present invention connects a large diameter piston reciprocated by a pressure fluid such as compressed air and a small diameter plunger to be inserted into the plunger chamber in series, and introduces a low pressure gas introduced into the plunger chamber to the piston and the plunger. It relates to a gas intensifier of a type in which pressure is increased in response to a ratio.

In general, a hydraulic clamp is employed as a fluid pressure clamp for fixing a mold to a fixing table such as an injection molding machine. This hydraulic clamp is excellent in miniaturizing the clamping device because strong clamping force is obtained by high pressure oil of about 250kgf / cm2, but if the oil leaks even in a very small amount from the packing for high pressure oil encapsulation, The oil is contaminated by the leakage. For this reason, there has been a limit to the need for hydraulic cleaning to meet the needs of ultra-cleaning in recent years, which has become particularly interesting.

MEANS TO SOLVE THE PROBLEM The present inventor considered the following clamping system first, in order to make both the said cleaning demand and the compactness of a fluid pressure clamp compatible. The system is a technique in which about 5 kgf / cm 2 of compressed air supplied from an air compressor is boosted to about 40 kgf / cm 2 by a gas intensifier, and the high-pressure air is used as a working fluid of the fluid pressure clamp.

The gas intensifier is configured to drive the gas pump by the pneumatic piston actuator described in the US patent 4,042,311 or US patent 4,812,109.

That is, the actuating chamber is installed above the pneumatic piston, and the compressed air is supplied to and discharged from the actuating chamber by the supply and discharge telephone means, and the smaller diameter plunger is lowered from the pneumatic piston than the pneumatic piston. The plunger chamber is provided below the plunger, and the first check valve for gas import and the second check valve for gas discharge are connected to the lower part of the plunger chamber.

The gas intensifier has a structure in which a downward fluid pressure acting on the pneumatic piston in the actuating chamber is driven downward by an upward discharge reaction force acting on the plunger in the plunger chamber to lower the pneumatic piston. At high loads after which the discharge pressure is sufficiently high, the piston and the plunger are driven down at a low speed. For this reason, the piston has a low inertia inertia at high loads, and when the piston descends until just before the bottom dead center, if the compressed air is discharged from the actuation chamber by the rapid distribution switch, the piston immediately reverses. Switch to the upward return stroke.

On the other hand, when the discharge pressure is low, the piston and the plunger are driven down the highway, so the descending inertia force of the piston is large. As a result, the run down of the plunger becomes large.

In the above technical background, the prior art known to the inventors knows that the depth dimension of the plunger chamber is lowered in order to prevent the plunger from colliding with the bottom wall of the plunger chamber at the end of the lower stroke of the first piston. It was set to a value deeper than the lower stroke of the plunger.

The prior art has the following problems.

The gas pump has a lower bottom dead center of the piston at higher loads than at lower loads, so that the gap between the bottom wall of the plunger chamber and the lower end of the plunger is large. For this reason, the compression ratio of the plunger chamber is small, and the gas discharge amount is reduced by the smaller the compression ratio. As a result, the boosting time by the gas intensifier is long.

An object of the present invention is to shorten the boosting time.

In order to achieve the above object, the present invention is configured a gas intensifier as follows.

The first cylinder hole 7, the plunger hole 20 smaller in diameter than the first cylinder hole 7, and the second cylinder hole 57 are formed in this order from above. The first piston 8 inserted into the first cylinder hole 7 and the plunger chamber 23 inserted into the plunger hole 20 are connected up and down, and the second cylinder hole 57 2 Insert the piston (58). A pressure fluid is supplied or discharged to the actuation chamber 9 formed between the upper end wall 7a of the first cylinder hole 7 and the first piston 8 described above. . The plunger chamber 23 is formed between the plunger 21 and the second piston 58, and the lower wall 60 of the second cylinder hole 57 and the second piston 58 are formed. The cushion chamber 61 is formed between and. In the lower portion of the plunger chamber 23, a first check valve 24 for gas import and a second check valve 25 for gas discharge are connected. The cushion chamber 61 and the outlet 25b of the second check valve 25 are connected by a communication path (communication path) 62. The stopper unit 64 prevents the second piston 58 from moving upwards beyond the set amount.

The present invention works as follows.

At the time of low load, since the pressure of the outlet 25b of the 2nd check valve 25 and the plunger chamber 23 is low, the 1st piston 8 and the plunger chamber 23 will drive down rapidly, and the 1st piston 8 ) Has a large descending inertia. For this reason, at the end of the lower stroke, the lower end 21a of the plunger 21 abuts against the second piston 58, and the plunger 21 continues against the gas pressure of the cushion chamber 61. 58) Press to lower. On the other hand, when the plunger 21 reverses and rises, the second piston 58 returns from the lowered position to the raised position by the pressure of the cushion chamber 61.

As the plunger 21 repeats the lifting stroke, the pressure at the outlet 25b of the second check valve 25 gradually rises. As a result, the descending speed of the first piston 8 becomes slow, so that the inertia force at the time of the lowering of the first piston 8 and the plunger 21 becomes small, and the overrun of the lower end of the plunger 21a decreases. Going. Following this, the height position of the second piston 58 is raised by the pressure acting on the second piston 58 from the cushion chamber 61, so that the lower end 21a of the plunger 21 and the second piston ( 58) Either the gap with or disappears small. For this reason, the compression ratio of the plunger chamber 23 can be maintained at a large value.

The present invention is configured and operated as described above, so that the compression ratio of the plunger chamber at high load can be increased to increase the gas discharge amount from the low load to the entire region at high load, so that the boosting time can be shortened.

Furthermore, since the downward movement of the plunger 21 can be buffered by the compression operation of the cushion chamber 61, the downward movement is slowly decelerated, and the impact force due to the collision between the plunger 21 and the second piston 58 is reduced. This ends small. As a result, the gas intensifier is low in vibration and noise.

[First Embodiment]

3 to 3 show a first embodiment.

In Fig. 1, reference numeral 1 denotes a gas intensifier, which is a pneumatic piston actuator 2 for generating a reciprocating linear motion using compressed air and a plunger type gas which is driven by the actuator 2 to boost the gas. It consists of the pump 3.

The mover 2 has a mover main body 4 for converting the pressure energy of the compressed air into power, and compressed air is supplied and discharged to the main mover main body 4 by the rapid distribution switching means 5. These mover main bodies 4 and the rapid distribution switching means 5 are fastened to the gas pump 3 by the plurality of tie rods 6.

The actuating body 4 is configured as follows.

The first piston 8 is inserted into the first cylinder hole 7 via a packing 10 in a gastight manner in an airtight direction. An actuation chamber 9 is formed between the upper end wall 7a, which is the first end wall of the first cylinder hole 7, and the first piston 8. When compressed air is supplied to the actuation chamber 9, the first piston 8 is driven to the bottom dead center side. On the other hand, when the compressed air is discharged from the actuation chamber 9, the first piston 8 can be returned to the top dead center side.

The supply and discharge switching means (5) has a supply and drain valve 13, the actuation chamber (9) through the supply and drain valve 13, the pressure supply port (14) and the back pressure port (排 壓 口) It is selectively connected to (15). The pressure supply port 14 is connected to the air compressor 17 via the pressure reducing valve 16. The discharge pressure of the compressor 17 can be set within the range of 5.0 to 9.9 kgf / cm 2. In addition, the exhaust port 15 is open to the atmosphere side. The above-described supply / discharge valve body 30 is configured to be switchable between the pressure supply position X and the back pressure position Y (see FIG. 2) of the compressed air by the pilot valve 18.

The plunger type gas pump 3 is configured as follows.

A plunger hole 20 of smaller diameter than the first cylinder hole 7 is formed in series below the first cylinder hole 7. The plunger 21 is inserted into the plunger hole 20 freely in the vertical direction through the packing 10 so that the upper portion of the plunger 21 is connected to the first piston 8. The plunger chamber 23 was formed below the lower end 21a of the plunger 21. The outlet 24b of the first check valve 24 for gas import and the inlet 25a of the second check valve 25 for gas extraction are connected to the lower part of the plunger chamber 23. The compressor 17 is connected to the inlet 24a of the first check valve 24.

When the first piston 8 is driven downward, the plunger lower end 21a enters the plunger chamber 23 to increase the internal pressure, and simultaneously presses and closes the valve body 26 of the first check valve 24. The valve body 27 of the second check valve 25 is pressed to open and discharge the compressed air that has been increased in pressure at the outlet 25b. On the contrary, in the rising return stroke, the valve body 26 is pressed by the pressure of the inlet 24a of the first check valve 24 so that about 5 kgf / cm 2 of compressed air is introduced into the plunger chamber 23. As a result, the plunger 21 raises and returns the first piston 8 by the pressure. By repeating the above steps, the discharged compressed air finally reaches a pressure of 40 kgf / cm 2 or more.

The specific configuration of the above-mentioned rapid-switching means 5 will be described with reference to FIGS. 1 and 2 above. The left peninsula and the first diagram in FIG. 2 represent the initial state of the lower driving stroke of the first piston 8, and the right peninsula in the second diagram is the rising return stroke of the first piston 8 in the statue. Indicates the initial state of.

The supply / discharge valve 13 may insert a normal supply / discharge valve body 30 into the supply / discharge valve box 29 fixed to the upper portion of the upper end wall 7a of the cylinder hole 7. When the valve body 30 is pushed up, the valve body 30 is switched to the sudden pressure position X of the left peninsula in FIG. 2 and is pushed down to switch to the back pressure position Y of the right peninsula in FIG.

The pressure port 14 is provided in the filter 37, the pressure operating chamber 33, the pressure compression valve seat 29a, the working chamber 32, the back pressure side seat 29b, the back pressure chamber 34, The back pressure hole 38 communicates with the back pressure port 15 in the order of the outlet chamber 39. The exit chamber 39 has a silencer 40 built therein. Further, the hydraulic pressure operating chamber 33 is communicated with the back pressure operating chamber 35 via a through hole 30d of the valve body 30. The back pressure working chamber 35 is partitioned from the back pressure chamber 34 by a 0 ring 42.

As shown in the left peninsula of FIG. 2, when the pressure distribution valve body 30 is pushed up to switch to the pressure supply position X, the hydraulic pressure receiving surface 30a provided at the lower part of the valve body 30 is the pressure supply side. The back pressure side pressure receiving surface 30b provided at the height of the middle of the valve body 30 in phase while the hydraulic pressure operating chamber 33 and the working chamber 32 communicate with each other is separated from the seat 29a. The sheet 29b is stuck to the work chamber 32 and the back pressure chamber 34 to be blocked.

Contrary to this, as shown in the right peninsula in FIG. 2, when the supply and drain valve body 30 is pushed down to the back pressure position Y, the hydraulic pressure receiving surface 30a for the hydraulic operation is attached to the hydraulic pressure side sheet 29a. At the same time between the hydraulic pressure working chamber 33 and the working chamber 32 is blocked, the back pressure side pressure receiving surface 30b is separated from the back pressure side sheet 29b, and the working chamber 32 and the back pressure chamber 34 are closed. It is communicating.

The pilot valve 18 switches the feed valve body 30 to the feed pressure position X and the back pressure position Y, so that the piston type pilot valve box 71 and the first piston are used. A spool 46 fixed to (8) includes a pressure relief valve seat 48, a pressure relief valve body 53, and a pressure relief seat 52 made of a zero ring.

In more detail, the cylinder chamber 70a of the pilot cylinder 70 is formed in the upper part of the supply / discharge valve box 29, and the pilot valve box 71 connects the 0 ring 72 to the cylinder chamber 70a. The airtight movement is inserted freely in the vertical direction through the gap. Moreover, the hydraulic pressure operation chamber 70b formed facing the lower surface of the pilot valve box 71 communicates with the back pressure operation chamber 35. The pilot valve box 71 is driven upward against the pressure of the return spring 73 by the internal pressure of the hydraulic pressure operation chamber 70b. The support cylinder 31 which protrudes downward from the pilot valve box 71 is inserted into the cylinder hole 30d of the supply / discharge valve body 30, and the pressure-sensitive seat (B) is inserted into the lower portion 49 of the support cylinder 31. 48) is mounted from the bottom side. The pressure relief valve body 53 is pressurized to close the valve downward by the valve closing spring 54 to the pressure relief seat 52 provided in the upper part of the pilot valve box 71. The pressure relief port 51 disposed above the pressure relief valve body 53 communicates with the back pressure port 15.

In the state where the spool 46 descending in parallel with the movement of the first piston 8 is at the top dead center indicated by the solid line of the left peninsula in the second figure, and is at the bottom dead center indicated by the two-dot chain line in the left peninsula. In the case of switching, the pressure relief valve body 53 is first attached to the pressure relief seat 52 so that the pressure relief port 51 is closed, and then the outer peripheral face of the spool 46 and the inner peripheral face of the pressure sensitive seat 48 are separated from each other. To start. Then, the compressed air in the hydraulic pressure operating chamber 33 opens the gap between the spool 46 and the seat 48, and the pilot valve chamber 45 and the through hole of the support cylinder 31. Through 31a, it introduces into the back pressure operation chamber 35 and the hydraulic pressure operation chamber 70b.

According to the internal pressure of the hydraulic operation chamber 70b, as shown by the solid line in the right peninsula, the pilot valve box 71 is raised against the pressure pressure of both springs 73 and 54 so that the pressure-pressure seat 48 is lifted. It is rapidly separated from the spool 46. As a result, the pressurized air is rapidly introduced into the back pressure working chamber 35, and the compressed air is pushed down strongly to the pressure drain valve body 30 to switch to the back pressure position Y on the right peninsula. As a result, the actuation chamber 9 communicates with the back pressure port 15 through the path of the supply / exhaust hole 36, the working chamber 32, the back pressure chamber 34, and the back pressure hole 38, so that the first piston 8 Upward return strokes are possible.

In addition, when the above-mentioned supply / discharge valve body 30 is pushed down, the pressure-reducing hydraulic pressure surface for the pressure-operating operation from the force exerted on the pressure-receiving area of the back pressure-side pressure-receiving surface 30b by an upward back pressure resistance received by the valve body 30 during its descending degree. It falls by the force applied to the hydraulic pressure area of 30a). For this reason, the rapid-discharge valve body 30 increases the falling speed during the lowering degree, and is surely switched to the back pressure position Y.

Contrary to the above, when the spool 46 is shifted from the bottom dead center position indicated by the solid line in the right peninsula to the top dead center position indicated by the solid line in the left peninsula in association with the rise of the first piston 8, first, the spool 46 The outer circumferential surface of the sheet 48 blocks and contacts the inner circumferential surface of the seat 48. Then, the pressure relief valve body 53 is separated from the pressure relief seat 52 against the valve receiving spring 54 to operate the back pressure operating chamber 35. Is communicated with the back pressure port 15 through the gap between the through hole 31a of the support cylinder 31, the seat 52 and the valve body 53, and the path of the pressure relief port 51. . As a result, the supply / discharge valve body 30 is pushed up to the differential pressure up and down to switch to the pressure supply position X on the left peninsula. Then, the actuation chamber 9 communicates with the pressure inlet port 14 from the path of the supply / exhaust hole 36, the working chamber 32, and the pressure-operating chamber 33, so that the downward driving stroke of the first piston 8 is performed. It is disclosed.

Said gas pump 3 is further comprised as follows.

As shown in FIG. 1, a second cylinder hole 57 of the same diameter as that of the hole 20 is provided below the plunger hole 20. As shown in FIG. The second piston 58 facing the lower end 21a of the plunger 21 is inserted into the second cylinder hole 57 through the zero ring 50 in a hermetic movement freely. A cushion chamber 61 is provided between the second piston 58 and the cover bolt 60. The cover bolt 60 constitutes the second end wall of the second cylinder hole 57. The cushion chamber 61 and the outlet 25b of the second check valve 25 are connected by a communication path 62.

In addition, the second piston 58 is pressed upward by the return spring 63 attached to the cushion chamber 61. The second piston 58 moves upward beyond the set amount by bringing the plunger 66 below the second piston 58 into contact with the stopper portion 64 of the circumferential wall of the second cylinder hole 57 from below. It is deterring. The narrowed part 68 of the said communication path 62 was comprised along the notch groove of the said plunger 66. As shown in FIG.

The second piston 58 and the cushion chamber 61 operate as follows, as shown in FIG. 3 (a) (b) (c) show the operation at low load, FIG. 3 (a) shows the plunger 21 at the top dead center, and FIG. 3 (b) shows the plunger 21 FIG. 3C shows a state in which the plunger 21 is lowered to the bottom dead center under high load.

In the state of FIG. 3A, the plunger 21 is returned to the top dead center by the compressed air introduced into the plunger chamber 23 from the first check valve 24. Further, the force of the difference between the upward force due to the compressed air introduced into the cushion chamber 61 and the downward force due to the internal pressure of the plunger chamber 23 and the return spring 63 are shot. By the force of pressure, it presses upwards. Reference numeral S denotes an allowable stroke of the second piston 58.

As shown in Fig. 3 (b), when the plunger 21 is lowered and the pressure in the plunger chamber 23 rises, the second check valve 25 opens, and the compressed air pressurized from the outlet 25b is opened. Is discharged. Then, the pressure acts on the cushion chamber 61 from the communication path 62 to hold the second piston 58 in the raised position.

At the time of low load, since the pressure of the outlet 25b of the 2nd check valve 25 and the plunger chamber 23 is low, the said by the 1st piston 8 (refer FIG. 1 or FIG. 2), The plunger 21 descends and drives rapidly. As a result, the lower end 21a of the plunger 21 abuts on the second piston 58 and continues as shown in FIG. 3 (c). The second piston 58 is pressed down against the return spring 63. Then, the compressed air in the cushion chamber 61 is further compressed and pushed out through the communication path 62 to the outlet 25b of the second check valve 25.

Reference numeral C in the figure indicates the lower stroke of the plunger 21 in the low pressure discharge state.

As the cushion chamber 61 performs the above compression operation, the downward movement of the plunger 21 can be buffered and the downward movement can be slowly decelerated, so that the impact force due to the collision between the plunger 21 and the second piston 58 is reduced. Ends small. In addition, during this cushioning operation, the rate of increase in pressure of the cushion chamber 61 can be reduced because the flow rate of the compressed air pushed out of the communication path can be reduced by the flow resistance given by the narrowed portion 62 provided in the communication path 62. This becomes large and can fully buffer the downward movement of the plunger 21. As a result, the vibration and noise of the gas intensifier are reduced.

On the other hand, in the rising return stroke, the plunger 21 rises due to the pressure of the gas introduced into the plunger chamber 23 from the first check valve 24. Then, the second piston 58 returns to the lifted position shown in FIG. 3 (a) from the lowered position of FIG. 3 (c) by the pressure of the cushion chamber 61 and the spring 63. FIG.

As the plunger 21 repeats the above-mentioned lifting stroke, the pressure at the outlet 25b of the second check valve 25 gradually increases. As a result, the descending speed of the first piston 8 becomes slow, so that the inertia force becomes small in the lowering formula of the first piston 8 and the plunger 21, and the overrun of the plunger lower end 21a decreases. For this reason, the falling stroke D of the plunger 21 becomes small at the time of high load of FIG. 3 (b) compared with the case of low load.

Correspondingly, the pressure in the cushion chamber 61 is increased due to the increase in the pressure of the outlet 25b of the second check valve 25, and the height position of the second piston 58 is gradually decreased in the end of the discharge stroke. Since it rises, the space | interval of LG of the plunger 21 and the 2nd piston 58 may disappear or may be small. For this reason, the compression ratio of the plunger chamber 23 can be maintained at a large value, and the gas discharge amount is large even at high load.

In addition, by providing a return spring 63 for pressing down the second piston 58 upwards, the second piston 58 is supported by the return spring 63 even when the gas pressure of the cushion chamber 61 is low at the time of low load. Since it can be reliably pressed by the plunger lower end 21a, a compression ratio can be enlarged. As a result, the pressure intensifier 1 has a large compression ratio in all areas of operation, and the average discharge amount is further increased.

Further, brake means 75 is provided to decelerate the ascending speed of the first piston 8 when it rises to near the top dead center of the first piston 8.

That is, a third cylinder hole 76 is provided in the upper end wall 7a of the first cylinder hole 7 above the actuation chamber 9. The third cylinder hole 76 is formed with a diameter smaller than that of the plunger hole 20. In addition, the third piston (77) is inserted into the third cylinder hole (76) in the up and down direction via the packing 78, and is freely fitted in the hermetic shape. The third piston 77 is fitted between the plunger 21 and the spool 46 in a state where the installation door and the first piston 8 can move together.

As shown in FIG. 2, a braking chamber 79 is formed on the side of the third piston 77 in the third cylinder hole 76 at the end of the upward movement of the first piston 8 above. do. The braking chamber 79 and the pressure supply port 14 described above are connected by a communication path 81. The opening and closing means 82 for opening and closing the communication path 81 includes a groove 83 formed in the lower portion of the spool 46 and a through hole 84 in the upper wall 7a of the first cylinder hole 7. ).

The braking chamber 79 and the opening and closing means 82 operate as follows.

In the right peninsula of the second diagram above, when the first piston 8 rises to the position of the one-dot chain diagram from the bottom dead center shown in the solid diagram, the third piston 77 also has one-dot chain at the position of the solid diagram. We go up to the position of the lead.

In the initial stage of the upward movement of the first piston 8, the compressed air in the actuation chamber 9 is indicated by a double-dotted line arrow in the middle period, so that the supply / exhaust hole 36, the working chamber 32, and the back pressure chamber ( 34) is discharged to the outside through the path of the back pressure hole 38. In addition, while the braking chamber 79 communicates with the actuation chamber 9, the upper outer circumferential surface of the spool 46 blocks the through hole 84.

When the first piston 8 of the statue rises to near the top dead center, the third piston 77 abuts against the packing 78 to seal the above-mentioned braking chamber 79. At the same time, the groove 83 of the spool 46 faces the through hole 84 to communicate with the braking chamber 79. Then, the compressed air in the operating chamber 33 is introduced into the braking chamber 79 in the groove 83 to press the third piston 77 downward by the pressure. As a result, the ascending speed of the first piston 8 is decelerated, and compressed air at the outlet 25b of the first check valve 24 is slowly introduced into the plunger chamber 23, so that the plunger chamber 23 The pressure goes up. Then, the pushing force acting on the plunger 21 from the plunger chamber 23 overcomes the force pushed down in the braking chamber 79 to move the first piston 8 to the top dead center.

Thus, since the pressure which receives the plunger chamber 23 becomes high, the next discharge amount also increases. This increase in discharge amount is a significant advantage when the pressure at the outlet 25b of the second check valve 25 is low. That is, as described above, the gas pump 3 is balanced by the lowering driving force acting on the first piston 8 in the actuation chamber 9 and the discharge reaction force acting on the plunger 21 in the plunger chamber 23. As it operates, the pressure in the actuation chamber 9 increases as the pressure of the outlet 25b increases. In other words, the pressure of the actuation chamber 9 is lower at lower load than at higher load. For this reason, at the time of the low load, the back pressure resistance in the actuation chamber 9 is small and the rise return time of the first piston 8 is short. As a result, the pressure which the plunger chamber 23 receives is low, and the next discharge amount is also small. However, according to the brake means 75 of the present invention, since the following discharge amount can be increased by increasing the receiving pressure of the plunger chamber 23 at the time of low load, the average discharge amount is increased and the set pressure (here, about 40 kgf / cm 2) is reached. The boosting time until it can be shortened. Moreover, of course, even under high load, the pressure which the plunger chamber 23 receives becomes high, and of course, the next discharge amount increases.

The above first embodiment can be modified as follows.

The gas intensifier 1 may be arranged in a vertical posture, and may be in a horizontal posture, in an oblique posture, or in an upside down position.

The quick-switching means 5 may be of the type described in the above-mentioned US Patent 4,042,311 or US Patent 4,812,109 or the like.

The plunger hole 20 and the cylinder hole 57 are preferably made of the same diameter, but may be different diameters.

A return spring for raising and returning the first piston 8 may be added below the first piston 8.

The return spring 63 provided in the cushion chamber 61 can also be omitted. However, by providing the return spring 63, the second piston 58 can be pressed against the plunger 21 by the spring 63 during low pressure operation, so that the compression ratio at the time of low load is also large and the average compression ratio is high. It has the advantage of being. The working fluid of the gas pump 3 may be nitrogen gas or helium gas instead of compressed air. The gas boosted by the gas pump 3 may be a kind of gas different from the gas supplied to the mover 2.

The packing 10, 59, 78 of each cylinder hole 7, 57, 76 may be X ring, U packing, or the like instead of the 0 ring.

4, 5, 6 and 7 show the second to fourth embodiments, respectively. In these Examples, the same code | symbol was attached | subjected to the member of the structure similar to said 1st Example in principle.

Second Embodiment

In this embodiment, the brake means 75 is changed as follows.

As shown in FIG. 4, the through hole 84 and the spool 46 of the cylinder upper wall 7a were closed by the packing 86. As shown in FIG. Moreover, the opening-closing means 82 is comprised by the check valve body 87 provided in the communication path 81, and the rod 88 which opens the valve protruding downward from the valve body 87. As shown in FIG. The check valve seat 89, which becomes the zero ring, is stopped by the support cylinder 90 from the lower side.

Then, when the first piston 8 has risen to near the top dead center, the first piston 8 pushes up the rod 88 to separate the check valve body 87 from the 0 ring 90. As a result, the compressed air in the pressure port 14 is introduced into the braking chamber 79 through the communication path 81.

Third Embodiment

In this embodiment, the brake means 75 is changed as shown in FIG. 5 and FIG.

As shown in FIG. 4, the spool 46, the cylinder top wall 7a, and the through hole 84 were closed with a packing 92. As shown in FIG. In addition, the braking chamber 99 communicates with the actuation chamber 9 through a narrow interval 93 df which is a fitting interval between the third cylinder hole 76 and the third piston 77.

The interval 93 in which the braking chamber 79 is narrowed operates as follows.

In the right peninsula of FIG. 6, when the first piston 8 ascends to the position of the one-dot chain diagram at the bottom dead center shown in the solid diagram, the third piston 77 is also the position of the one-dot chain diagram at the position of the solid diagram. Going up.

In the middle stage at the beginning of the upward movement of the first piston 8, the compressed air in the actuation chamber 9, as indicated by the double-dotted line chart, the supply / exhaust hole 36, the working chamber 32, and the back pressure. Discharged to the outside through the path of the seal 34 and the back pressure hole 38. In addition, the braking chamber 79 is open to the actuation chamber 9.

When the first piston 8 ascends close to the top dead center, the third piston 77 fits into the third cylinder hole 76 and the throttle action of the narrowed interval 93 causes the Increase the internal pressure. Since the internal pressure is applied to the upper surface of the third piston 77 as the back pressure, the ascending speed of the first piston 8 is decelerated, and the compressed air at the outlet of the first check valve (not shown here) is plunger chamber 23. ) Is introduced slowly, and the pressure to receive the plunger chamber 23 becomes high.

Then, the pushing force acting on the plunger 21 in the plunger chamber 23 overcomes the pushing force in the braking chamber 79 to move the first piston 8 to the top dead center. Therefore, even at the time of low load, since sufficient gas can be taken in the plunger chamber 23 and the pressure of the chamber 23 can be raised, the next discharge amount will increase. As a result, the gas intensifier increases the average discharge amount and can shorten the boosting time until the set pressure (here, about 40 kgf / cm 2) is reached. In addition, in obtaining the above-mentioned advantages, since only the third piston 77 is fitted into the third cylinder hole 76, the configuration is simplified.

Fourth Embodiment

In this embodiment, the brake means 75 shown in Figs. 5 and 6 is further changed as follows.

As shown in FIG. 7, the third cylinder hole 76 and the third piston 77 are blocked by the packing 95, and the braking chamber 79 and the actuation chamber 9 are exhausted to the exhaust path 96. The throttle valve 97, which is a needle valve, is provided in the exhaust passage 96. Then, when the first piston 8 rises to near the top dead center and the third piston 77 is hermetically fitted to the third cylinder hole 76, the braking chamber is caused by the throttle action of the throttle valve 97. The internal pressure of 79 is raised to slow down the rising speeds of the first piston 8 and the plunger 21. As a result, the pressure to receive in a plunger chamber becomes high, and the next discharge amount becomes large by that much, and a pressure raising time can be shortened. In addition, since the exhaust speed in the braking chamber 79 can be adjusted by the throttle valve 97, there is an advantage that the brake force can be unadjusted to the first piston 8.

In addition, the exhaust path 96 may communicate with the actuation chamber 9 and communicate with the supply / exhaust hole 36 or the like.

The present invention is not limited to the above embodiments and can be variously changed according to the technical concept of the present invention, which will be included in the range of equivalents by the scope of the claims.

Claims (7)

The gas intensifier includes a fluid pressure piston actuator 2 provided on the first end side, and a plunger type gas pump 3 provided on the second end side, and includes a first cylinder hole 7 having a first end wall 7a. ), A plunger hole 20 having a diameter smaller than that of the first cylinder hole 7, and a second cylinder hole 57 having a second end wall 60 are sequentially formed from the first end side to the second end side. The first piston 8 is inserted into the first cylinder hole 7, the plunger 21 is inserted into the plunger hole 20, and is connected to the first piston 8. The second piston 58 is inserted into the second cylinder hole 57, and the actuation chamber 9 is formed between the first end wall 7a and the first piston 8 to supply and discharge. The pressure fluid is supplied or discharged by the switching means 5, the plunger chamber 23 is formed between the plunger 21 and the second piston 58, and the cushion chamber 61 is Second end wall 60 and the above second blood It is formed between the ton 58, the first check valve 24 for gas import and the second check valve 25 for discharge having the outlet 25b and the second of the plunger chamber 23 The communication passage 62 connects the cushion chamber 61 and the outlet 25b of the second check valve 25, and the stopper portion 64 is connected to the end portion. And a piston (58) configured to support movement over the set amount to the first end side. The gas intensifier according to claim 1, wherein a return spring (63) for suppressing the second piston (58) on the first short axis is provided in the cushion chamber (61). The gas intensifier according to claim 1 or 2, wherein a narrow portion (68) is provided in the communication passage (62). The method according to any one of claims 1 to 3, wherein the third cylinder hole (76) faces the actuation chamber (9) in the first end wall (7a) of the first cylinder hole (7). And a third piston (77) inserted into the third cylinder hole (76) to the first end portion of the first piston (8), wherein the first end wall (7a) and the third The braking chamber 79 is formed between the piston 77 and the braking chamber 79 is formed, and the braking chamber described above when the movement of the first piston 8 to the first short axis is completed. A gas intensifier provided with a means for increasing the internal pressure of (79). 5. The method according to claim 4, wherein the third piston (77) is hermetically fitted to the third cylinder hole (76) when the movement of the first piston (8) to the first short axis is completed. The communication path 81 which connects the pressure supply port 14 of the quick-switching switching means 5 and said braking chamber 79 is provided, and at the beginning of the movement to the 1st end side of the said 1st piston 8 is provided. The gas which interlocked and connected the opening-and-closing means 82 which open and operate the frost-shaped communication path 81 when the frostbite movement is complete | finished to block and operate the said communication path 81 by steam to the 1st piston 8 of the frostbite. Intensifier. 5. The method according to claim 4, wherein when the movement to the first end side of the first piston (8) is finished, the third piston (77) is fitted to the third piston (76) by a narrow gap 93, And a gas intensifier in which said braking chamber (79) is in communication with said actuation chamber (9) via said narrowing interval (93). The said third piston 77 is airtightly fitted into the said 3rd cylinder hole 76, when the movement to the 1st end side of the said 1st piston 8 is complete | finished, The said The gas intensifier of which the exhaust path 96 communicated with the said braking chamber 79 is provided in the 1st end wall (7a), and the throttle valve was provided in the exhaust path (96).