KR950007623B1 - Fluid pressure intensifier - Google Patents

Abstract

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Description

Fluid Pressure Intensifier

1 is a front view showing a partial cross section of the right half of the pressure intensifier according to the present invention.

FIG. 2 is an enlarged front view of a portion of the intensifier of FIG. 1 as a partial section.

3 is another partial front view of the present invention showing a preferred shock valve assembly.

4 is an enlarged cross-sectional view of the preferred shock valve assembly depicted in FIG.

FIG. 5 is a sectional view similar to FIG. 4 showing a preferred shock valve assembly. FIG.

* Explanation of symbols for main parts of the drawings

10 housing 24 valve body

26: low pressure piston 28,30: high pressure piston

The present invention relates to a fluid pressure intensifier system.

More particularly, it relates to a double acting hydraulic pressure intensifier.

In a typical high pressure fluid intensifier system, the fluid pressure acts in a reciprocating dual operation, ie low pressure and high pressure piston assembly, to compress the water to thousands of psi.

The piston assembly of such a system is exposed to a fluid pressure of 3,000 psi and a water pressure of 20 to 6,000 psi. These assemblies must be designed to withstand significant pressure while isolating pressure fluids / water.

The pressure chamber in which such a piston in the assembly operates and the various pressure seals are very severely stressed. Pressure chambers are often made of members that are held together with screws or bolts to withstand circulating pressure rises and falls. Periodic replacement of the high pressure seal is very difficult due to the attachment of the various components that make up the pressure chamber of the intensifier and the piston assembly. Usually the intensifier must be completely disassembled to repair or replace the internal parts.

The pressure intensifier of the present invention includes an assembly having a central low pressure chamber positioned at both sides by a high pressure chamber installed in a low pressure chamber in an axial line, a low sump and a high pressure piston held in the pressure chamber, and an pressure chamber arranged in an axial direction. And a suction / discharge valve mounting end retainer screwed to each end of the housing for securing and positioning the inner member which makes the pressure chamber in position, and the suction / discharge mounted by the end retainer in fluid communication with the high pressure chamber. It includes a valve body.

Another aspect of the invention is to provide a low pressure fluid control valve actuator.

The actuator has a piston assembly connected to an external limit switch and in fluid communication with the low pressure chamber. Two such actuators are provided for operating the low pressure fluid control valve on one of each axis of the low pressure chamber. The piston assembly of each actuator extends to one end of the low pressure chamber and is moved by the low pressure piston to effectively operate the external limit switch and change the flow direction of the low pressure fluid.

As a result, the low pressure piston is brought out of contact with the actuator piston so that the low pressure fluid acts on the piston and extends back into the low pressure chamber and out of contact with the external limit switch. As the low pressure piston moves to the opposite side of the low pressure chamber, the process is duplicated for other low pressure fluid control valve actuators. These actuators are installed by cylinder blocks that form adjacent end boundaries of the low pressure chamber and the high pressure chamber. The actuator can be accessed through the housing incision.

The pressure intensifier of the present invention uses fluid (oil) to drive the high pressure and low pressure piston assemblies to obtain the high pressure water fluid. The intensifier shown in FIG. 1 has a dual operation. It comprises a housing 10 in the form of an elongated steel cylinder.

The right half is shown in FIG.

The left half is the same as the right side. An end retainer ring 12 is mounted at the housing and at each end and the end of the housing has a thread therein to engage an external thread on the end retainer ring 12 as shown.

In the housing 10 a low pressure chamber 14 is formed by an iron cylinder 16 fitted into a cylindrical end cap 18 at each end (the right cap is shown and the left cap is the same as the right).

In the housing 10, the left and right high pressure chambers (the right high pressure chamber 20 is shown and the left high pressure chamber is the same) have an inner end portion at the end cap 18 and an outer end portion of the suction / exhaust valve. It is formed by an extension steel barrel cylinder 22 fitted to the valve body 24 of the assembly.

The sleeve and ring bearings 26, 28 coincide with the outer ends of the barrel cylinders 22 in the end retainers 12. The outer surface of the end cap 18 coincides with the inner surface of the housing cylinder 10 with a slight margin for slipping clearance. Tightening the end retainer 12 compresses the pressure chamber member in the longitudinal axis direction and tensions the housing 10 in the longitudinal axis direction.

Once one or both of the end retainers 12 are removed, these members are removed from the housing very quickly. The low and high pressure cylinders 16, 20 are mounted axially parallel to the housing cylinder 10 by means of end caps 18 and retainer rings 12.

Due to the relative dimensions of the members described so far, the pressure chamber member is limited to any transverse or longitudinal axis movement. The low pressure and high pressure piston assembly includes a low pressure piston 26 and a left-right high pressure piston 28, 30.

The low pressure piston is a cylindrical disk in the low pressure chamber 14.

The outer circumferential surface of the lower pressure cylinder 16 is fitted with an appropriate fluid pressure sealing part 32 so as to seal one side of the low pressure chamber 14 with each other while having a margin for slipping clearance. The high pressure piston is connected to the opposite side of the low pressure piston 26 and extends through the respective end caps 18 to the high pressure chamber sleeve 20.

Each high pressure piston has an elongated cylindrical rod 30a having a diameter slightly smaller than the inner diameter of the sleeve 20, and at its inner end to provide a cylindrical flange 30b having a diameter larger than that rod. It is a single part machined to

The high pressure piston flange 30b is fitted in a cylindrical counter bore 34 machined in each surface of the low pressure piston 26. The flange 30b is held in place by the retainer ring 34, which is held in a groove machined in the counter bore.

The cylindrical passage in the end cap 18 extends through the high pressure piston rod 30a and has a diameter slightly larger than the piston rod diameter. The high pressure side of the end cap 18 goes inward and the diameter thereof becomes smaller, i.e., the outermost end is the high pressure cylinder 20, the middle part is the cylindrical piston rod middle ring 38, and the innermost end is the appropriate high pressure static ( static) is machined to fit the seal 40.

The intermediate ring 38 is machined to provide an intermediate portion that matches the diameter of the middle end of the counterbore 18a and an internal extension that matches the diameter of the inner end of the counterbore 18a. The inner extension of the intermediate ring 38 holds the fluid seal 40 in place and fits against it. The intermediate ring 38 also has an outer extension that extends outward above the middle of the counter bore 18a and coincides with the inner diameter of the high pressure cylinder 22.

The high pressure cylinder 20 abuts against the outermost end of the counter bore 18a by load bearing contact, and makes contact with the external extension of the intermediate ring 38 to hold it in position. The reactive fluid force of the fluid actuation in the low pressure chamber 14 is transmitted through the end cap 18 and the high pressure cylinder 20 to the internal threads of the end retainer 12 and the housing cylinder 10.

The intermediate ring 38 is made of a nonferrous metal such as beryllium copper or aluminum nickel bronze alloy. It is used not only as a retainer for the fluid seal 40 but also as a bushing for the high pressure piston rod 30a.

In addition, the high-pressure piston rod (30a) and the high-pressure cylinder 20 also serves to keep the shaft center coincident. In addition, it is also used as a metal protector for the high pressure dynamic sealing assembly 42.

The opposite end of the high pressure cylinder 20 is fitted over a stub protruding from the valve body 24. The valve body 24 is machined to provide a cylindrical stub 24a. The end of the stub is machined to provide a smaller cylindrical end face as a sheet for the high pressure dynamic seal assembly 44. The stepped transition between the high pressure cylinder mounting stub and the high pressure seal sheet provides a metal protector for the seal assembly 44. The end diameter of the stub 24a corresponds to the diameter of the high pressure piston rod 30a as shown.

The high pressure piston rod 30a is in the inner sleeve 20 of the cylinder 20 by a dashed line adjacent to the seal assembly 42 depicting the position shown and the maximum contraction of the end of the piston rod 30. Shuttle between the indicated positions. The seal assemblies 42 and 44 are maintained to accumulate high pressure in the cylinder 20 as the piston rod 30a reciprocates back and forth.

The seal assembly 42 contacts the intermediate ring 38 and the Delrin dynamic auxiliary seal 42a in contact with the polyurethane lip seal 42b. The seal assembly 44 consists of the same commercialized lip seal that contacts the delrin ring and subsequently contacts the nonferrous metal auxiliary ring.

As the high pressure piston rod 30a is retracted from the position shown, the low pressure water is transferred to the high pressure chamber 20 through the suction 첵 valve 48 provided by the valve body 24 with the passage 50 to the valve body opening 52. Is induced.

When the piston rod 30a returns to the position shown again, the intake 첵 valve 48 is closed, the water is compressed to high pressure, and is opened by the valve body opening 52, the discharge passage 54, and the valve body 24. It is forcibly discharged through a discharge check valve 56 installed.

The reciprocating motion of the high pressure piston becomes effective as the fluid is pumped into the low pressure chamber 14 on one side or the other side of the low pressure piston 26. Each end cap 18 is ported at 60 to the low pressure chamber 14 and to provide fluid flow. The suction tube 62 is screwed into the port 60 to connect to the fluid flow supply.

When the fluid is pumped through the port 60 to the low pressure chamber 14, the low pressure piston is moved to the left in the position shown, thereby contracting the right high pressure piston rod 30a and the left high pressure piston rod 28a. Is extended. At the same time, the fluid is discharged through the fluid port in the left cylinder block and the water in the left high pressure chamber is compressed and discharged through the left valve body. When the low pressure piston 26 reaches the left end of the low pressure chamber 14, the fluid flow is reversed and the low pressure piston 26 moves to the right. The fluid flows through the right cylinder block, and the water in the high pressure chamber 20 is compressed and discharged through the valve body 24.

As the low pressure piston 26 reciprocates, fluid accumulates between the high pressure piston flange 30b and the low pressure piston counterbore 34. In order to prevent unwanted pressure build up behind the flange 30b, the bearer of the counterbore 34 flows on the opposite side of the low pressure piston 26 through the vent passage 64 and the check valve 66.

The high pressure piston flange 28b and its counter counterbore 34 flow equally through the vent passage 68 and the check valve 70. By this arrangement, a relatively loose fit exists between the high pressure piston flange and its respective counter bore sheet and the high pressure piston is easily supported by their respective counter bore sheet snap ring 36.

A limit switch 74 for the fluid control valve is installed at each adjacent end cap 18. The signal state of each switch is validated by reciprocating movement of the actuator piston assembly slidably mounted in the adjacent end cap 18 as shown. It can be seen that a solenoid operated four-way control valve is provided to control the fluid flow from and to the low pressure chamber 14.

Each limit switch 74 actuates either of the two control valve solenoids.

Referring to the right half, the right side movement of the actuator moving pin 72 to the outside of the end cap 18 is made by mechanical contact with the low pressure piston 26. In addition, the left side movement of the moving pin 72 to the inner side of the end cap 18 is made by the fluid from the low pressure chamber 14. When the low pressure piston 26 moves to the left in the position shown, the fluid enters the chamber 70 and presses the moving pin 72 to the left to change the signal state of the limit switch 74.

The chamber 70 is formed between the moving pin 72, the sealing ring 73 and the cylindrical passageway in the end cap 18. This passage has an outer portion of larger diameter than its inner portion, and the stepped surface 86 formed therebetween serves as a stop for limiting the left movement of the moving pin 72. The moving pin 72 includes a cylindrical member machined in the shape of a passageway and has a smaller diameter inner end portion and a stepped surface 78 therebetween to connect with the face 76 to limit the left movement of the pin. Has a large diameter middle part with

The moving pin 72 extends through the sealing ring 73 toward the limit switch 74 and has a smaller diameter outer end, which is fitted with a limit switch actuating plunger 77.

The moving pin 72 includes an axial passage 80 extending from its inner end and interconnecting a radial passage 82 which provides fluid communication between the low pressure chamber 14 and the chamber 70. The stepped surface 84 between the middle portion and the outer portion of the smaller diameter moving pin 72 forms a piston surface 84. The diameter of the outer pin portion is sufficiently reduced such that the area of the piston face 84 is larger than the area of the inner pin end 86.

When the piston 26 moves to the left in the position shown, fluid from the low pressure chamber 14 enters the chamber 70 through passages 80 and 82 in the moving pins 72. The fluid in chamber 70 acts against piston face 84.

Since the area of the piston face 84 is larger than the area of the inner end 86 of the pin 72, the fluid in the chamber 70 has a surface 78 and the end cap 18 where the movement of the moving pin 72 is shortened. The moving pin 72 is moved to the left until it is stopped by the contact between the inner surfaces 76.

When the piston 26 is reversed and moved to the right with respect to the shown position, the piston 26 contacts the protruding piston pin end 86 and drives the pin to the right of the shown position. The chamber 71 between the stepped surfaces 76 and 78 is in communication with the atmosphere through the passage 79. The interior and middle portions of the moving pins 72 have appropriate fluid seals as shown to practically prevent fluid from entering the chamber 71.

The plunger 77 includes an elongated rod 77a loosely fitted in the axial passageway in the outer portion of the pin 72. The outer end of the plunger 77 is cap-sealed by the switch contact 77b. The coil spring 75 between the end of the pin and the plunger contact 77b extends to move the plunger 77 to the right.

As the piston 26 moves the moving pin 72 to the right of the position shown, the spring 75 is compressed and effectively contacts the plunger 77 with the limit switch 74.

When the piston 26 moves to the left and the pin 72 moves to the left from the position shown, the moving pin 72 makes a relative movement to the plunger 77. This relative movement removes the compressive force exerted on the spring 75 and causes the plunger 77 to be released from effective contact with the contact switch 74.

The loose, slippery connection between the pin 72 and the plunger 74 provides room for positioning the switch 74 during assembly and prevents the limit switch from being damaged if the pin 72 moves excessively. give.

By providing an incision in the housing 10 as shown, the limit switch 74 can be installed in the restriction of the housing 10 and is hand operated.

The switch 74 is bolted to the mounting bracket 90. The bracket 90 is bolted to the mounting plate 92 which itself is bolted to the end cap 18 at one end. The mounting plate 92 has a passage that is machined to fit into the outer end portion of the moving pin 72. The mounting plate 92 also closes the outer end of the operator pin passage provided in the end cap 18 and to keep the sealing ring 73 in place against the relative force of the working fluid in the chamber 70. It contacts the outer end of the sealing ring 73.

The intensifier device utilizes fluid (oil) to drive the high pressure and low pressure piston assemblies to obtain high pressure water flow. The intensifier shown in FIG. 1 has a dual operation. It comprises a housing 10 in the form of an extended iron cylinder.

The right half is shown in FIG. The left half is the same.

Each end of the housing has an end retainer ring 12 and an end of the housing 10 is internally threaded to match an external thread on the end retainer ring 12 as shown. Within the housing 10, a low pressure chamber 14 is formed by an iron cylinder 16 that fits into a cylindrical end cap at each end (right cap is shown and the left cap is opposite but the same). Also in the housing 10, each of the left and right high pressures formed by an extended iron barrel cylinder 22 which is fitted at the inner end to the end cap 18 and at the outer end to the valve body 24 of the intake / exhaust valve assembly. A chamber is provided (the right high pressure chamber 20 is shown and is identical to the left high pressure chamber). The end retainer 12 operates through the valve body 24 and coincides with the outer end of the cylinder 22.

The outer surface of the end cap 18 coincides with the inner surface of the housing cylinder 10 with a small margin for sliding clearance. Tightening the end retainer 12 compresses the compression pressure chamber member in the longitudinal axis direction and positions the housing cylinder 10 in the longitudinal axis tension direction.

Once one or both of the end retainers 12 are removed, these members are very easily removed from the housing. The low and high pressure cylinders 16, 22 are mounted in an axial line with the housing cylinder 10 by means of end caps 18 and retainer rings 12.

Due to the relative dimensions of the members described so far, the pressure chamber member is limited to any longitudinal or transverse axis movement.

The low pressure and high pressure piston assembly includes a low pressure piston 26 and a left-right high pressure piston 28, 30. The low pressure piston is a cylindrical disk contained in the low pressure chamber 14. The outer circumferential surface thereof coincides with the inner surface of the low pressure cylinder 16 having a margin for sliding clearance, and is equipped with an appropriate hydraulic seal 32 to seal one side of the low pressure chamber 14 from the other. The high pressure piston is connected to the opposite side of the low pressure piston 26 and extends through the end cap 18 to the low pressure chamber sleeve 20. The outer end of the high pressure cylinder 20 fits over a pilot or shoulder that protrudes from the valve body 24.

The valve body 24 is machined to provide a cylindrical stub 24a. The end of the stub is machined to provide a smaller cylindrical end face as the sheet of high pressure static seal assembly 44. The short binary transition between the high pressure cylinder mounting stub and the high pressure sealing sheet has a metal protector for the sealing assembly 44.

The end diameter of the stub 24a corresponds to the diameter of the high pressure piston shown.

When the high pressure piston rod 30 is retracted from the position as shown, the low pressure water is led to the high pressure chamber 20 through the suction passage 50 in the intake / exhaust 어셈블리 valve assembly 48. When the piston rod 30 is returned back to the position shown, the water is compressed to high pressure and discharged through the discharge passage in the valve valve assembly 25. The flow of water into and out of the high pressure chamber 20 is controlled by a hydraulically actuated poppet valve valve 52.

The intake / discharge water check valve assembly 25 communicates with the low pressure water intake manifold 51, the poppet check valve mechanism 52, and the high pressure water discharge passage 54 in communication with the valve body 24 low pressure intake passage 50. And a manifold locking nut 55 for supporting the high pressure discharge water pipe adapter 54 and the manifold 51 to the valve body 24. The outer end of the valve body 24 is threaded on the outside thereof, and the lock nut 55 is screwed to fix the position of the manifold 51.

The low pressure suction water line 56 is attached to the manifold 51 and the high pressure discharge water line 57 is attached to the adapter 53. The inner surface of the manifold 51 is machined to provide the annular body 58 for the distribution of suction water from the suction pipe passage 56 to the suction passage 50.

4 and 5, the check valve mechanism 52 includes a suction poppet 100, a discharge poppet 102, a valve stem 104 connecting two poppets, a high pressure sheet 106, and a discharge poppet. And an enlarged contact end 108 of the stem 104 that supports and secures 102.

The stem 104 extends through the high pressure water discharge passage 54 and has a poppet installed at the opposite end. The inner end or head 110 of the stem 104 is adapted to provide an inner annular groove 111 for the return coil spring 114 and a spring retainer “E” ring clip 112 for supporting the poppet 100. It is processed.

This mechanism is provided with a suction poppet 100 mounted on the inner end face of the stub 24a to seal the low pressure water suction passage 50, and the discharge poppet 102 is a high pressure to seal the high pressure water discharge passage 54. It is arranged to rest on the sheet member 106.

The suction poppet 100 is slidably mounted and axially movable on the inner end of the stem 104. The outlet poppet 102 is axially slidably mounted on the outer end of the stem 102 and supported thereon by an enlarged stem end 108.

The length of the stem 104 between the head 110 and the end 108 is such that the discharge poppet 102 when the high pressure water moves the stem 104 and operates against the head 110 as far as the head 110 allows. ) Is of sufficient length to deviate from the sheet (shown in Figure 4).

The inner end of the head 110 and stem 104 is counterbore machined in the axial direction to provide a passage for communicating one or more diametric passages 116 that intersect and drill within the stem 104. The outer end of the stem 104 only into the interior of the discharge poppet 102 provides a passage 118 through the valve body 24 and the high pressure water discharge passage 54 between a portion of the stem 104 and the bore. The shape is made.

The intermediate length of the stem 104 is shaped to provide a passage 120 between a portion of the stem 104 and a bore providing a high pressure water discharge passage 54 through the valve body 24.

Passage 120 includes cross bores 116 and passage 118 such that the high pressure water passes through water discharge passage 54 when discharge poppet 102 is lifted from sheet 106 and travels to the position shown in FIG. ).

The adapter 53 extends the sheet member 106 into the high pressure water effluent conduit while having a space for the high pressure water to flow from the passage 54 to the discharge conduit 57 and around the poppet 102 and the end 108. It has an internal cavity 122 that closes the outlet poppet 102 and the enlarged stem 108. The adapter 53 has an inclined annular surface 124 at the base of the cavity 122.

The face 124 is on the sheet member 106 to secure the sheet 106 in the recess 126 provided in the valve body 24 when the adapter 53 is screwed onto the valve body 24. Contact against the corresponding inclined surface.

The suction valve 100 has an annular recess 128 that communicates with the suction water passage 50 when the suction poppet 100 is seated against the end face 130 of the stub 24a.

The spring 114 is seated in a compressed state while being processed in the adjacent surface of the suction poppet 100. When the water is compressed by a high pressure piston to a pressure sufficient to overcome the spring force of the spring 114, the valve stem 104 is brought to the position shown in FIG. 4 by the hydraulic pressure acting on the valve stem head 110. Is moved. Prior to this, the hydraulic pressure acting on the suction poppet 100 is opposed to the suction poppet 100 against the face 130 on the stub 24a of the valve body 24 to seal off the low pressure suction passage 50. ).

When the valve stem 104 is in the position shown in FIG. 4, the discharge poppet is lifted from the sheet member, and the high pressure water is led to the cavity 122 by the high pressure piston rod through the passages 114, 116, 120, and 118 to the conduit. Exit through (57).

When the high pressure piston rod reaches the end of the compression cycle and is reversed and starts to contract, the spring force of the spring 110 and the high pressure water of the conduit 57 move the valve stem 104 to the position of FIG. 5. The discharge poppet 102 is brought into close contact with the sheet member 114 to close the high pressure discharge of the conduit 57.

As the high pressure piston rod contracts, the low pressure hydraulic force from the passage 50 lifts the poppet 110 from its sheet 130 on the stub 24a and flows around the poppet 100 into the high pressure chamber.

The spring force of the spring 114 is small enough so that the low pressure hydraulic force acting on the opposite side of the poppet 100 causes the valve stem 104 from the position shown in FIG. 5 to the valve stem to discharge water from the passage 50 to the high pressure chamber. Will move poppet 100 along.

The movement distance of the poppet 100 is limited by the spring clip 112. Of the two poppet sealing surfaces, the sealing surface 132 associated with the discharge poppet 102 causes severe stress. Thus, the sheet member 124 is provided as the counter member. In addition, the mating surfaces of the poppet 102 and the sheet member 124 are subject to wear and therefore these surfaces should be periodically polished to prevent high pressure water leakage from the conduit 57.

The shape and arrangement of the adapter 53 eases this problem.

The adapter 53 can be removed by unscrewing from the valve body 24 to expose the sheet member 106, the poppet 102, and the enlarged stem end 108 without the need for disassembly of other parts of the system. Can be.

Poppet 102 replaces the polishing sheet member 106 or poppet 102 of the sealing surface by removing the assembly and disconnecting the clip 112, or any operation required in connection with the high pressure discharge 첵 valve mechanism. Can be removed to allow.

The high pressure outlet conduit 57 is typically a stainless steel tube and more preferably is screwed by a coupling mechanism that is wound coiled around the adapter 53 and allows the adapter to pivot about the conduit 57. . The elasticity of the tube on the coil allows removal from the valve body 24 for operation on the mechanism in which the adapter 53 is exposed.

Although the preferred embodiment of the present intensifier has been described in accordance with the basic principles of the invention, any change will be possible without departing from the scope of the invention.

Claims (9)

A fluid pressure booster, comprising: a low pressure and high pressure cylinder device having a cylindrical low pressure chamber and a pair of cylindrical high pressure chambers extending from opposite ends of the low pressure chamber, and a double operating low pressure provided for reciprocating movement in the low pressure chamber. A low pressure and high pressure piston device having a piston portion and having a pair of extended high pressure piston portions connected to opposite sides of the low pressure piston portion and extending from the low pressure piston portion to an adjacent high pressure chamber for reciprocating movement, and the low pressure and high pressure chamber in a row A cylindrical housing device for closing and limiting the low pressure and high pressure cylinder device to maintain and maintain the housing, and the housing in fluid communication with the high pressure chamber for sending compressed fluid to one high pressure chamber and simultaneously discharging the compressed fluid from the other high pressure chamber. Fluid suction installed by the device and And a discharge device and a working fluid suction and discharge device provided while the fluid is in fluid communication with the low pressure chamber so that the working fluid alternately operates with respect to one side or the other side of the low pressure piston so that the low pressure and high pressure piston devices reciprocate. Pressure booster. The low pressure and high pressure cylinder device of claim 1, wherein the low pressure and high pressure cylinder device has a low pressure cylinder and end caps fitted together to form the low pressure chamber, and a pair of high pressure cylinders are aligned with each other and in line with the low pressure cylinder to form the high pressure chamber. Extending outwardly from the furnace end cap, each end cap having a bore extending through the high pressure piston portion, wherein the low pressure and high pressure cylinder device is configured to compress the low pressure and high pressure cylinder to the end cap by the cylindrical housing device. And arranged in a fluid pressure intensifier. 3. The fluid suction and discharge device according to claim 2, wherein the fluid suction and discharge devices each have a pair of valve valve bodies which are fitted to one outer end of the high pressure cylinder and are formed and installed to be compressed to the high pressure cylinder by the cylindrical housing device. Fluid pressure intensifier, characterized in that. 4. The pressure regulator of claim 3, wherein the fraud housing device has a housing cylinder having a threaded end and a pair of threaded retainers each provided with a bore in which one of the valve bodies is fitted, the end retainer being operated under conditions of operation. Characterized in that the housing arrangement is formed and arranged to compressally connect the valve body adjacent to one of the high pressure cylinders when screwed to the housing cylinder with sufficient force to hold and set it in place. Pressure intensifier. A working fluid suction and discharge device installed while being in fluid communication with the low pressure chamber in such a manner that the working fluid alternately operates with respect to one side or the other side of the low pressure piston unit to reciprocate the low pressure and high pressure piston device, and the working fluid suction and discharge device. The fluid pressure intensifier of claim 1, comprising a working fluid flow control operating device for operating the working fluid flow control device to change the direction of the working fluid flow therethrough. It is installed in fluid communication with the low pressure chamber for movement and is moved by contacting the low pressure piston portion from the first, i.e., non-operational position to the second, ie operating position, and to the first position by the working fluid in the low pressure chamber. A fluid pressure intensifier formed and arranged to return. 6. The low pressure and high pressure cylinder device of claim 5, wherein the low pressure and high pressure cylinder device comprises a pair of low pressure chamber end caps, each end cap having a bore from which an actuating piston device extends to form opposite ends of the low pressure chamber. The apparatus includes a moving pin having an inner end exposed to the low pressure chamber, an outer end extending outwardly from the end cap, and an intermediate portion having a piston surface in fluid communication with the low pressure chamber, wherein the moving pin comprises the piston face. The area of the inner end is larger than the area of the inner end, so that the compressed working fluid in the low pressure chamber operating on the piston face and the inner end is formed and arranged to validate the movement of the moving pin into the low pressure chamber. A fluid pressure intensifier. 7. A piston mounting switch plunger according to claim 6, wherein said piston device has a spring-loaded switch contact plunger installed to be superimposed within an outer end of said moving pin for contact operation with a switch when said actuating piston device is moved to an actuating position. Fluid pressure intensifiers. 4. The fluid suction and discharge device according to claim 3, wherein each valve body has a longitudinal axial fluid passage opening from one end to an adjacent high pressure piston chamber and an opening toward the cavity within the connecting mechanism to the high pressure discharge pipe adjacent to the other end. Has a valve mechanism for each valve body, each valve mechanism including an extended valve stem extending from the high pressure chamber at the inner end and the connecting cavity at the outer end through the axial fluid passage and connecting the high pressure fluid passage to the connecting cavity. And through the connecting passage, the discharge poppet is mounted by the valve stem outer end in the connecting cavity and is exposed to the connecting cavity through the high pressure fluid reverse flow from the connecting cavity. Shaped to be seated against the discharge sheet member to prevent In that it comprises a sheet output member accumulator fluid pressure increase, characterized. 9. The apparatus of claim 8, wherein the fluid suction and discharge device has a low pressure fluid suction distributor installed by each valve body, and each valve body has an extended suction fluid passage opening to an adjacent high pressure piston chamber and a low pressure fluid adjacent to one end. Having an opening to the suction distributor, each valve mechanism is slidably installed on the inner end of the valve stem in the high pressure chamber, and closes the suction fluid passage opening to the high pressure fluid chamber and closes the suction fluid in the suction fluid passage. And a suction valve that surpasses the force exerted by the fluid pressure intensifier.

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