KR20150016677A - Automatic pressure regulating control device for reciprocatable double acting booster - Google Patents

Abstract

The present invention relates to an automatic pressure control regulator for a reciprocatable double acting booster having a main control valve and a pressure control valve. The main control valve includes: a first valve body having two connecting ports which connect to a first input-output port and a second input-output port; a second valve body integrated with the first valve body having two connecting ports which connect to a first exhaust back pressure port and a second exhaust back pressure; a first spool operating inside the first valve body; and a second spool integrated with the first spool and operating inside the second valve body. The pressure control valve includes: a pressure control valve body having a first side port which connects to a driving port of the first valve body, and having a second side port which connects to a driving device to supply the predetermined pressure, while the back pressure ports connected to the second side port and generating a back pressure; a pressure control valve spool operating inside the pressure control valve body; and a pressing tool for pressure control applying the set pressure on the pressure control valve spool. According to the composition of the automatic pressure control regulator for a reciprocatable double acting booster, the present invention facilitates the assembling construction and installation of the reciprocatable double acting booster by simplifying the control configuration and control flow path while boosted pressure is constantly maintained by being continuously supplied with fluids regardless of the external load changes.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic pressure regulating control device for a double-acting reciprocating pressure booster,

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an automatic pressure regulation control device for a double-acting type reciprocating pressure booster, and more particularly, to an automatic pressure regulation control device for a double-acting type reciprocating pressure booster in which the reciprocating pressure- To an automatic pressure regulating control mechanism for a double-acting reciprocating pressure booster for controlling the flow of a pressure fluid.

The pressure booster is provided with a piston which is freely displaceable in the cylinder, so that the piston is displaced in response to the action of the pressure fluid supplied to the operating chamber of the cylinder, so that the pressure fluid in the compression chamber formed on the opposite side to the piston from the operating chamber, And the outlet pressure is increased to be supplied to the drive device, and the pressure fluid is discharged from the discharge port through the check valve. There are a single acting pressure booster and a double acting pressure booster.

The single acting pressure booster 10 is a booster which alternately repeats the inflow / outflow of the pressure fluid in two cycles. As shown in FIG. 1, the booster 10 includes a cylinder 11a formed on one side thereof and a pressure- A driving piston 12 which operates in the driving chamber 11a and a pressure-increasing piston 13 which operates in the pressure-increasing chamber 11b. The driving piston 12 and the pressure- And connected by a rod 14. The single acting pressure booster 10 is provided with a control valve V1 for controlling the inflow and outflow directions of the fluid to be connected to both ports of the drive chamber 11a and to supply the pressurized pressure fluid to the drive device F (Two) check valves V2 for supplying the pressurized fluid to the tank T and controlling the suction direction of the pressure fluid in the tank T are connected to the ports of the booster chamber 11b.

The double acting type pressure booster 20 is a booster which alternately repeats the inflow / outflow of the pressure fluid in one cycle. As shown in FIG. 2, the booster 20 includes a cylinder 21a in the middle and a pressure increase chamber 21b on both sides. And a pressure-increasing piston 23 that operates in the pressure-increasing chamber 21b. The pressure-increasing piston 23 is connected to both sides of the drive piston 22, Respectively. The double acting pressure booster 20 is provided with a control valve V1 for controlling the inflow and outflow directions of the fluid to be connected to both ports of the drive chamber 21a and to supply the pressurized fluid to the drive device F (Four) check valves V2 for supplying the pressurized fluid to the tank T and controlling the suction direction of the pressure fluid in the tank T are installed in connection with the ports of the pressurization chamber 21b.

Such a single acting or double acting pressure booster suffers from a surge pressure during the change of direction and an outlet pressure fluctuates according to the change of load, and the double-acting pressure booster must have a long cylinder length. A reciprocatable double acting booster is disclosed in Korean Patent Publication No. 2008-0083603, Korean Patent No. 10-1028380, and the like to compensate for the disadvantage that the length becomes longer.

The double-acting type reciprocating booster 30 is a booster which alternately repeats the inflow / outflow of the pressure fluid in one cycle. As shown in FIG. 3, the first chamber 31a is provided at one side (see Korean Patent Publication No. 2008-0083603) A first piston 32 which is operated in the first chamber 31a and a second piston 33 which is operated in the second chamber 31b and in which a second chamber 31b is formed on the other side, The first piston 31 and the second chamber 31b are connected to each other by a piston rod 34. The first piston 31 and the second chamber 31b are connected to each other by a first piston 32, And a back pressure chamber in which the pressure fluid is supplied and discharged by the second piston (33) and the pressure fluid is changed in pressure to be discharged. A switching valve 40 for controlling the inflow and outflow directions of the fluid is provided in the drive chambers of the first chamber 31a and the second chamber 31b in the double-acting type reciprocating booster 30, (Four) check valves 50 for supplying the pressure fluid changed in the back pressure chambers of the first chamber 31a and the second chamber 31b to the drive apparatus and forming the back pressure in the back pressure chamber are provided.

However, since the valve for controlling the double-action type reciprocating booster 30 is divided into one directional control valve and a plurality of check valves, there are many control parts and the control configuration and control flow path are complicated, It is not easy to assemble and install the battery.

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above problems, and it is an object of the present invention to provide a pressure booster which facilitates assembly and installation of a double-acting reciprocating pressure booster by simplifying a control structure and a control channel, To provide an automatic pressure regulating control mechanism for a double-acting reciprocating pressure booster which keeps the boosted pressure constant while maintaining a constant pressure.

To achieve the above object, according to the present invention, there is provided an automatic pressure regulation control mechanism for a double-acting type reciprocating pressure booster, comprising a first input / output port formed on one side of a first cylinder chamber, a second input / output port formed on a side of a second cylinder chamber , A first discharge back pressure port formed on the other side of the first cylinder chamber, and a second discharge back pressure port formed on the other side of the second cylinder chamber, the automatic pressure regulation control mechanism comprising: A main control valve connected to the pressure booster for opening and closing the input / output port and exhaust backpressure port connected to the pressure booster, and a pressure A control valve; The main control valve includes a first valve body having a first port and a second port connected to the second port, and a drive port connected to the pressure control valve, a first valve body having a first exhaust backpressure port and a second exhaust backpressure A second valve body having two connection ports connected to the port and having a drive port defining a back pressure in the double-acting reciprocating pressure booster, the valve body integrally formed with the first valve body; And includes a first spool and a second spool that operates in the second valve body and is formed integrally with the first spool.

The pressure regulating valve includes a primary port connected to the driving port of the first valve body, a secondary port connected to the driving device for supplying a predetermined pressure, and a pressure regulating valve connected to the secondary port to form a back pressure, A regulating valve body; A pressure regulating valve spool operable within the pressure regulating valve body; And a pressure regulator for applying a set pressure to the pressure regulating valve spool.

The presser foot is a spring. The pressure control valve spool has two land portions connected by one spool rod portion.

And a latch valve connected to the double-acting reciprocating pressure booster and the main control valve for operating the spool of the main control valve according to the position of the piston of the double-acting reciprocating pressure booster.

The latch valve includes an inlet port connected to a source of fluid, a latch valve body having a first valve body of the main valve or a latch valve outlet port connected to the second valve body for applying pilot pressure; A latch valve spool operable within the latch valve body; And a valve operation connecting rod connected to the latch valve spool. The valve operation connecting rod has a pressing pin portion protruding into the first cylinder chamber or the second cylinder chamber.

The latch valve body is formed with an outlet port for returning fluid to the tank. The latch valve outlet port communicates with a spool latch port that presses the latch valve spool to maintain the switching position of the valve.

The latch valve spool has two land portions connected by one spool rod portion.

The first valve body is formed with a supply port for supplying fluid from a fluid supply source, and the second valve body is formed with a return port for returning fluid to the tank. The return port is formed by one or two.

The first spool and the second spool include a land portion and a spool rod portion connecting the land portion, and the first spool and the second spool are connected and integrated by the spool connecting rod portion.

In the first spool, three land portions are connected by two spool rod portions, and the second spool is connected by two spool rod portions.

According to the automatic pressure regulation control mechanism for a double-acting type reciprocating pressure booster according to the present invention, the automatic pressure regulation control mechanism for a double-acting reciprocating pressure booster according to the present invention is connected to a double-acting reciprocating pressure booster having two input / output ports and two exhaust backpressure ports, The control flow path is simplified to facilitate assembly and installation of the double-acting-type reciprocating pressure booster, and the effect of keeping the pressurized pressure constant while the flow rate is continuously supplied even when the external load is changed.

1 is a configuration diagram showing a control device to which a general single acting pressure booster is coupled.
2 is a block diagram showing a control device to which a general double acting pressure booster is coupled.
Fig. 3 is a configuration diagram showing a conventional double-acting type reciprocating pressure booster.
4 is a configuration diagram showing an automatic pressure regulation control mechanism for a double-acting type reciprocating pressure booster according to the first embodiment of the present invention.
5A and 5B are operational states of an automatic pressure regulation control mechanism for a double-acting type reciprocating pressure booster according to a first embodiment of the present invention.
6 is a configuration diagram showing an automatic pressure regulation control mechanism for a double-acting type reciprocating pressure booster according to a second embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. Note that, in the drawings, the same components are denoted by the same reference symbols as possible. Further, the detailed description of known functions and configurations that may obscure the gist of the present invention will be omitted. For the same reason, some of the components in the drawings are exaggerated, omitted, or schematically illustrated.

4 is a configuration diagram showing an automatic pressure regulation control mechanism for a double-acting type reciprocating pressure booster according to the first embodiment of the present invention. In the first embodiment, an automatic pressure regulation control mechanism including a latch valve and a pressure control valve at the same time will be described by way of example. As shown in the figure, the control device according to the first embodiment of the present invention is an automatic pressure regulation control mechanism for controlling the double-acting type reciprocating pressure booster 60, and includes a main control valve 70, a latch valve 80, (90).

The double-acting type reciprocating pressure booster 60 includes a cylinder 61 in which a first cylinder chamber 61a is formed on one side and a second cylinder chamber 61b is formed on the other side and a cylinder 61a which operates in the first cylinder chamber 61a. A first piston 62 and a second piston 63 operating in the second cylinder chamber 61b and a piston rod 64 integrally connecting the first piston 62 and the second piston 63 . A first input / output port 65a is formed on one side (first piston side) of the first cylinder chamber 61a and a second input / output port 65b is formed on one side (second piston side) of the second cylinder chamber 61b. A first discharge back pressure port 66a is formed on the other side (piston rod side) of the first cylinder chamber 61a and a second discharge back pressure port 66b is formed on the other side (piston rod side) of the second cylinder chamber 61b. A port 66b is formed.

The main control valve 70 is a valve connected to the double-acting type reciprocating pressure booster 60 for opening and closing the first and second input / output ports 65a and 65b and the first and second discharge back pressure ports 66a and 66b, A valve body 110, a second valve body 120, a first spool 130, and a second spool 140.

The latch valve 80 is connected to the double-acting reciprocating pressure booster 60 and the main control valve 70 to actuate the spool of the main control valve 60 in accordance with the piston position of the double-acting reciprocating pressure booster 60 A latch valve body 150, a latch valve spool 160, and a direction switching valve operation connecting rod 170. The latch valve 80 is in the form of a three-port two-position valve, and the position of the valve is switched by the valve operation connecting rod 170 connected to the pressure booster 60. The switching position of the valve is controlled by a latch valve spring, Is held by the pressure of the latch port and serves to apply or release pressure to a pilot port, which will be described later, of the main controller valve 70 in accordance with the change of the position of the latch valve 80. [

The pressure regulating valve 90 is connected to the main control valve 70 and supplies the fluid boosted by the bi-directional reciprocating pressure booster 60 to the driving device at a constant pressure irrespective of the load variation. 180, a pressure regulating valve spool 190, and a pressurizing valve 195.

The first valve body 110 and the second valve body 120 are integrally connected to each other through the connection passage portion 101. The first valve body 110 has a first spool 130, (Not shown) of the latch valve body 150 is provided at the other end of the first valve body 110. The first valve body 110 is provided with an operating spring 102 for applying an elastic restoring force to the spool A pilot port 103 connected to the outlet port for operating the first spool 130 and the second spool 140 by the pressure of the fluid is formed. The pilot port 103 may be formed in the second valve body 120.

A connection port (A port) A connected to the first input / output port 65a through the booster connection pipe D11 is formed in the first valve body 110 so as to form an inner space on the inner surface of the first valve body 110 And a connection port (B port) B connected to the second input / output port 65b through the booster connection pipe D12 is formed as an inner space on the inner surface of the first valve body 110. [ The first valve body 110 is also provided with a supply port (P port) P through which a fluid is supplied from a fluid supply source (not shown) through a supply connection pipe E10 to an inner space of the first valve body 110 Respectively. The first valve body 110 is provided with two drive ports (C port) for supplying the fluid pressurized by the double-acting type reciprocating pressure booster 60 to the pressure regulating valve 90 through the drive connection pipe F10 C1, and C2 are formed in the inner surface of the first valve body 110 as a recessed space. The two drive ports (C1) and (C2) are connected through a drive connection pipe (F10). Five ports are formed in the first valve body 110 except for the pilot port 103.

A connection port (Xa port) Xa connected to the first exhaust backpressure port 66a through the booster connection pipe D13 is formed in the second valve body 120 in the inner surface of the second valve body 120 And a connection port (Xb port) Xb connected to the second discharge back pressure port 66b through the booster connection pipe D14 is formed as an inner space of the inner surface of the second valve body 120 . In addition, two return ports (R ports) R1 and R2 for returning the fluid to the tank 104 through the return connection pipe G10 are formed in the second valve body 120 on the inner surface of the second valve body 120 And is formed as a recessed space. The second valve body 120 is connected to the driving connection pipe F10 through the orifice O so that the driving port C port C3 forming the back pressure is inserted into the inner surface of the second valve body 120 Space. Two return ports (R1) (R2) are connected via a return connection pipe (G10). Five ports are formed in the second valve body 120.

The first spool 130 and the second spool 140 are connected to each other through the spool connecting rod portion 105 to be integral with each other. The spool connecting rod portion 105 is connected through the inside of the connecting passage portion 101. The first spool 130 forms a five port three position valve together with the first valve body 110 and the second spool 140 forms a five port three position valve together with the second valve body 120. The first spool may form a 5-port 2-position valve or a 4-port 2-position valve with the first valve body and the second spool may form a 5-port 2-position valve or a 4- It is possible.

The first spool 130 operates in the first valve body 110 and the three land portions 131, 132 and 133 are connected by the two spool load portions 134 and 135. The land portion 131 closes the drive port C1 and the land portion 132 opens and closes the supply port P and the land portion 133 opens and closes the drive port C2. The spool rod portion 134 connects the land portion 131 and the land portion 132 and the spool rod portion 135 connects the land portion 132 and the land portion 133. [

The second spool 140 operates in the second valve body 120 and is structured such that the two land portions 141 and 142 are connected by one spool rod portion 143. The land portion 141 opens and closes the connection port Xa and the land portion 142 opens and closes the connection port Xb. The spool rod portion 143 connects the land portion 141 and the land portion 142.

4 shows a state in which the land portions 131, 132 and 133 of the first spool 130 close the supply port P and the drive ports C1 and C2 and the land portions 141 and 142 of the second spool 140 Represents a neutral position in which the connection ports Xa and Xb are closed and the fluid is not supplied to the first input / output port 65a or the second input / output port 65b of the double-action type reciprocating pressure booster 60 .

The latch valve body 150 is provided with a latch valve spring 106 which applies an elastic restoring force in contact with the latch valve spool 160 to the end of the latch valve body 150, An inlet port L1 through which the pressure fluid flows in the connection pipe E10 is formed as an inner space of the inner surface of the spout valve body 150 while a pressure fluid is supplied through the outlet connection pipe J10 to the tank 104 (Not shown) is formed on the inner surface of the latch valve body 150 as a recessed space. The latch valve body 150 is formed with a latch valve outlet port L4 connected to the pilot port 103 through the pilot port connection pipe K10 to apply pilot pressure to the first valve body 110. [ The latch valve outlet port L4 communicates with the spool latch port L3 that presses the latch valve spool 160 to maintain the switching position of the valve. The latch valve outlet port L4 and the spool latch port L3 may be connected to a pilot port formed in the second valve body 120. [ The inlet port L1 may be directly connected to the fluid source directly through the inlet connection pipe H10 without through the supply connection pipe E10.

The latch valve spool 160 operates in the latch valve body 150 and is structured such that the two land portions 161 and 162 are connected by one spool rod portion 163. The latch valve spool 160 moves to one side by the elastic force of the latch valve spring 106 and keeps the pilot pressure of the main valve 70 in the released state. The land portion 161 opens and closes the outflow port L2 and the land portion 162 opens and closes the inflow port L1. 4 is a neutral state in which the land portions 161 and 162 close the outflow port L2 and the inflow port L1.

The direction switching valve operation connecting rod 170 has one side fixedly connected to the land portion 162 of the latch valve spool 160 and the other side projecting into the first cylinder chamber 61a or the second cylinder chamber 61b And the latch valve spool 160 is moved left and right when the first piston 62 and the second piston 63 reach the end of the cylinder chamber. The direction switching valve operation connecting rod 170 may be replaced by a separate mechanical push rod or electromagnet.

The pressure regulating valve body 180 includes a primary port M1 connected to the driving port C2 of the first valve body 110 and a secondary port connected to the driving device And a back pressure port M3 connected to the secondary port M2 to form a back pressure. The primary port M1 is connected to the drive connection pipe F10 via an orifice O via a drive input connection pipe N10. The secondary output port M2 is connected to the drive unit through a drive output connection pipe Q10 and the drive output connection pipe Q10 is connected to the back pressure port M3 through the back pressure connection pipe S10 via the orifice O, Respectively. The back pressure port M3 applies back pressure at the left end of the land portion 191 of the pressure control valve spool 190. An air inlet 181 is formed in the pressure regulating valve body 180 so that a space in which the pressure regulating pressurizing valve 195 operates is exposed to atmospheric pressure.

The pressure regulating valve spool 190 operates in the pressure regulating valve body 180 and is structured such that the two land portions 191 and 192 are connected by one spool rod portion 193. The land portion 191 opens and closes the secondary port M2. In the steady state, the land portion 191 opens the secondary port M2. The primary port M1 is always open irrespective of the movement of the pressure regulating valve spool 190.

The pressure regulating valve 195 applies a predetermined pressure to the pressure regulating valve spool 190 and is installed in close contact with the right end of the land portion 192. The pressure regulating pressure regulator 195 is a spring, but various pressure regulators such as a proportional control solenoid can be used.

The operation of the automatic pressure control mechanism for the double-acting type reciprocating pressure booster according to the first embodiment of the present invention will be described with reference to FIGS. 5A and 5B.

When the first spool 130 and the second spool 140 move to the right according to the restoring action of the operating spring 102 at the neutral position of FIG. 4, as shown in FIG. 5A, The connection port Xb communicates with the drive port C2 and the connection port Xb communicates with the drive port C2 while the connection port Xa communicates with the return port R1, (Hereinafter referred to as " A position ").

The fluid supplied from the fluid supply source (not shown) through the supply connection pipe E10 is connected to the supply port P and the connection port A and flows through the booster connection pipe D11 to the first input / (The left side space of the first piston) of the first cylinder chamber 61a through the first cylinder chamber 61a and the piston joints (the first piston and the second piston and the piston rod) 62 of the pressure booster 60, 63, 64) to the right. At the same time, the fluid in one side (right side) space of the second cylinder chamber 61b (the space on the right side of the second piston) flows out through the second input / output port 65b, passes through the booster connection pipe D12, And the drive port C2 and is supplied to the drive device (not shown) via the pressure control valve 90 via the drive connection pipe F10.

On the other hand, the fluid in the other side (right side) space (the space on the right side of the first piston) of the first cylinder chamber 61a flows out through the first discharge back pressure port 66a and passes through the booster connection pipe D13, Xa and the return port R1 and is discharged to the tank 104 through the return connection pipe G10. Simultaneously, the fluid flowing out through the connection port B and the drive port C2 passes through the booster connection pipe D14 through the drive port C3 and the connection port Xb, and flows through the second discharge backpressure port 66b (The left space of the second piston) of the second cylinder chamber 61b to apply the back pressure to the second piston 63.

When the right side surface of the first piston 62 of the double-acting type reciprocating pressure booster 60 contacts the pressing pin portion 171 of the valve operation connecting rod 170, the latch valve spool 160 moves to the right, And the pressure fluid flowing into the latch valve body 150 through the inlet connection pipe H10 connected to the fluid source flows through the latch valve outlet port L4 and the pilot port connection pipe K10 to the first A pilot pressure is applied to the right side surface of the first spool 130 in the pilot port 103 of the valve body 110 to move the first spool 130 to the left. At this time, since the spool latch port L3 is connected to the latch valve outlet port L4, back pressure is applied to the left side surface of the latch valve spool 160, and the latch valve spool 160 is moved to the right The outlet port L2 is kept closed.

The supply port P is communicated with the connection port B and the connection port A is communicated with the connection port B as shown in Figure 5B when the second spool 140 integrally formed with the first spool 130 moves to the left, The connection port Xa communicates with the drive port C3 and the connection port Xb communicates with the return port R2 (hereinafter, referred to as a B position).

The fluid supplied from the fluid supply source (not shown) through the supply connection pipe E10 is connected to the supply port P and the connection port B and flows through the booster connection pipe D12 to the second input / (The right side space of the second piston) of the second cylinder chamber 61b through the first and second piston chambers 61a and 61b and the piston assemblies (the first piston and the second piston and the piston rod) 62 of the pressure booster 60, 63, 64) to the left. At the same time, the fluid in one side (left side) space (the left side space of the first piston) of the first cylinder chamber 61a flows out through the first input / output port 65a, passes through the booster connection pipe D11, And the driving port C1 and is supplied to the driving device (not shown) via the pressure control valve 90 via the driving connection pipe F10.

On the other hand, the fluid in the other side (left side) space of the second cylinder chamber 61b (the left side space of the second piston) flows out through the second discharge back pressure port 66b, passes through the booster connection pipe D14, Xb and the return port R2, and is discharged to the tank 104 through the return connection pipe G10. At the same time, the fluid flowing out through the connection port A and the drive port C1 passes through the booster connection pipe D13 through the drive port C3 and the connection port Xa, and flows through the first discharge backpressure port 66a (The right side space of the first piston) of the first cylinder chamber 61a to apply the back pressure to the first piston 62a.

At this time, the left side surface of the second piston 63 of the double-acting type reciprocating pressure booster 60 is brought into contact with the pressing pin portion 171 of the valve operation connecting rod 170 so that the latch valve spool 160 is engaged with the latch valve spring 106, The inflow port L1 is closed and the outflow port L2 is opened so that the pilot pressure through the spool latch port L3 and the pilot port 103 is released, The first spool 130 is moved to the right by the elastic force of the operating spring 102. [

As described above, the piston assemblies (the first piston, the second piston, and the piston rod) of the pressure booster are supplied through the supply port P from the fluid supply source as the neutral position and the A position and the B position are repeated in the cylinder 61 The fluid is pressurized through a double-acting, reciprocable pressure booster (60) to continuously drive the drive through the drive ports (C1, C2).

At this time, if the fluid pressure is higher than the set pressure of the pressurizing port 195 of the pressure regulating valve 90 in accordance with the fluid pressure output through the drive connection pipe F10, the pressure regulating valve spool The back pressure is applied to the pressure regulating valve spool 190 so that the pressure regulating valve spool 190 moves to the right to close the secondary port M2. When the output fluid pressure is lower than the set pressure of the pressure applying valve 195 of the pressure regulating valve 90, the pressure regulating valve spool 190 is moved to the left again by the pressure of the pressure regulating valve 195, M2. Therefore, it is possible to amplify and maintain a constant pressure despite the load fluctuation.

6 is a configuration diagram showing an automatic pressure regulation control mechanism for a double-acting type reciprocating pressure booster according to a second embodiment of the present invention. As shown in the figure, the control device 200 according to the second embodiment of the present invention includes a main valve 70 connected to the double-action type pressure-return booster 60 for opening and closing the input / output port and the exhaust backpressure port, A latch valve 80 connected to the pressure booster 60 and the main control valve 70 for actuating the spool of the main control valve 70 in accordance with the position of the piston of the double acting type reciprocating pressure booster 60, And a pressure regulating valve (90) connected to the double-acting type reciprocating pressure booster (60) for supplying the fluid, which has been pressurized, to the drive device at a constant pressure regardless of the load variation.

The main control valve 70 includes a first valve body 210 having two connection ports A and B to which the booster connection pipes D21 and D22 are respectively connected and a booster connection pipe D23 and D24, A second valve body 220 integrally formed with the first valve body 210 and having two connection ports Xa and Xb respectively connected to the first valve body 210 and the second valve body 210, And a second spool 240 that operates in the second valve body 220 and is formed integrally with the first spool 230.

The first valve body 210 is formed with a supply port (P port) P through which fluid is supplied from a fluid supply source (not shown) through a supply connection pipe E20, Two drive ports (C ports) C1 and C2 for supplying the fluid pressurized by the booster to the drive device via the pressure regulating valve 90 are formed. Two return ports (R ports) R1 and R2 for returning fluid to the tank 204 through the return connection pipe G20 are formed in the second valve body 220 while the back pressure connection pipe S20 (C port) C3 which is connected to the pressure regulating valve 90 and forms a back pressure on the pressure regulating valve 90. [

The pressure regulating valve 90 is connected to the main control valve 70 and supplies the fluid boosted by the bi-directional reciprocating pressure booster 60 to the driving device at a constant pressure irrespective of the load variation. 280, a pressure regulating valve spool 290, and a pressurizing port 295.

The pressure regulating valve body 280 includes a primary port M1 connected to the driving port C2 of the first valve body 210 and a secondary port connected to the driving device And a back pressure port M3 connected to the secondary port M2 to form a back pressure. The primary port M1 is connected to the drive connection pipe F20 via an orifice O via a drive input connection pipe N20. The secondary port M2 is connected to the driving device through the driving output connection pipe Q20 and the driving output connection pipe Q20 is connected to the back pressure port M3 through the back pressure connection pipe S20 via the orifice O Subsequently, the back pressure connection pipe S20 is connected to the driving port C3 of the second valve body 220. [ The back pressure port M3 applies a back pressure at the left end of the pressure regulating valve spool 290.

The remaining configuration and operation of the second embodiment of the present invention are similar to those of the first embodiment (Figs. 4 to 5B), and therefore, a detailed description thereof will be omitted.

In an embodiment of the present invention, the first spool and the second spool of the main control valve may be configured in the form of two to six land portions. In the first and second embodiments of the present invention, the first spool has three land portions, and the second spool has two land portions.

In an embodiment of the invention, the spool of the latch valve may be configured in the form of two to three land portions. In the first and second embodiments of the present invention, the spool of the latch valve has two land portions.

Further, the automatic pressure control mechanism of the present invention can be used as an automatic flow control mechanism for FA because the double-acting type reciprocating pressure booster 60 functions as a flow amplifier by reversing the inlet and outlet.

It should be noted that the embodiments of the present invention disclosed in the present specification and drawings are only illustrative of the present invention in order to facilitate the understanding of the present invention and are not intended to limit the scope of the present invention. It will be apparent to those skilled in the art that other modifications based on the technical idea of the present invention are possible in addition to the embodiments disclosed herein.

60: Double-acting reciprocating pressure booster
61: cylinder 61a: first cylinder chamber
61b: second cylinder chamber 62: first piston
63: second piston 64: piston rod
65a: first input / output port 65b: second input / output port
66a: first exhaust backpressure port 66b: second exhaust backpressure port
70: main valve 80: latch valve
90: pressure regulating valve 101: connecting passage portion
102: Operation spring 103: Pilot port
104: tank 105: spool connecting rod section
106: latch valve spring 110: first valve body
120 second valve body 130: first spool
140: second spool 150: latch valve body
160: Latch valve spool 170: Direction switching valve operation connecting rod
171: Pushing pin part 180: Pressure regulating valve body
190: Pressure regulating valve spool 195: Pressure regulating valve
A, B, Xa, Xb: connection port C1, C2, C3, C4:
D11, D12, D13, D14: Booster connector
E10: Supply connector F10: Drive connector
G10: Return connector H10: Inlet connector
J10: Outlet connector K10: Pilot port connector
L1: incoming port L2: outgoing port
L3: Spool latch port L4: Latch valve outlet port
M1: Primary port M2: Secondary port
M3: Back pressure port N10: Drive input connector
O: Orifice P: Supply port
Q10: Drive output connector R1, R2: Return port
S10: Backpressure connector

Claims (14)

A first input / output port formed on one side of the first cylinder chamber, a second input / output port formed on a side of the second cylinder chamber, a first exhaust backpressure port formed on the other side of the first cylinder chamber, And a second discharge back pressure port formed on the other side,
A main control valve connected to the double-acting type pressure booster for opening and closing the two input / output ports and the two discharge back pressure ports, and a control valve connected to the main control valve for controlling the fluid pressurized by the double- And a pressure regulating valve for supplying the pressure regulating valve to the drive unit at a constant pressure without using the pressure regulating valve;
Wherein the main valve has a first valve body having a first port connected to the first input / output port and a second port connected to the second input / output port, and a driving port connected to the pressure control valve,
A reciprocating pressure booster having a first discharge back pressure port and two connection ports connected to the second discharge back pressure port, and a driving port for forming a back pressure in the double reciprocating pressure booster, wherein the driving port is integrally formed with the first valve body A second valve body,
A first spool operable within said first valve body,
And a second spool that operates in the second valve body and is formed integrally with the first spool. The method according to claim 1,
Wherein the pressure regulating valve includes a primary port connected to a driving port of the first valve body, a secondary port connected to the driving device for supplying a predetermined pressure, and a back pressure port connected to the secondary port, A pressure regulating valve body having a valve body;
A pressure regulating valve spool operating in the pressure regulating valve body;
And a pressure regulating pressure port for applying a predetermined pressure to the pressure regulating valve spool. The method of claim 2,
Wherein the pressure regulating pressure regulator is a spring. 2. The automatic pressure regulating regulator for a double-acting reciprocating pressure booster according to claim 1, wherein the pressure regulating pressure regulator is a spring. The method of claim 2,
Wherein the pressure regulating valve spool has two land portions connected by one spool rod portion. The method according to claim 1,
And a latch valve connected to the double-acting reciprocating pressure booster and the main control valve for actuating the spool of the main control valve according to the piston position of the double-acting type reciprocating pressure booster. Pressure control mechanism. The method of claim 5,
A latch valve body having an inlet port connected to a fluid source and a latch valve outlet port connected to the first valve body or the second valve body for applying pilot pressure;
A latch valve spool operable within said latch valve body;
And a valve operation connecting rod connected to the latch valve spool. The method of claim 6,
Wherein the latch valve outlet port communicates with a spool latch port that presses the latch valve spool to maintain the valve switching position. The method of claim 6,
Wherein the valve operation connecting rod has a pressing pin portion protruding into the first cylinder chamber or the second cylinder chamber. The method of claim 6,
Wherein the latch valve spool is moved to one side by an elastic force of the latch valve spring to maintain the pilot pressure of the main valve in the released state. The method of claim 6,
Wherein the latch valve spool is connected to the two land portions by a single spool rod portion. The method according to claim 1,
Wherein the first valve body is formed with a supply port for supplying fluid from a fluid supply source,
Wherein the second valve body is formed with a return port for returning fluid to the tank. The method of claim 11,
Wherein the return port is formed by one or two return ports. The method according to claim 1,
Wherein the first spool and the second spool include a land portion and a spool rod portion that connects the land portion and the land portion. The method according to claim 1,
Wherein the first spool is connected by three spool load portions, and the second spool is connected by one spool load portion. The automatic pressure for a double-acting reciprocating pressure booster Adjustable control mechanism.

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