KR100486847B1 - Pressure Intensifying Cylinder - Google Patents

Abstract

The present invention relates to a pressure-increasing cylinder that improves the performance and output of pneumatic cylinders and hydraulic cylinders widely used in all fields of the industry, and is formed on the front and rear of the main body in the pressure-increasing cylinder operated by pneumatic or hydraulic pressure, and thus the operating piston and the pressure piston By installing a pilot rod valve in which opening and closing is controlled by a hydraulic vehicle or a pneumatic differential in the first and second operating chambers for driving the engine, and a check valve is further installed in the second operating chamber formed at the rear to drive the pressure piston, At low loads, both the check valve and the quick rod valve are kept closed so that only the working piston is moved forward. At high loads, the check valve is closed and the quick rod valve is opened by hydraulic or pneumatic pressure to operate the pressurized piston. Force the piston. When retracting, the piston rod closes and the check valve opens, Will prevent the pressure is first, to ensure that the injection operation both the second working chamber piston and the pressure piston by the wonbok and also to quickly forward / backward in the cylinder pressure increase as well as erroneous operation does not occur.

Description

Pressure Intensifying Cylinder

The present invention relates to a pressure-increasing cylinder, and more particularly to a pressure-increasing cylinder that improves the performance and output of pneumatic and hydraulic cylinders widely used in all industries.

Pneumatic cylinders and hydraulic cylinders have been used a lot for pressurization and transport, but nowadays is mostly used for pressurization due to the technology development of other transfer devices.

Pneumatic cylinders and hydraulic cylinders used for pressurization are mainly used for clamping mechanisms, compression mechanisms, and caulking mechanisms. Such clamping mechanisms and compression mechanisms do not require much operating force at the start of operation. In many cases, a large operating force is required. Therefore, the cylinder used for pressurization needs to exert a larger operating force in the vicinity of the extrusion end of the piston rod as compared with the starting position or the intermediate position.

Because of the necessity as described above, when determining the size of the cylinder, it was necessary to consider whether to obtain the required operating force near the extrusion end of the piston rod, it was inevitable to use a cylinder of a larger diameter and weight than necessary. However, when using a cylinder having a large diameter and weight as described above, the operation is relatively slow and the working efficiency is lowered, and a large amount of hydraulic oil is required, resulting in a loss of hydraulic oil as well as a high cost.

In order to solve this problem, the cylinder is configured to increase the operating force near the end of the piston rod by connecting a booster device to the pipeline for supplying hydraulic or pneumatic pressure to the cylinder to apply a higher pressure near the extrusion end position of the piston rod. It has been proposed. However, such a cylinder is not only complicated in structure, but also needs to use at least four solenoid valves, resulting in an increase in manufacturing cost.

In addition, the conventional cylinder had to have a complicated circuit, a variable pump and a control device as described above for the boosting function, the low output high speed and the high output low speed, and thus there was a problem that the price was high and the failure rate was high.

The present invention has been made to solve the problems of the conventional pressure-sensitive cylinder as described above,

A first object of the present invention is to provide a pressure-increasing cylinder with a simplified configuration having a large capacity and a high energy efficiency compared to its size.

It is a second object of the present invention to provide a boosting cylinder which is operated accurately and without malfunction by allowing quick and accurate boosting and retraction to be performed at the time of boosting and retracting.

The above object is a Pyrod which is opened or closed by a hydraulic vehicle or a pneumatic differential in the first and second operating chambers formed at the front and rear of the main body to drive the operation piston and the pressure piston in the booster cylinder operated by pneumatic or hydraulic type. By installing a valve and further installing a check valve in a second operation chamber formed at the rear to drive the pressure piston, during operation, the check valve and the pilot valve are kept closed to move only the operation piston when the load is low. During high load, the check valve is closed and the piston rod is opened by hydraulic or pneumatic pressure so that the pressurized piston exerts a force on the operating piston.In reverse, the piston rod is closed and the check valve is opened while hydraulic or pneumatic The cylinder is configured so that the working piston and the pressurized piston are restored by injecting them into the first and second working chambers. It is achieved by.

The pressure-increasing cylinder of the above configuration is implemented in the following embodiments, respectively in the hydraulic and pneumatic.

That is, the hydraulic pressure booster cylinder which concerns on 1st Embodiment of this invention,

A relatively small first forward / reverse operating chamber formed at the front of the main body and partitioned by an actuating piston projecting the push rod to the outside;

A second large forward / reverse operating chamber formed at a rear side of the main body and partitioned by a pressurizing piston for forming or releasing hydraulic pressure while the push rod moves forward and backward into the first forward operating chamber;

A forward hydraulic inlet formed at a rear of the main body and connected to the first forward operating chamber and the second forward operating chamber through a hydraulic passage formed inside the main body;

A first hydraulic inlet for reverse, formed in front of the main body and in communication with the first reverse operating chamber;

A second hydraulic inlet connected to the front end of the second reverse operation chamber;

A hydraulic outlet for connecting the front end face and the outer circumference of the second reverse operation chamber;

A bypass valve that penetrates the first forward operation chamber and the second reverse operation chamber and is configured to open and close the hydraulic outlet, and opens the hydraulic outlet only when the pressure piston is advanced by the hydraulic vehicle; And

And a check valve installed in the reverse hydraulic pressure inlet for allowing the hydraulic pressure to flow into the second reverse operating chamber during the reverse movement.

On the other hand, the pneumatic booster cylinder according to the second embodiment of the present invention,

A relatively small first forward / reverse operating chamber formed at the front of the main body and partitioned by an actuating piston projecting the push rod to the outside;

A front / rear operating chamber, which is partitioned by a piston, the front of which is connected to the first forward operation chamber to form hydraulic pressure, and the rear of which is formed of pneumatic pressure;

A relatively large second forward / reverse operating chamber formed at a rear of the main body and partitioned by a pressurizing piston for forming or releasing hydraulic pressure while the push rod installed through the piston is moved forward / backward into the first forward operating chamber; ;

A forward pneumatic inlet connected to the rear operation chamber and the second forward operation chamber through a pneumatic passage formed inside the main body;

A first pneumatic inlet for reversing formed in front of the main body and in communication with the first reversing operating chamber;

A second pneumatic inlet connected to the front end of the second reverse operation chamber, and a pneumatic discharge port connecting the front end surface and the outer circumference of the second reverse operation chamber;

A bypass valve which penetrates the rear operation chamber and the second reverse operation chamber and opens and closes the pneumatic outlet so as to open the pneumatic outlet only when the pressure piston is moved forward by a pneumatic differential; And

And a check valve installed in the reverse second pneumatic inlet to allow pneumatic pressure to flow into the second reverse operating chamber during the reverse.

Hereinafter, with reference to the accompanying drawings will be described a preferred embodiment of the present invention.

1 to 5 are diagrams showing a hydraulic booster cylinder according to an embodiment of the present invention, with reference to these drawings will be described a hydraulic booster cylinder according to the present embodiment.

In the drawings, Figure 1 is a longitudinal cross-sectional view showing the configuration of the hydraulic booster cylinder according to an embodiment of the present invention, Figure 2 is a cross-sectional view showing a closed state of the pilot valve constituting the hydraulic booster cylinder, 3 is a longitudinal sectional view showing a forward operation at low load of the hydraulic booster cylinder, Figure 4 is a longitudinal sectional view showing a forward operation at high load of the hydraulic booster cylinder, Figure 5 is a cross-sectional view showing an open state of the pilot rod valve. .

The hydraulic pressure-increasing cylinder according to this embodiment is formed in front of the main body 10 as shown in Figs. 1 and 2, and the diameter of the push rod 21 is partitioned by the working piston 20 protruding outward. The small first forward / reverse operating chambers 22 and 24; A relatively large diameter is formed at the rear of the main body 10 and is partitioned by a pressure piston 30 that forms or releases hydraulic pressure while the push rod 31 moves forward and backward into the first forward operation chamber 22. A second forward / reverse operating chamber (32) (34); A forward hydraulic inlet formed at the rear of the main body 10 and connected to the first forward operation chamber 22 and the second forward operation chamber 32 through a hydraulic passage 42 formed inside the main body 10. 40; A first hydraulic inlet 52 for reversing formed in front of the main body 10 and in communication with the first reverse operating chamber 24; A second hydraulic pressure inlet 54 for reversing connected to a distal end of the second reverse operation chamber 34; A hydraulic outlet 56 connecting the front end surface and the outer circumference of the second reverse operation chamber 34; In order to penetrate the first forward operation chamber 22 and the second reverse operation chamber 34 and to open and close the hydraulic outlet 56, when the pressure piston 30 is advanced by a hydraulic vehicle. A quick rod valve 60 to open the hydraulic outlet 56 only; And a check valve 70 installed in the reverse hydraulic pressure inlet 54 to allow the hydraulic pressure to flow into the second reverse operation chamber 34 at the time of reverse movement.

On the other hand, in the above configuration, the first hydraulic inlet 52 for the reverse, the second hydraulic inlet 54 for the reverse and the hydraulic outlet 56 are all connected to the reverse hydraulic tank (not shown), and the first hydraulic oil for the reverse Check valves 57 and 58 are further installed at the inlet 52 and the hydraulic outlet 56 to control the flow of hydraulic pressure.

In addition, the quick rod valve 60 and its installation structure will be described in more detail with reference to FIG. 2, wherein the hydraulic outlet 56 has a '┏' type so as to connect the second reverse operation chamber 34 to the outside. And an operating groove 65 formed concentrically with the end of the second reverse operation chamber 34 side of the hydraulic outlet 56. The operating groove 65 is connected to the first hydraulic inlet 52 for reverse through the hydraulic passage 64 formed at the rear end, and the front end thereof is opened toward the first forward operation chamber 22. On the other hand, the bypass rod 60 is installed through the operating groove 65 and the hydraulic outlet port 56, the packing 67 is interposed in the main body 10 to maintain the airtight, the bypass rod 60 The valve piston 66 is provided with a packing 68 at its outer circumference to form a reciprocating motion in the working groove 65 at the distal end thereof, and at the rear end thereof, the hydraulic outlet 56 at the second reverse operation chamber 34 side ends. The close contact portion 62 is formed to open and close the door.

Therefore, when the operating piston 20 moves forward and the hydraulic pressure inside the first forward operating chamber 22 becomes larger than the internal hydraulic pressure of the second reverse operating chamber 34, the pilot valve 60 is operated by the hydraulic vehicle. While retracting, the close contact portion 62 is spaced apart from the hydraulic outlet 56 so that the hydraulic pressure in the second reverse operation chamber 34 is discharged through the hydraulic outlet 56, and conversely, when the working piston 20 is reversed, Hydraulic pressure injected into the working groove 65 through the first hydraulic inlet 52 and the hydraulic passage 64 for the reverse, and the hydraulic vehicle in the first forward operating chamber 22 and the second reverse operating chamber 34. By the forward rod valve 60 is advanced, the hydraulic pressure in the second reverse operation chamber 34 is prevented from being discharged to the outside.

In addition, when the configuration of the check valve 70 in more detail with reference to Figure 1, while forming the insertion groove (74) for inserting the ball 72 in the second hydraulic inlet 54 for the reverse, the ball 72 ) Is made larger than the diameter of the reverse second hydraulic inlet 54, so that the ball 72 can open and close the reverse second hydraulic inlet 54. On the other hand, between the insertion groove 74 and the second reverse operating chamber 34 is installed a spring 76 fixed to the end of the second reverse operating chamber 34 side by the second hydraulic inlet ( 54, the ball 72 is pushed to the pressure and spaced apart from the second hydraulic inlet 54 for the reverse so that the hydraulic pressure is injected into the second reverse operating chamber 34, if there is no hydraulic supply Due to the elasticity of the spring 76, the ball 72 comes into close contact with the end of the second hydraulic inlet 54 for the reverse movement, so that the hydraulic pressure in the second operating chamber 34 for the second reverse hydraulic pressure is passed through the second hydraulic inlet 54 for the reverse movement. To prevent leakage.

In the drawing, reference numeral 12 denotes a sealing ring.

The operation of the hydraulic booster cylinder according to the present invention configured as described above will be described below.

First, as shown in FIG. 1 and FIG. 2, the hydraulic oil passing through the forward hydraulic inlet 40 formed at the rear of the main body 10 in the state in which both the pressurized piston 30 and the working piston 20 are retracted is primarily Acting on the pressurized piston 30 and subsequently acting on the first forward operation chamber 22 of the actuating piston 20 through the hydraulic passage 42 to advance the actuating piston 20.

In this case, the second reverse operation chamber 34 is blocked by the check valve 70 and the quick rod valve 60 so that hydraulic oil injected into the second forward operation chamber 32 is applied to the pressure piston 30. Even if it acts, the pressurized piston 30 does not move forward, but is constrained. This is because the hydraulic oil of the second reverse operation chamber 34 acts on the close contact portion 62 of the quick rod valve 60 as shown in FIG. 62 is in close contact with the inner circumference of the second reverse operation chamber 34, and the hydraulic oil of the second reverse operation chamber 34 and the elastic force of the spring 76 constitute the check valve 70. Since the ball 72 blocks the second hydraulic inlet 54 for the reverse movement, the hydraulic oil movement of the second reverse operation chamber 34 is blocked, and thus the pressure piston 30 is prevented from moving forward. to be.

When the operation piston 20 moves forward by a predetermined distance as described above, and fails to move forward by the high load as shown in FIG. 3, the operation piston 22 of the first forward operation chamber 22 in which the operation piston 20 is installed is provided. The hydraulic oil pressure rises to reach the maximum. When the maximum pressure of the hydraulic oil in the first forward operation chamber 22 acts on the valve piston 66 having a relatively large area as compared with the close contact portion 62, the pressure is greater than the force applied to the close contact portion 62. As the piston 66 retracts as shown in FIGS. 3 to 5, the close contact portion 62 and the hydraulic outlet 56 of the second reverse operation chamber 34 are separated, and accordingly, the second reverse operation chamber 34 is provided. Of the hydraulic oil is discharged to the first hydraulic inlet 52 for the reverse through the hydraulic outlet (56).

Accordingly, since the pressurized piston 30 is advanced as shown in FIG. 4 in the state of FIG. 3, the push rod 31 of the pressurized piston 30 passes through the sealing ring 12 and the hydraulic oil of the first advance operating chamber 22. At this time, the total pressure of the hydraulic oil acting on the large cross section of the second forward operation chamber 32 is concentrated on the end surface of the push rod 31 of the operating piston 20 of the relatively small cross section, and the concentrated force By the principle of this Pascal, it acts on the whole area of the 1st forward operation chamber 22, and the operation piston 20 advances with a big force.

In addition, when the hydraulic piston is injected into the first and second hydraulic inlets 52 and 54 for reversing, the operating piston 20 and the pressurized piston 30 operate in the first reverse operation chamber 24. A force for reversing 20 acts, and at the same time, the pressure of the internal hydraulic oil in the first forward working chamber 22 rises, acting on the end surface of the push rod 31 of the pressure piston 30, and at the same time, The hydraulic oil passing through the passage 64 reaches the pilot rod 60, and the hydraulic oil injected into the reverse second hydraulic inlet 54 is transferred to the second reverse operation chamber 34 through the check valve 70. It acts and is made by backing the pressurized piston 30.

6 to 10 are diagrams showing a pneumatic booster cylinder according to another embodiment of the present invention, with reference to these drawings will be described the pneumatic booster cylinder according to the present embodiment.

In the drawings, Figure 6 is a longitudinal sectional view showing the overall configuration of the pneumatic booster cylinder according to the present embodiment, Figure 7 is a longitudinal sectional view showing the forward operation at low load of the pneumatic booster cylinder, Figure 8 is a pneumatic type Fig. 9 is a sectional view showing the forward operation of the booster cylinder at high load, and Fig. 9 is a sectional view showing a closed state of the exhaust check valve constituting the pneumatic booster cylinder, and Fig. 10 is a sectional view showing an open state of the exhaust check valve. .

6 to 8, the pneumatic booster cylinder according to the present embodiment is formed in front of the main body 10 'and is partitioned by the actuating piston 20' protruding to the outside. First forward / reverse operating chambers 22 'and 24' having a relatively small diameter; Front / rear operating chambers 82 'and 84' which are partitioned by a piston 80 ', the front of which is connected to the first forward operating chamber 22' to form hydraulic pressure, and the rear of which is formed of pneumatic pressure; A pressurized piston formed at the rear of the main body 10` and configured to release or release hydraulic pressure while the push rod 31` installed through the piston 80` moves forward and backward into the first forward operation chamber 22`. Second large forward / reverse operating chambers 32 'and 34', each of which is divided into 30 '; A forward pneumatic inlet 40 'connected to the rear operation chamber 84' and the second forward operation chamber 32 'through a pneumatic passage 42' formed inside the main body 10 '; A reverse first pneumatic inlet 52 'formed in front of the main body 10' and in communication with the first reverse operating chamber 24 '; A second pneumatic inlet port 54` connected to the front end of the second reverse operation chamber 34`; A pneumatic discharge port 56` for connecting the front end surface and the outer circumference of the second reverse operation chamber 34`; It is installed to penetrate the rear operation chamber 84 'and the second reverse operation chamber 34' and open and close the pneumatic discharge port 56` to move the pressure piston 30 'by the pneumatic differential. A bypass valve (60`) which opens the pneumatic discharge port (56`) only at a time; And a check valve 70 'installed in the reverse second pneumatic inlet 54' to allow air pressure to flow into the second reverse operating chamber 34 'at the time of reverse movement.

On the other hand, in the above-described configuration, both the reverse first pneumatic inlet 52`, the reverse second pneumatic inlet 54` and the pneumatic outlet 56` are connected to the reverse pneumatic tank (not shown), Check valves 57 'and 58' are further provided at the first pneumatic inlet 52 'and the pneumatic outlet 56' to control the flow of pneumatic pressure.

In addition, referring to the quick rod valve 60` and its installation structure, the pneumatic discharge port 56` is formed in a '┏' type to connect the second reverse operation chamber 34` to the outside, and the pneumatic pressure An operating groove 65 'is formed concentrically with the end of the second reverse operating chamber 34` side of the discharge port 56`. The operation groove 65 'is connected to the first pneumatic inlet 52' for reversal through a pneumatic passage 64 'formed at the rear end thereof, and the front end thereof is opened toward the rear operation chamber 82'. On the other hand, the quick rod valve (60`) is provided with a packing (67`) is interposed in the main body (10`) so that airtightness is maintained while passing through both the operation groove (65`) and the pneumatic discharge port (56`) The valve piston 66` is provided at the distal end of the pilot rod 60` with a packing 68` installed at its outer circumference so as to reciprocate in the operating groove 65`, and at the rear end thereof, a second reverse operation chamber ( A close contact portion 62` formed to open and close the end of the 34`) side pneumatic discharge port 56` is formed.

Therefore, when the operating piston 20 'advances and the air pressure inside the rear operating chamber 82' becomes larger than the air pressure inside the second reverse operating chamber 34 ', the close contact portion 62' is retracted by the pneumatic difference. ) Is spaced apart from the pneumatic outlet (56`) so that the air pressure in the second reverse operation chamber (34`) is discharged through the pneumatic outlet (56`), on the contrary, when the working piston (20`) reverses, Pneumatic and rear operating chamber 22` and second reversing operating chamber 34` which are injected into working groove 65` through pneumatic inlet 52` and pneumatic passage 64` By this, since the pilot rod 60 'is advanced, the air pressure inside the second reverse operation chamber 34' is prevented from being discharged to the outside.

In addition, looking at the configuration of the check valve (70`), the insertion groove (74`) for inserting the ball 72` into the second pneumatic inlet port (54) for the reverse, but the diameter of the ball (72`) The diameter of the reverse second pneumatic inlet 54 'is made larger so that the ball 72' can open and close the reverse second pneumatic inlet 54 '. On the other hand, between the insertion groove 74` and the second reverse operating chamber 34`, a spring 76` with a fixed end of the second reverse operating chamber 34` is installed, so that the pneumatic pressure is reversed. When injected into the second pneumatic inlet 54 ′, the ball 72 ′ is pushed to the pressure so as to be spaced apart from the second pneumatic inlet 54 ′ so that the pneumatic pressure is injected into the second reverse operating chamber 34 ′. If there is no pneumatic supply, the ball 72 'is brought into close contact with the end portion of the second pneumatic inlet port 54` by the elasticity of the spring 76', so that the inside of the second reverse operating chamber 34 ' The pneumatic pressure is prevented from leaking through the reverse second pneumatic inlet 54 '.

In addition, an exhaust passage 26 ′ is formed in the operation piston 20 ′ to connect the first operation chamber 24 ′ to the outside, so that the pneumatic pressure of the first operation chamber 24 ′ is increased. To prevent flow into the operating chamber 22`.

In addition, an exhaust check valve 90 'for exhausting air bubbles in the hydraulic oil of the first forward operation chamber 22' and the front operation chamber 82 'is provided. As shown in Figs. 9 to 10, the exhaust check valve 90 'includes an installation groove 92' that is open toward the rear operation chamber 84 ', a center of the installation groove 92' and a front operation chamber. Exhaust hole 94` of fine size connecting 82 ', valve piston 95`, spring 96`, and spring seat 97`, which are sequentially inserted into the installation groove 92`, are installed. It consists of.

With the above configuration, when the operation piston 20 'is advanced, the valve piston 95' of the exhaust check valve 90 'is turned to pneumatic pressure in the rear operation chamber 84' as shown in FIG. When the operating piston 20 'is retracted or the internal pressure of the first forward operation chamber 22` rises due to bubble generation, the spring 96` is held as shown in FIG. The inner circumferential surface of the installation groove 92` and the valve piston 95` are opened to push the bubbles of the front operation chamber 82` to the rear operation chamber 84`, the pneumatic passage 42`, and the pneumatic inlet for forwarding. To 40 '.

In the drawings, reference numeral 12 ′ denotes a sealing ring.

The operation of the pneumatic booster cylinder according to the present invention configured as described above will be described below.

First, as shown in FIG. 6, the advance pneumatic inlet 40 'formed behind the main body 10' in the state which both the pressurized piston 30 ', the working piston 20', and the piston 80 'have retracted. When pneumatic flows through, the pneumatic pressure primarily acts on the pressurized piston 30 ', and then acts on the rear working chamber 84' of the piston 80 'via the pneumatic passage 42' to form a piston ( 80 '), and the piston 80' acts on the first forward operating chamber 12 'to advance the working piston 10'.

At this time, the close contact portion 62 'of the fast rod valve 60' is in close contact with the pneumatic discharge port 56 'on the side of the second reverse operation chamber 34', and the ball 72 'of the check valve 70' is closed. Since the reverse second pneumatic inlet port 54 'is blocked, all of the air discharge passages of the second reverse operation chamber 34' are blocked so that the pneumatic pressure injected into the second forward operation chamber 32 'is pressurized. Even when acting on 30 ', the pressurized piston 30' cannot be moved forward and is constrained.

Then, as described above, when the operating piston 20 'is advanced by a certain distance by the piston 80`, and it cannot be moved by the high load as shown in FIG. 7, the first advance operating chamber 22' ) And the hydraulic oil in the front operating chamber 82` stops the advancement of the piston 80`. Accordingly, if the pneumatic pressure of the rear operating chamber 84 'is increased and the maximum pneumatic pressure of the rear operating chamber 84' acts on the valve piston 66 'having a relatively large area as compared with the close contact portion 62'. Since the valve piston 66` retreats, the pneumatic outlet 56` of the second contacting chamber 62` and the second reverse operating chamber 34` are separated from each other, because the piston piston 66` retreats. Accordingly, the pneumatic pressure of the second reverse operation chamber 34 ′ is discharged to the first pneumatic inlet 52 ′ for the reverse through the pneumatic discharge port 56 ′.

Accordingly, since the pressurized piston 30 'is advanced as shown in FIG. 8 in the state of FIG. 7, the push rod 31' of the pressurized piston 30 'passes through the sealing ring 12' and moves the operating piston 20 '. In this case, the force of pneumatic force acting on the large cross section of the second forward operation chamber 32 'into which the pressure piston 30' is fitted is concentrated on the cross section of the relatively small push rod 31 ', and this concentrated force By this Pascal principle, the working piston 20 'advances with great force by acting on the entire area of the hydraulic oil located in the first forward working chamber 22' of the working piston 20 '.

The forward movement of the actuating piston 20 'acts on the actuating piston 20' more than the force of the internal hydraulic oil of the first actuating chamber 22 'and the front actuating chamber 82'. Or stop when the piston 80` moves forward.

On the other hand, the reverse operation of the operating piston (20 ') and the pressurized piston (30') is, when the pneumatic pressure is injected into the first and second pneumatic inlet (52 ', 54') for the reverse, The force for retracting the actuating piston 20 'acts at 24', and at the same time, the hydraulic oil pressure inside the first forward actuating chamber 22 'rises, causing the push rod 31' of the pressurized piston 30 'to rise. In addition to acting on the end face, it acts on the rear operation chamber (84`), and the pneumatic pressure passing through the pneumatic passage (64`) reaches the operating groove (65`) of the pilot rod (60`) and the pneumatic outlet (56 `), And the pneumatic pressure injected into the reverse second pneumatic inlet 54` acts on the second reverse operation chamber 34 through the check valve 70`, thereby reversing the pressure piston 30. Is done.

Therefore, the operation piston 20 'and the pressure piston 30' reach the maximum reversal point and wait for the next operation.

On the other hand, the cross section of the pressurized piston 30 'on the side of the second reverse operating chamber 34' at the time of advancing the operating piston 20 'in the state of low load in the above-described configuration is the first forward operating chamber 32'. There is a concern that the push rod 31` is moved forward by the pneumatic compressibility because it is smaller than the cross section of the side pressurized piston 30`, and the reaction force at the end of the push rod 31` positioned in the first forward operation chamber 22` is increased. Resolved.

According to the present invention configured as described above, not only can the large force be exerted by the small diameter cylinder, but also the diameter of the cylinder is small, the filling amount of pneumatic and hydraulic pressure is small, the filling time is fast, and the productivity and operating efficiency are improved. There is.

Furthermore, since the pilot rod valve is automatically opened and closed according to the low load and high load, that is, the boosting pressure is automatically switched and the pneumatic and hydraulic pressure of the second reverse operation chamber are controlled so that the switching according to the load is precisely controlled. It is possible to change the operation, thereby preventing the malfunction of the cylinder.

1 is a vertical cross-sectional view showing the configuration of a hydraulic pressure-increase cylinder according to an embodiment of the present invention,

2 is a cross-sectional view showing a closed state of a bypass valve constituting the hydraulic booster cylinder;

Figure 3 is a longitudinal sectional view showing the forward operation at low load of the hydraulic booster cylinder,

4 is a longitudinal sectional view showing a forward operation at high load of the hydraulic booster cylinder;

5 is a cross-sectional view showing an open state of the quick rod valve;

6 is a longitudinal sectional view showing a configuration of a pneumatic booster cylinder according to another embodiment of the present invention;

7 is a longitudinal sectional view showing a forward operation at low load of the pneumatic booster cylinder;

8 is a longitudinal sectional view showing a forward operation at high load of the pneumatic booster cylinder;

9 is a longitudinal sectional view showing a closed state of a check valve constituting the pneumatic booster cylinder;

10 is a longitudinal sectional view showing an open state of the check valve.

* Description of the symbols for the main parts of the drawings *

10, 10`: main body 20, 20`: working piston

21, 21`: push rod 22, 24, 22`, 24`: operating chamber for 1st forward / reverse

30, 30`: Pressurized piston 31, 31`: Push rod

32, 34, 32`, 34`: 2nd operating room for forward / reverse

40, 40`: Hydraulic inlet 42, 42`: Hydraulic passage

52, 52`: 1st hydraulic inlet for reverse direction 54, 54`: 2nd hydraulic inlet for reverse direction

56, 56`: Hydraulic outlet 60, 60`: By-rod valve

70, 70`: check valve 80, 80`: piston

82`, 84`: front / rear operating chamber 90`: check valve for exhaust

Claims (6)

A first small forward / reverse operating chamber (22) (24) formed in front of the main body (10) and partitioned by a working piston (20) in which the push rod (21) protrudes outward; A relatively large diameter is formed at the rear of the main body 10 and is partitioned by a pressure piston 30 that forms or releases hydraulic pressure while the push rod 31 moves forward and backward into the first forward operation chamber 22. A second forward / reverse operating chamber (32) (34); A forward hydraulic inlet formed at the rear of the main body 10 and connected to the first forward operation chamber 22 and the second forward operation chamber 32 through a hydraulic passage 42 formed inside the main body 10. 40; A first hydraulic inlet 52 for reversing formed in front of the main body 10 and in communication with the first reverse operating chamber 24; A second hydraulic pressure inlet 54 for reversing connected to a distal end of the second reverse operation chamber 34; A hydraulic outlet 56 connecting the front end surface and the outer circumference of the second reverse operation chamber 34; In order to penetrate the first forward operation chamber 22 and the second reverse operation chamber 34 and to open and close the hydraulic outlet 56, when the pressure piston 30 is advanced by a hydraulic vehicle. A quick rod valve 60 for opening the hydraulic outlet 56 only; And And a check valve (70) installed in the reverse hydraulic pressure inlet (54) to allow the hydraulic pressure to flow into the second reverse operation chamber (34) during the reverse movement. According to claim 1, wherein the rod rod valve 60 is a close contact portion 62 receives the hydraulic pressure of the second operation chamber 34 for opening and closing the hydraulic outlet 56, and the first hydraulic inlet for the reverse ( 52 is provided with a valve piston 66 installed in an operation groove 65 connected rearward through the hydraulic passage 64 and open toward the first forward operation chamber 22 to operate the first forward operation. A hydraulic booster cylinder, characterized in that the hydraulic outlet (56) is opened and closed while being forward / reversed by the hydraulic vehicle in the chamber (22), the second reverse operation chamber (34), and the operation groove (65). A relatively small first forward / reverse operating chamber 22 '(24') formed in front of the main body 10 'and partitioned by an actuating piston 20' protruding outwardly. `) And; Front / rear operating chambers 82 'and 84' which are partitioned by a piston 80 ', the front of which is connected to the first forward operating chamber 22' to form hydraulic pressure, and the rear of which is formed of pneumatic pressure; A pressurized piston formed at the rear of the main body 10` and configured to release or release hydraulic pressure while the push rod 31` installed through the piston 80` moves forward and backward into the first forward operation chamber 22`. Second large forward / reverse operating chambers 32 'and 34', each of which is divided into 30 '; A forward pneumatic inlet 40 'connected to the rear operation chamber 84' and the second forward operation chamber 32 'through a pneumatic passage 42' formed inside the main body 10 '; A reverse first pneumatic inlet 52 'formed in front of the main body 10' and in communication with the first reverse operating chamber 24 '; A second pneumatic inlet port 54` connected to the front end of the second reverse operation chamber 34`, and a pneumatic exhaust port connecting the front end surface and the outer circumference of the second reverse operation chamber 34` ( 56`); It is installed to penetrate the rear operation chamber 84 'and the second reverse operation chamber 34' and open and close the pneumatic discharge port 56` to move the pressure piston 30 'by the pneumatic differential. A bypass valve 60 'that opens the pneumatic discharge port 56` only at the time; And And a check valve (70`) installed in said reverse second pneumatic inlet (54 ') to allow air pressure to flow into said second reverse operation chamber (34`) at the time of reverse movement. 4. The hydraulic rod (64) according to claim 3, wherein the bypass rod (60 ') is connected to the contact portion (62) which receives the pneumatic pressure from the second operating chamber (34) and the first pneumatic inlet port (52) for the reverse direction. Rear piston connected to the rear side and having a valve piston 66 'installed in the operating groove 65` which is open toward the rear operating chamber 84`. A pneumatic booster cylinder characterized by opening and closing the pneumatic discharge port 56` while moving forward and backward by the pneumatic differential in the operating chamber 34` and the working groove 65`. 4. The pneumatic booster cylinder according to claim 3, wherein the actuating piston (20 ') is provided with an exhaust passage (26') connecting the first reverse operating chamber (24 ') to the outside. 4. The exhaust check valve (90 ') according to claim 3, wherein the piston (80`) has an air bubble in the hydraulic oil of the first forward operating chamber (22`) and the front operating chamber (82`). Is installed; The exhaust check valve 90` is a minute size connecting the installation groove 92` opened to the rear operation chamber 84` and the center of the installation groove 92` and the front operation chamber 82`. Pneumatic pressure boost, characterized in that it has an exhaust hole 94`, and a valve piston 95`, a spring 96` and a spring seat 97` which are sequentially inserted into the installation groove 92`. cylinder.