KR20190022961A - Gas booster having auto-stop function and method of controlling the same - Google Patents

Abstract

A gas booster having an auto-stop function comprises a drive cylinder, a first pressure increase cylinder, a second pressure increase cylinder, a drive piston head in the drive cylinder, a first pressure increase piston head in the first pressure increase cylinder, a second pressure increase piston head in the second pressure increase cylinder, a pneumatic providing unit having a drive conversion valve enable the drive piston head to reciprocate by providing pressure air to the drive cylinder, a gas providing unit providing low pressure gas to the first pressure increase cylinder and the second pressure increase cylinder, and a gas discharge unit discharging high pressure gas from the first pressure increase cylinder and the second pressure increase cylinder.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a gas booster including an automatic shut-

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas pressure booster, and more particularly, to a gas pressure booster and an operation method thereof, in which the pressure of the gas is constantly increased or maintained at a high pressure while reciprocating the piston with pneumatic pressure.

The pressure booster includes a piston reciprocating within the cylinder and the cylinder, and moves the piston in response to the action of the pressure fluid supplied to the working chamber of the cylinder, thereby improving the pressure of the other pressure fluid in the pressure chamber corresponding to the piston .

Pressure boosters include single acting pressure boosters and double acting pressure boosters.

A single acting pressure booster is a booster which alternately repeats the inflow and outflow of pressure fluid in two cycles. The booster includes a cylinder having a drive chamber formed on one side and a booster chamber on the other side, a drive piston operating in the drive chamber, And a pressure-increasing piston.

The double acting type pressure booster is a booster which alternately repeats the inflow and outflow of the pressure fluid in one cycle. The booster includes a middle drive chamber and a cylinder in which the two pressure chambers are formed, a drive piston that operates in the drive chamber, And a piston.

This single-acting and double-acting pressure booster is disclosed in Korean Patent No. 10-1505016 (registered on Mar. 17, 2015). According to the Korean patent, the drive piston, the piston rod, and the pressure-increasing piston are integrally formed, and the integrally formed part must be accurately moved in the cylinder. Also, if the gas entering the booster chamber is too low, operating the gas booster may be inefficient, and frequent operation of the gas booster may have an effect on reducing the life of the gas booster. On the other hand, if the gas in the booster chamber or the storage tank is too high, it may not be necessary to repeatedly perform the booster process because it causes a disruption to the booster chamber or the storage tank.

However, it is not possible to find a solution to solve this problem in the similar Korean gas booster as well as Korean registered patent.

The present invention provides a gas booster capable of implementing an automatic shutoff function according to the pressure of a fluid entering and exiting a booster cylinder in controlling a gas booster, and a control method thereof.

The present invention provides a gas booster capable of automatically controlling the operation of a gas booster by using a mechanical element instead of an electrical control, and a control method thereof.

According to an exemplary embodiment of the present invention, a gas booster including an automatic shut-off function includes a drive cylinder, a first booster cylinder provided on one side of the drive cylinder, A drive piston head reciprocably provided in the drive cylinder and dividing the interior of the drive cylinder into a first drive space and a second drive space, A first pressure-increasing piston head provided in the first pressure-reducing cylinder so as to be opposed to the drive space, a second pressure-regulating piston head provided in the second pressure-regulating cylinder so as to be reciprocable in the second pressure- Pressure piston head selectively providing pressure air to a first drive space or a second drive space of the drive cylinder, And a drive switching valve mounted on a flow path for supplying pressure air to reciprocate the piston head to select a flow path connecting the first drive space or the second drive space, using a first booster check valve Pressure gas to the first pressure-increasing space of the first booster cylinder and the second booster chamber of the second booster cylinder in one direction, and a second booster chamber And a gas discharge portion for discharging the high-pressure gas in one direction.

The pressure of at least one of the second fluid supply portion and the second fluid discharge portion is out of a predetermined range, the pneumatic bypass circuit connected to the operation end of the drive switching valve is blocked, As shown in FIG.

The pneumatic bypass circuit may include a first branch flow path branched from a supply pipe of the air pressure providing section and connected to an operation end of the drive switching valve, and a second branch flow path branched again from the first branch flow path to discharge air to the outside.

In the case of the double-acting type, the driving piston head is repeatedly moved left and right. A first driving two-way valve for selectively opening and closing the second branch passage corresponding to the one end position of both ends is provided on the second branch passage Way valve for selectively opening and closing the first branch passage corresponding to the position of the drive piston head at the other end position is mounted on the first branch passage before being separated from the second branch passage, .

A first shut-off two-way valve connected to the gas supply unit and a second shut-off two-way valve connected to the gas discharge unit may be mounted on the first branch flow path after being separated from the second branch flow path. Here, the first shut-off two-way valve may block the first branch flow path if the pressure of the gas supplied from the gas supply is lower than the low-pressure setting value, and the second shut- If the pressure is higher than the high pressure setting value, the first branch passage can be shut off.

In addition, only the first blocking 2-way valve is provided to be connected to the gas supply, and the gas discharge can be configured to use another valve or other isolation device from the outside. Similarly, only a second interrupting two-way valve may be provided to couple with the gas outlet, which may also be configured externally using another valve or other interrupter.

To this end, the first shut-off two-way valve may be a spring return type two-way valve that by default blocks the second branch flow path, and the second shut-off two-way valve may be a spring return Way two-way valve. In addition to the spring return type, various types of valves can be used, and any one of them can also be used by those skilled in the art.

According to an exemplary embodiment of the present invention for achieving the objects of the present invention, a gas booster including an automatic shut-off function includes a drive cylinder including a drive piston head, a first booster piston interlocked with the drive piston head, A first fluid feeder for feeding a first fluid to move the driving piston head, a second fluid feeder for feeding a second fluid to the first pressure-increasing cylinder, and a second fluid feeder for feeding a second fluid to the second pressure- And a second fluid outlet for discharging a second fluid that has been pressurized from the first fluid outlet and the second fluid outlet. When an exception occurs in which the gas pressure in at least one of the second fluid outlet and the second fluid outlet is out of a predetermined range, Can be blocked.

The gas booster of the present invention may correspond to a single acting or double acting type. In the double acting type, the second booster cylinder is provided on the other side of the drive cylinder opposite to the first booster cylinder. The piston structure is physically coupled to the drive piston head And a second pressure-increasing piston head reciprocating within the second pressure-reducing cylinder.

If an exception occurs, the operation can be stopped by physically moving the drive piston head in only one predetermined direction in addition to the method of shutting off the power supply. In the case of simply disconnecting the power supply, there is a lot of preparation in order to restart after the cause is resolved, but there is a difference in that if the physically driven piston head moves in one direction and stops, it can be operated immediately after the cause solution.

The inside of the driving cylinder is divided into a first driving space and a second driving space by a driving piston head, and the first fluid providing portion selectively supplies the first fluid to the first driving space or the second driving space of the driving cylinder A bypass circuit connected from the supply pipe of the first fluid supply unit to the operation end of the drive switching valve, and a blocking two-way valve mounted on the bypass circuit to selectively block the bypass circuit .

The operating end of the shut-off two-way valve can be connected to the second fluid supply or second fluid discharge and can selectively block the bypass circuit in exceptional situations.

In this specification, the first fluid may be pressurized air or the like, and the second fluid may be a gas to be pressurized. Further, a range can be set so that the gas to be pressurized is out of a predetermined low pressure set value or higher and lower than a predetermined high pressure set value, and the shut-off two-way valve is provided with a second fluid feed (gas feed) And a fluid can be operatively connected to the outlet (s) to maintain a predetermined range.

For reference, 'two-way valve' in the present specification is not limited to a two-way valve but can be understood as a concept including a three-way valve, a four-way valve or other valve capable of performing a two- Way valve 'is not limited to a simple three-way valve but also a concept including a combination of two-way valves capable of functioning as a three-way valve, a four-way valve or other valves.

In this regard, the shut-off two-way valve may include a first shut-off two-way valve coupled to the second fluid supply and a second shut-off two-way valve coupled to the second fluid discharge, It may be meant that the second fluid supply or second fluid discharge is connected to the operation end and the valve is pneumatically or hydraulically connected so that the valve can be operated according to a predetermined pressure.

To this end, the first shut-off two-way valve may be a spring return type two-way valve that by default blocks the bypass circuit, and the second shut-off two-way valve is a spring return type two- There is a number.

According to an exemplary embodiment of the present invention for achieving the above-described objects of the present invention, there is provided a hydraulic control apparatus for an internal combustion engine, comprising a drive cylinder including a drive piston head, a first booster cylinder including a first booster piston head interlocked with the drive piston head, A first fluid supply for supplying a first fluid to move the drive piston head, a second fluid supply for supplying a second fluid to the first pressure-applying cylinder, and a second fluid supply unit for supplying a second fluid supplied from the second pressure- Wherein the gas booster is automatically shut off when an exception occurs in which the gas pressure of at least one of the second fluid supplier and the second fluid outlet is out of a predetermined range, .

In this embodiment, the operation of the gas booster may be blocked by allowing the drive piston head to move only in a predetermined direction when an exception occurs, and the second drive two-way valve The operation of the drive piston head can be stopped only in a predetermined direction, and the operation can be stopped until the cause is solved.

The inside of the driving cylinder is divided into the first driving space and the second driving space by the driving piston head and a driving switching valve is provided in the first fluid supplying portion to selectively supply the first driving space or the second driving space of the driving cylinder So that the driving piston head can reciprocate. Way valve for selectively blocking the bypass circuit on a bypass circuit connected from the supply pipe of the first fluid supply unit to the operation end of the drive switching valve, and the operation end of the shutdown two-way valve is connected to the second fluid supply unit 2 fluid outlet, thereby selectively blocking the bypass circuit in the exceptional situation.

Way two-way valve connected to the second fluid supply as the shut-off two-way valve and a second shut-off two-way valve connected to the second fluid discharge, wherein the first shut- May be a spring return type two-way valve for shutting off the circuit, and the second breaking two-way valve may be a spring return type two-way valve that opens the bypass circuit by default.

The gas booster of the present invention can realize an automatic shutoff function according to the pressure of the fluid entering and exiting the booster cylinder in controlling the gas booster.

The gas booster of the present invention can automatically control the operation of the gas booster by using mechanical or hydrodynamical elements instead of electrical control and can be operated again when the cause is resolved, .

1 to 3 are views for explaining an operation mechanism of a gas booster according to an embodiment of the present invention.
FIG. 4 is a diagram for explaining a control method in an exceptional situation according to the gas booster and the control method of FIG. 1; FIG.
5 and 6 are views for explaining a control method in an exceptional situation according to the gas booster and the control method of FIG.
7 is a view for explaining a control method in the exceptional situation according to the gas booster and the control method of FIG.
FIGS. 8 and 9 are views for explaining a control method in the exceptional situation according to the gas booster and the control method of FIG.
10 is a view for explaining a sectional structure of a gas booster according to an embodiment of the present invention.
11 is a view for explaining a coupling relationship between the first pressure-increasing piston head and the first piston rod in Fig.
12 is a view for explaining the engagement relationship between the first pressure-increasing piston head and the first piston rod of FIG. 10 in an exploded state;
13 is a view for explaining a cross-sectional structure for explaining a gas booster according to an embodiment of the present invention.
FIG. 14 is a view for explaining a cross section of a fluid mixture prevention structure in the gas booster of FIG. 13; FIG.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. However, the present invention is not limited to the embodiments. For reference, the same numbers in this description refer to substantially the same elements, and the contents described in the other drawings under the above-mentioned rules can be explained by quoting, and the contents which are judged to be obvious to the person skilled in the art or repeated can be omitted.

1 to 3 are views for explaining an operation mechanism of a gas booster according to an embodiment of the present invention.

1 to 3, the gas booster 100 according to the present embodiment includes a driving cylinder 110, a first booster cylinder 120 provided at one side of the driving cylinder 110, A second booster cylinder 130 provided on the other side and a second booster cylinder 130 provided to be reciprocable within the drive cylinder 110 and dividing the interior of the drive cylinder 110 into a first drive space 112 and a second drive space 114 A drive piston head 150 which is reciprocally provided within the first pressure-reducing cylinder 120 and which is provided with a first pressure-reducing cylinder 122 which is provided in the first pressure- 1 pressure-regulating piston head 160 and a second pressure-reducing cylinder 130 provided inside the second pressure-regulating cylinder 130 so as to be reciprocable within the second pressure-regulating cylinder 130 and opposed to the second driving space 114 A first pressure piston head 170, a first piston connecting the first pressure-increasing piston head 160 and the drive piston head 150, And a load (180) and the second booster piston head the second piston rod 190 connecting the unit 170 and the driving piston head 150.

The driving piston head 150 is selectively provided with the pressure air to the first driving space 112 or the second driving space 114 of the driving cylinder 110 by using the three- Of the first booster cylinder (120) and the second booster cylinder (130) of the first booster cylinder (120) using the first booster check valve (222, 224) The gas supply unit 220 for supplying the low pressure gas in one direction to the pressure increasing space 132 and the gas supplying unit 220 for supplying the low pressure gas from the first pressure increasing space 122 and the second pressure increasing space 132 using the second pressure increasing check valves 232, And a gas discharge unit 230 for discharging the high-pressure gas in one direction.

A pneumatic bypass circuit 250 is provided from the supply line of the pneumatic feeder 210 and the pneumatic bypass circuit 250 includes a first branch flow path 252 leading from the supply line to the operating end of the drive switching valve 212, And a second branch passage 254 branching from the passage 252 and discharging air to the outside.

The first driving two-way valve 214 for selectively opening and closing the second branch passage 254 corresponding to the one end position of the both ends of the driving piston head 150 is repeatedly moved to the left and right, And a second drive two-way valve 216 for selectively opening and closing the first branch passage 252 corresponding to the drive piston head 150 reaching the other end position can be mounted on the branch passage 254 And may be mounted on the first branch passage 252 before being separated from the second branch passage 254.

Further, the shutoff valve portion 240 may be provided on the first branch passage 252. Specifically, the first shut-off two-way valve 242 connected to the gas supply unit 220 and the second shut-off two-way valve 244 connected to the gas discharge unit 230 are separated from the second branch flow channel 254 The first branch passage 252 can be mounted on the first branch passage 252. Here, the first interrupting two-way valve 242 can block the first branch passage 252 when the pressure of the gas supplied from the gas supplier 220 is lower than the low-pressure set value (e.g., 0.3 to 3 bar) Way valve 244 can block the first branch passage 252 when the pressure of the gas discharged from the gas discharge portion is higher than the set high pressure.

To this end, the first shut-off two-way valve 242 may be a spring return type two-way valve which by default blocks the second branch flow path 254, and the second shut- Way valve of a spring return type which opens the first branch passage.

According to the present embodiment, the drive switching valve 212 is a spring-return type three-way valve that connects pressure air to the first drive space 112 by default, The valve is operated to connect to the second driving space 114. When the pressure is lower than a certain level at the operation end, the pressure is returned to the default position and the pressure air can be connected to the second driving space 114. [

The drive switch valve 212 is in the default position and the pressure air is supplied to the first drive space 112 to move the drive piston head 150 toward the second booster cylinder 130. [

Here, the first shut-off two-way valve 242 is in the open state when a gas pressure higher than the low-pressure set value is applied to the operation end and the second shut-off two-way valve 244 applies a gas pressure lower than the high- Is in an open state.

The second booster piston head 170 moves to the right together with the drive piston head 150 and the pressure of the second booster piston 132 is increased by the second booster piston head 170, Pressure gas can be discharged to the gas discharging part 230 through the second pressure-reducing check valve 234 connected to the high-pressure check valve 132.

At the same time, the first pressure-increasing piston head 160 is also moved to the right side to expand the first pressure-applying space 122 and the external low-pressure gas is supplied through the first pressure-check valve 222 of the gas- And may be supplied to the first pressure-increasing space 122.

Referring to FIG. 2, when the drive piston head 150 or other structure reaches a certain position while moving to the right, the second drive two-way valve 216 may be actuated. The second drive two-way valve 216 is located on the pneumatic bypass circuit 250 which bypasses the pneumatic feeder 210 supplying the pressurized air and supplies the pressurized air to the operating end of the drive switch valve 212. The second drive two-way valve 216 is a spring-return type two-way valve, which by default blocks the pneumatic bypass circuit 250 so that the pressurized air presses the operation end of the drive switch valve 212, 212, respectively.

However, the second drive two-way valve 216 may be operated by the drive piston head 150 to be switched to the open position. When the second drive two-way valve 216 is switched to the open position, the pressure is transferred to the drive switching valve 212 through the pneumatic bypass circuit 250. The pressure air is supplied to the second drive space 114, The piston head 150, the first pressure-regulating piston head 160, and the second pressure-regulating piston head 170 can all be moved in the leftward direction.

The pressure of the first pressure-increasing space 122 is increased while the first pressure-increasing piston head 160 is moved to the left side and the high-pressure gas is supplied through the second pressure-check valve 232 connected to the first pressure- And may be discharged to the gas discharge portion 230. The second pressure-regulating piston head 170 is also moved to the left so that the second pressure-regulating space 132 is expanded and the external low-pressure gas is supplied through the first pressure-check valve 224 of the gas- 2 < / RTI >

As the drive piston head 150 moves to the left, the second drive two-way valve 216 can also return to the shut off position. However, at this time, both the first drive two-way valve 214 and the second drive two-way valve 216 are shut off, so that the pressure on the operation end of the drive changeover valve 212 may not be affected.

Referring to FIG. 3, when the drive piston head 150 or other structure reaches a certain position while moving to the left, the first drive two-way valve 214 can be operated. The first drive two way valve 214 is located at the end of the pneumatic bypass circuit 250 equipped with the drive changeover valve 212 and the second drive two way valve 216. The first drive two-way valve 214 is also a spring-return type two-way valve that can block the pneumatic bypass circuit 250 by default.

However, when the driving piston head 150 moves to the left end and operates the first driving two-way valve 214, the pressure of the pneumatic bypass circuit 250 connected to the driving switching valve 212 is rapidly lowered, The pressure holding the valve 212 is lost, and the drive switching valve 212 can return to the default position.

1, pressure air begins to be supplied to the first drive space 112, and the drive piston head 150, the first pressure-regulating piston head 160, and the second pressure-regulating piston head 170, Can be moved to the right again.

The pressure of the second pressure-increasing space 132 is increased while the second pressure-regulating piston head 170 is moved to the right side and the high-pressure gas is supplied through the second pressure-check valve 234 connected to the second pressure- And may be discharged to the gas discharge portion 230. The first pressure boosting piston head 160 is moved to the right side to expand the first pressure boosting space 122 and the external low pressure gas is supplied through the first pressure boosting check valve 222 of the gas supplier 220 1 < / RTI >

FIG. 4 is a diagram for explaining a control method in an exceptional situation according to the gas booster and the control method of FIG. 1; FIG.

Referring to FIG. 4, it is assumed that the gas pressure in the gas supply unit 220 drops below the low-pressure setting value in the normal operation state as shown in FIG. 1 or FIG. The first interrupting two-way valve 242 is hydraulically connected to the gas supplier 220. When the pressure of the gas temporarily decreases, the pressure applied to the first interrupting two-way valve 242 drops, The one-way two-way valve 242 can be switched to the cut-off state which is the default.

In this case, the driving piston head 150 can move to the right by the supply of the pressurized air. However, unlike FIG. 2, even if the drive piston head 150 reaches a certain position capable of operating the second drive two-way valve 216, since the first blocked two-way valve 242 is in the blocked state The drive switching valve 212 can not be switched.

As a result, since the first shut-off two-way valve 242 is in the default cut-off state, the gas booster including the drive piston head 150 temporarily stops operating.

Of course, if the pressure of the gas supplier 220 returns to the original state, the first shut-off two-way valve 242 can be switched to the open state, and if the second drive two-way valve 216 is in the open state, The drive switching valve 212 is switched and the gas booster can start operating again.

5 and 6 are views for explaining a control method in an exceptional situation according to the gas booster and the control method of FIG.

Referring to FIGS. 5 and 6, it is assumed that the gas pressure in the gas supply unit 220 drops below the low-pressure setting value in a normal operation state as shown in FIG. As shown in FIG. 2, when the pressure of gas in the gas supplier 220 temporarily decreases during the movement of the drive piston head 150 to the left, the pressure applied to the first shut-off two-way valve 242 drops, The one-way two-way valve 242 can be switched to the cut-off state which is the default.

6, the drive switching valve 212 is switched to the default state to start supplying the pressurized air to the first pressurized space 112, and the drive piston head 150 is moved to the right by the supply of the pressurized air . 2, even if the drive piston head 150 reaches a certain position capable of operating the second drive two-way valve 216, the first interruption two-way valve 242 is in the disconnected state The drive switching valve 212 can not be switched.

7 is a view for explaining a control method in the exceptional situation according to the gas booster and the control method of FIG.

Referring to FIG. 7, it is assumed that the gas pressure in the gas discharge portion 230 is increased to a value higher than the high-pressure setting value in a normal operation state as shown in FIG. 1 or FIG. The second interrupting two-way valve 244 is hydraulically connected to the gas discharging part 230. When the pressure of the discharged gas temporarily increases, the pressure applied to the second interrupting two-way valve 244 rises , The second blocking two-way valve 244 can be switched to the blocking state.

In this case, the driving piston head 150 can move to the right by the supply of the pressurized air. However, unlike FIG. 2, even if the drive piston head 150 reaches a specific position to actuate the second drive two-way valve 216, the second blocked two-way valve 244 is in a shutdown state The drive switching valve 212 can not be switched.

As a result, since the second shut-off two-way valve 244 is in the cut-off state, the gas booster including the drive piston head 150 temporarily stops operating.

Way valve 244 can be switched to the default open state and the second drive two-way valve 216 can be switched to the open state if the pressure of the gas discharge portion 230 drops and returns to the original state The drive switching valve 212 is switched, so that the gas booster can start operating again.

FIGS. 8 and 9 are views for explaining a control method in the exceptional situation according to the gas booster and the control method of FIG.

Referring to FIGS. 8 and 9, it is assumed that the gas pressure in the gas discharge part 230 rises above the high pressure setting value in a normal operation state as shown in FIG. As shown in FIG. 2, when the pressure of the gas temporarily rises in the gas discharging part 230 during the movement of the driving piston head 150 to the left side, the pressure applied to the second blocking two-way valve 244 is raised, The two-way two-way valve 244 can be switched from the open state to the shut-off state.

9, the drive switching valve 212 is switched to the default state by the spring restoring force to start supplying the pressurized air to the first pressurized space 112, while the drive piston head 150 is driven by the supply of the pressurized air You can move to the right. 2, even if the drive piston head 150 reaches a certain position capable of operating the second drive two-way valve 216, the second blocked two-way valve 244 is in the cut-off state The drive switching valve 212 can not be switched.

10 is a view for explaining a sectional structure of a gas booster according to an embodiment of the present invention, FIG. 11 is a view for explaining a coupling relation between the first pressure-increasing piston head and the first piston rod in FIG. 10, 12 is a view for explaining the coupling relationship between the first pressure-increasing piston head and the first piston rod in Fig. 10 in a disassembled state.

10 to 12, the driving piston head 150 and the first pressure-rising piston head 160 do not form an integral body, but are connected to each other through an assembly of the first piston rod 180.

The opposite end of the first piston rod 180 is also in the same or similar manner as the drive piston head 150. In this way, And the drive piston head 150 and the second booster piston head 170 about the second piston rod 190 may be connected in the same or similar manner or structure. The description of the repetition of the same structure can be omitted.

A pivot head 182 is provided at the end of the first piston rod 180 and a pivot cup 162 may be formed in the first pressure intensifying piston head 160 in correspondence with the pivot head 182. The first piston rod 180 can pivot about the pivot head 182 while the pivot head 182 is received in the pivot cup 162. Even if the center of the shaft and the center of the cylinder do not perfectly coincide, 1 pressure-rising piston head 160 can smoothly move.

For large installations used in ships and the like, the length of the piston rod can increase from a few meters to a hundred meters. In this case, it is not easy to control the error range up to several micrometers. However, as in this embodiment, by allowing the piston rod to move relative to the piston head, it is possible to some extent solve the problem of the error in a large facility.

Referring again to the drawings, a circumferential groove 184 may be formed in the pivotal head 182 and the washer cap 164 may be coupled to the circumferential groove 184 of the pivotal head 182 such that the first piston rod 180 The pivot cup 162 can be moved freely without departing from it.

The washer cap 164 may be divided into two pieces or three or more pieces and is inserted into the circumferential groove 184 in a separated state and is respectively fixed around the pivot cup 162 to separate the first piston rod 180 1 pressure-boosting piston head 160 in the pivot cup 162. [

There are many more ways of pivotally connecting the first piston rod 180 to the first pressure-tightening piston head 160, but in one example, a pivoting head 182 is formed on either side of the first piston rod 180, A pivot cup 162 may be formed on each of the first pressure-regulating piston head 160 and the driving piston head 150 to connect them.

FIG. 13 is a sectional view for explaining a gas booster according to an embodiment of the present invention, and FIG. 14 is a view for explaining a cross section of a fluid mixture preventing structure in the gas booster of FIG.

Referring to FIG. 13, the gas booster according to the present embodiment is a quadruple-acting gas booster (BQD) having two gas chambers. In the first booster cylinder 120 and the second booster cylinder 130, two The case where the pressure increasing space is applied is shown in FIG. In this case, since the gas chamber and the air chamber are in contact with each other, a structure for preventing mixing of the fluid may be required. In this embodiment, different types of gas supplier 220 'and gas discharger 230' may be provided differently from the previous embodiment, and four check valves may be provided, respectively.

For the sake of reference, in this embodiment, the mixing prevention structure formed on the partition wall between the driving cylinder 110 and the second booster cylinder 130 is described, but the same contents are used for blocking the driving cylinder 110 and the first booster cylinder 130 In describing the structure, it can also be referred to.

14, a partition wall is provided between the driving cylinder 110 and the second booster cylinder 130, and the partition wall may be provided with a boss for allowing the second piston rod 190 to pass axially. The boss may be provided with a buffer inlet 140 for providing an inert gas to the outer surface of the second piston rod 190. A buffer outlet 145 may be formed on both sides of the buffer inlet 140, The inactive fluid or the mixture of inert gas and other gas introduced from the unit 140 can be discharged to the outside.

Accordingly, it is possible to prevent the air in the driving cylinder 110 and the gas in the second booster cylinder 130 from being mixed with each other, and eventually the gas to be subjected to the booster can be prevented from being mixed with other gases.

Specifically, the buffer inflow section 140 is connected to the buffer inflow port 142 and the buffer inflow port 142 formed in the partition wall for introducing an inert gas such as nitrogen (N ₂ ) from the outside, and is connected to the inner surface of the boss in the circumferential direction May include a formed central groove (144). The buffer outlet 145 is formed in front of and behind the buffer inlet 140 and includes a peripheral groove 148 and a peripheral groove 148 spaced apart from each other at both sides of the central groove 144 and formed circumferentially on the inner surface of the boss. And a buffer outlet 146 for discharging the gas introduced into the buffer outlet 146 to the outside.

The nitrogen (N ₂ ) introduced from the outside flows into the central groove 144 through the buffer inlet 142, and the mixing of air and gas can be primarily blocked by nitrogen. In addition, the introduced nitrogen is collected through the peripheral groove 148 and the buffer outlet 146, and can be discharged to the outside through the buffer outlet 145. Therefore, the air chamber and the gas chamber can be blocked by nitrogen.

Although the present embodiment has described a double-acting gas booster in which a booster piston head is provided on both sides with a central drive piston head, according to another embodiment of the present invention, a single-acting gas booster with one drive piston head and one booster piston head A piston rod capable of pivoting motion of the present invention can be applied.

To this end, the single acting universal gas booster may comprise a drive cylinder, a booster cylinder provided on one side of the drive cylinder, and a piston structure reciprocating within each of the cylinders. Characteristically, the piston structure may include a drive piston head, a booster piston head, and a piston rod, which may be pivotally coupled on either or both of the drive piston head and the booster piston head.

Although the present invention has been described with reference to the preferred embodiments thereof, it will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the spirit and scope of the invention as defined in the following claims. It can be understood that

100: gas booster 110: driving cylinder
120: first booster cylinder 130: second booster cylinder
140: Buffer inlet 145: Buffer outlet
150: driving piston head 160: first booster piston head
170: second booster piston head 180: first piston rod
190: second piston rod 210:
220: gas supply unit 230: gas discharge unit
240: Shut-off 2-way valve 250: Pneumatic bypass circuit

Claims (17)

Drive cylinder;
A first booster cylinder provided at one side of the drive cylinder;
A second booster cylinder provided on the other side of the drive cylinder;
A drive piston head reciprocally provided in the drive cylinder and dividing an interior of the drive cylinder into a first drive space and a second drive space;
A first booster piston reciprocally provided in the first booster cylinder and providing a first booster chamber in the first booster cylinder opposed to the first booster chamber;
A second booster piston reciprocatingly provided in the second booster cylinder and providing a second booster chamber in the second booster cylinder opposed to the second booster chamber;
Wherein the first driving space or the second driving space of the driving cylinder selectively supplies pressure air to reciprocate the driving piston head and is mounted on a flow path for supplying the pressure air, And a drive switching valve for selecting a passage connecting the second drive space;
A gas supplier for providing a low-pressure gas in one direction to the first booster chamber of the first booster cylinder and the second booster chamber of the second booster cylinder using a first booster check valve; And
And a gas discharge portion for discharging the high-pressure gas in one direction from the first pressure-increasing space and the second pressure-increasing space using a second pressure-check valve,
When an exception occurs in which the gas pressure of at least one of the second fluid supply portion and the second fluid discharge portion is out of a predetermined range, the pneumatic bypass circuit connected to the operation end of the drive switch valve is cut off, And the head is moved only in a predetermined direction. The method according to claim 1,
The pneumatic bypass circuit includes a first branch flow path branched from a supply pipe of the pneumatic pressure providing portion and connected to the operation end of the drive switching valve and a second branch flow branch branched again from the first branch flow path and discharging air to the outside In addition,
A first drive two-way valve for selectively opening and closing the second branch passage corresponding to the one end position of the drive piston head is mounted on the second branch passage,
And a second drive two-way valve for selectively opening and closing the first branch passage is mounted on the first branch passage before being separated from the second branch passage in correspondence with reaching the other end position of the drive piston head Wherein the gas booster comprises an automatic shut-off function. 3. The method of claim 2,
A first shut-off two-way valve connected to the gas supply unit is mounted on the first branch flow channel after being separated from the second branch flow channel,
Wherein the first shut-off two-way valve cuts off the first branch flow passage when the pressure of the gas supplied from the gas supply is lower than the low-pressure set value. 3. The method of claim 2,
A second shut-off two-way valve connected to the gas discharge unit is mounted on the first branch flow path after being separated from the second branch flow path,
And the second shut-off two-way valve blocks the first branch flow passage when the pressure of the gas discharged from the gas discharge portion is higher than a set high pressure. 3. The method of claim 2,
A first shut-off two-way valve connected to the gas supply unit and a second shut-off two-way valve connected to the gas discharge unit are mounted on the first branch flow channel after being separated from the second branch flow channel,
Wherein the first shut-off two-way valve cuts off the first branch flow passage when the pressure of the gas supplied from the gas supply is lower than the low-pressure set value,
And the second shut-off two-way valve blocks the first branch flow passage when the pressure of the gas discharged from the gas discharge portion is higher than a set high pressure. The method according to claim 3 or 5,
Wherein the first shut-off two-way valve is a spring return type two-way valve that blocks the second branch flow path by default. The method according to claim 4 or 5,
And the second shut-off two-way valve is a spring return type two-way valve that opens the first branch flow path by default. A drive cylinder including a drive piston head;
A first booster cylinder including a first booster piston head operatively associated with the drive piston head;
A first fluid supplier for supplying a first fluid to move the driving piston head;
A second fluid supplier for supplying a second fluid to the first booster cylinder; And
And a second fluid outlet for discharging the second fluid that has been pressurized from the second pressure-regulating cylinder,
Wherein the operation of the gas booster is automatically shut off when an exception occurs in which the gas pressure of at least one of the second fluid supplier and the second fluid outlet is out of a predetermined range. 9. The method of claim 8,
Wherein when the exception occurs, the driving piston head is moved in only one predetermined direction to block the operation. 10. The method of claim 9,
Wherein the inside of the driving cylinder is divided into a first driving space and a second driving space by the driving piston head,
Wherein the first fluid supply part includes a drive switching valve for selectively supplying the first fluid to the first drive space or the second drive space of the drive cylinder to reciprocate the drive piston head, A bypass circuit connected from the supply pipe to an operation end of the drive switching valve, and a blocking two-way valve mounted on the bypass circuit to selectively block the bypass circuit,
And an operating end of the blocking two-way valve is connected to the second fluid delivering portion or the second fluid discharging portion to selectively block the bypass circuit in the exceptional situation. . 11. The method of claim 10,
Wherein the blocking two-way valve includes at least one of a first blocking two-way valve coupled to the second fluid delivering portion and a second blocking two-way valve coupled to the second fluid ejecting portion,
The first interrupting two-way valve is a spring return type two-way valve for blocking the bypass circuit by default,
And the second shut-off two-way valve is a spring return type two-way valve that opens the bypass circuit by default. 9. The method of claim 8,
A second booster cylinder is provided on the other side of the drive cylinder opposite to the first booster cylinder and the piston structure is physically engaged with the drive piston head to reciprocate the second booster piston head reciprocating within the second booster cylinder Wherein the gas booster comprises an automatic shut-off function. A first pressure providing cylinder including a driving cylinder including a driving piston head and a first pressure-increasing piston head interlocking with the driving piston head, a first fluid supplying unit supplying a first fluid for moving the driving piston head, And a second fluid discharge portion for discharging a second fluid that has been pressurized from the second pressure-regulating cylinder, the control method comprising the steps of:
Wherein the control unit automatically stops the operation when an exception occurs in which the gas pressure of at least one of the second fluid supply unit and the second fluid discharge unit is out of a predetermined range. Way. 14. The method of claim 13,
Wherein the operation of the gas booster is interrupted by allowing the driving piston head to move only in a predetermined direction when the exception occurs. 15. The method of claim 14,
Wherein the inside of the driving cylinder is divided into a first driving space and a second driving space by the driving piston head,
A drive switching valve is provided in the first fluid supplier to selectively supply the first fluid to the first drive space or the second drive space of the drive cylinder to reciprocate the drive piston head,
Way valve for selectively blocking the bypass circuit on a bypass circuit connected from the supply pipe of the first fluid supply unit to the operation end of the drive switching valve, the operation end of the shut-off two-way valve being connected to the second fluid Wherein the bypass circuit is selectively disconnected in connection with the supply or the second fluid discharge portion, and in the exceptional condition, the bypass circuit is selectively shut off. 16. The method of claim 15,
And a second blocking two-way valve coupled to the second fluid outlet as the blocking two-way valve, and a second blocking two-way valve coupled to the second fluid outlet,
The first interrupting two-way valve is a spring return type two-way valve for blocking the bypass circuit by default,
Wherein the second shut-off two-way valve is a spring return type two-way valve that opens the bypass circuit by default. 14. The method of claim 13,
A second pressure boosting cylinder is provided on the other side of the drive cylinder opposite to the first pressure boosting cylinder, the piston structure being physically coupled to the drive piston head and reciprocating within the second pressure boosting cylinder, Wherein the gas shut-off valve is operated in a double-acting manner.

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