DE102016124636A1 - Liquefied gas compressor with a pressure-volume converter and a torque converter - Google Patents

Abstract

The present invention relates to a liquid gas compressor, and more particularly to a liquid gas compressor having a pressure-to-volume converter and a torque converter for successively compressing and storing gas, comprising: an even number of first vertical compression tubes for compressing and discharging incoming gas, a first pressure-volume Conversion means for increasing the volume, while the interior of each of the first vertical compression tubes liquid is supplied, a first hydraulic pump, a first closed pressure circuit with a first motor which drives the first hydraulic pump, and a first torque converter which controls the output torque of the first motor, second vertical compression tubes for increasing the pressure, while the interior of each of the second vertical compression tubes liquid is supplied, a second hydraulic pump and a second closed pressure circuit with a a second motor that drives the second hydraulic pump and a second torque converter that controls the output torque of the second motor.

Description

Technical part

The present invention relates to a liquid gas compressor, and more particularly to a liquid gas compressor having a pressure-volume conversion device and a torque converter for successively compressing and storing gas, comprising: an even number of first vertical compression tubes for compressing and discharging introduced gas; a first pressure-volume conversion means for increasing the volume while supplying and discharging liquid to the inner space of each of the first vertical compression tubes; a first hydraulic pump; a first closed pressure circuit having a first motor that drives the first hydraulic pump and a first torque converter that controls the output torque of the first motor; second vertical compression tubes for increasing the pressure, while the interior of each of the second vertical compression tubes liquid is supplied and discharged therefrom; a second hydraulic pump; and a second closed pressure circuit having a second motor that drives the second hydraulic pump and a second torque converter that controls the output torque of the second motor.

State of the art

A pistonless compressor for gaseous media is from the U.S. Patent No. 6652243 B2 known.

In this reciprocating compressor, the working fluid in the compressor cylinders is connected to a positive displacement machine formed as a hydraulic pump, with a control valve for controlling the inflow and outflow of the working fluid, the control valve being controlled as a function of the fluid level of the working fluid in the compressor cylinders, which is detected by means of electronic displacement measuring systems. The compressor cylinders are preferably arranged vertically to assist the outflow of working fluid from the displacer cylinder by gravity.

In such a compressor, the fluid column of the working fluid can not be accelerated by gravitational acceleration, so that the cycle speed of the compressor is limited by the gravitational acceleration.

Because of this large cycle time and long station times, such compressors have a high flow rate pulsation of the flow of the compressed medium.

If a uniform flow rate of the compressed medium is required, for example when fueling vehicles, a buffer is required, in which the compressor cylinders transport the medium. In order to achieve a high compressor performance, large cylinder dimensions of the compressor cylinders are required due to the high cycle time. The large cylinder dimensions and the buffer cause high manufacturing costs and require a large installation space. In addition, a high structural complexity is required by the electronic position measuring systems and the control valve. In addition, the large cylinder dimensions require a large amount of working fluid, resulting in high manufacturing costs and high operating costs. In order to transport the large amount of working fluid, a powerful hydraulic pump is required, which entails correspondingly high production costs and has a high noise level during operation.

From the WO 2006/034748 A1 For example, a pistonless compressor with a working fluid formed as an ionic fluid is known. A separator is provided to recover ionic fluid carried into the compressed medium from the outlet channel. The ionic fluid is supplied via a supply device in the compressor cylinder. For this purpose, a level measuring system is provided, by which the level of the working fluid in the compressor cylinders is measured, wherein when falling below a reference value by means of the supply working fluid is supplied into the compressor cylinder. In addition to the already from the U.S. Patent No. 6652243 B2 known disadvantages is with the from the WO 2006 1034748 A1 known compressor connected due to the level measuring system a high structural complexity.

In addition, typical compressors are known in which the positive displacement machine is designed as a piston engine with at least one cylinder chamber and each cylinder chamber is connected to a compressor cylinder. Here, the flow of the compressed medium is generated by a plurality of compressor cylinders, which are each connected to a cylinder chamber of the piston engine and successively and thus evenly transport the medium in the outlet channel, whereby a flow of compressed medium can be obtained with low flow rate pulsation. Such typical compressors have short station times and thus a short cycle time, whereby the cylinder dimensions of the compressor cylinder can be reduced. This results in a small structural space requirement and a low production cost. In addition, the amount of working fluid can be reduced, which also results in a low operating cost. Besides, it is it is possible to move the working fluid at about the gravitational acceleration, the reciprocating engine being adapted to be operated at a high speed. In this case, the structural complexity and the noise level for the displacement machine designed as a piston engine can be reduced even with a high compressor output.

However, in such typical compressors, due to the short cycle time in the compressor cylinders, accurate level measurement of the working fluid is no longer possible, thus no longer guaranteeing safe operation of the compressor with a sufficient amount of working fluid in the displacer cylinders.

To solve the above problems is in the Korean Patent Application No. 10-1422807 a pistonless compressor described.

As in 1 is shown, the piston-less compressor is a compressor ( 1 ) for compressing gaseous media; the compressor has one or more compressor cylinders ( 4a ; 4b ; 4c ; 4d ; 4e ) with an inlet channel ( 6 ) and an outlet channel ( 7 ) are connected to a medium; in the compressor cylinders ( 4a ; 4b ; 4c ; 4d ; 4e ) is a working fluid formed as an ionic fluid ( 5 ); the compressor cylinders act with a positive displacement machine ( 2 ) together; the displacement machine ( 2 ) as a piston engine with multiple cylinder chambers ( 2a ; 2 B ; 2c ; 2d ; 2e ), wherein each of the cylinder chambers ( 2a ; 2 B ; 2c ; 2d ; 2e ) with compressor cylinders ( 4a ; 4b ; 4c ; 4d ; 4e ) cooperates.

Furthermore, in order to provide a compressor in which reliable operation is ensured with a low structural outlay, it is provided in the invention that the outlet duct (FIG. 7 ) of the compressor ( 1 ) a separating device ( 8th ) for working fluid ( 5 ), wherein the separating device ( 8th ) for the return of the working fluid ( 5 ) with the inlet channel ( 6 ) of the compressor ( 1 ) connected is.

However, such a reciprocating compressor does not have a piston between the working fluid and gaseous media, so that the working fluid directly contacts with gas and gas is absorbed by the working fluid that falls only by gravity. Therefore, the piston-less compressor is not suitable for a compacting apparatus because the cycle time for the compacting operation is quite long due to acceleration by gravity, causing a low compression efficiency.

Further, there are problems in that a working fluid separator and a return device are required because gas comes into direct contact with the working fluid so that working fluid is contained in the gas and transported with the gas, the working fluid is ionized to prevent the separation of gas and gas To allow working fluid, and the manufacturing costs are high due to a complex structure, such as a installed in a storage container of the working fluid level measuring system, high.

Further, ionized working fluid is separated by a high-speed rotary motion of a rotating radial distributor, breaking the ionic character of the ionized fluid, rapidly destroying the ionization, and increasing the volume of the working fluid contained in and transported by the gas, and that by gravity dropped working fluid absorbs gas, so a standby gas compressor should be installed on an inlet shear to increase the compression efficiency. Therefore, noises and heat are generated, so that no advantages can be found in a comparison with a conventional compressor.

In addition, although there is a five-stage compression cylinder, the working fluid is sequentially distributed by a cylinder via a rotary distributor, so that a compression operation of another cylinder begins after the compression operation of a cylinder is completed. Therefore, there are problems in that the compression efficiency is low and the manufacturing cost is high due to many and complicated cylinders.

To solve such problems is further in the Korean Patent Application No. 10-1559108 a pistonless compressor described.

As in 2 1, the rodless cylinder gasification apparatus is constructed with: a rodless cylinder ( 110 ), the inside of which is shaped like an empty cylinder, wherein gas is supplied to one end via a gas supply line (GSL), a gas supply opening ( 111 ) and a gas outlet ( 112 ) are each designed to dispense the gas via a gas outlet line (GOL), a fluid outlet ( 113 ), which is connected to a working fluid line (OL) is arranged at another end, a piston ( 114 ) is raised and lowered by working fluid, thereby forcibly absorbing gas to a vacuum state for compression; a hydraulic pump ( 120 ) for supplying working fluid to the fluid outlet ( 113 ) of the rodless cylinder ( 110 ) via the working fluid line (OL) and for compressing gas in the rodless cylinder ( 110 ); a gas storage tank ( 130 ) for storing gas in the rodless cylinder ( 110 ) and via the gas outlet ( 112 ) and the Gas outlet (GOL) is issued; one in the gas storage tank ( 130 ) or in the gas supply line (GSL) installed pressure sensor (PS) for measuring the internal pressure of the gas storage container ( 130 ) and the internal pressure of the gas supply line (GSL); a position sensor (LS), which in an upper and in a lower portion of each rodless cylinder (LS) 110 ) is installed, for measuring a position of the piston ( 114 ); and a control unit ( 140 ) for controlling the operation of each hydraulic pump ( 120 ) in accordance with the piston position detected by the position sensor (LS) after the operation of the hydraulic pump ( 120 ), when the internal pressure of the gas storage tank ( 130 ) is measured by the pressure sensor (PS) and it is determined that the accumulator pressure is lower than a reference pressure.

However, there are problems in that the rodless cylinder gasification apparatus is damaged due to the piston being worn during the upward and downward movement because the piston is closely fitted to the inner wall of the compression cylinder to allow direct contact between the working fluid and the gas thereby causing the working fluid and the gas to come into contact with each other, and a friction loss is maintained because the piston is actually present although it has no piston rod shape.

In addition, there is another problem that a hydraulic pump suction pipe for the working fluid in the rodless cylinder gasification apparatus is directly connected to the lower portion of the compression cylinder and, due to the worn rodless piston, supplies gas to the hydraulic pump, thereby interrupting the operation of the hydraulic pump.

Another problem is that although the position sensor for detecting up and down movement of the piston is disposed in the compression cylinder of the rodless cylinder gasification apparatus, the piston is not moved when gas is leaked due to the worn piston, thereby interrupting operation of the apparatus becomes.

State of the art

References

• (Patent Reference 1) Korean Patent No. 10-1422807
• (Patent Reference 2) Korean Patent No. 10-1559108

Brief description of the invention

Technical problem

It is an object of the present invention to solve the above problems and to provide a liquid gas compressor, and more particularly a liquid gas compressor having a pressure-volume conversion means and a torque converter for successively compressing and storing gas, comprising: an even number of first vertical pipes for compression and discharge of incoming gas; a first pressure-volume conversion means for increasing the volume while supplying and discharging liquid to the inner space of each of the first vertical compression tubes; a first hydraulic pump; a first closed pressure circuit having a first motor that drives the first hydraulic pump and a first torque converter that controls the output torque of the first motor; second vertical compression tubes for increasing the pressure, while the interior of each of the second vertical compression tubes liquid is supplied and discharged therefrom; a second hydraulic pump; and a second closed pressure circuit having a second motor that drives the second hydraulic pump and a second torque converter that controls the output torque of the second motor.

Technical solution

In order to achieve the above objects, the present invention provides a liquid gas compressor having a pressure-volume conversion device and a torque converter, comprising: a first closed pressure circuit for outputting gas via a first gas outlet pipe by forcibly absorbing and compressing gas up to one Vacuum state while pressurized liquid supplied and discharged via a first pressurized liquid line is raised and lowered by gas supplied via a first gas supply line and pressurizing pressurized fluid by working oil supplied and discharged via a first working oil passage; a buffer tank for temporarily storing pressurized gas discharged via the first gas exhaust pipe; a second closed pressure circuit for outputting gas via a second gas outlet tube by forcibly absorbing and compressing gas to a vacuum state, while pressurized fluid supplied and discharged via a first pressure fluid line is raised and lowered by gas supplied from the intermediate reservoir via a second gas supply line , And for pressurizing pressurized fluid by working oil, via a second working oil line is supplied and discharged; a main storage tank for storing compressed gas discharged via the second gas discharge pipe; and a control unit for storing pressurized gas in the main storage tank and controlling the operation of the first and second closed pressure circuits by checking the pressure of gas flowing toward the first closed pressure circuit and the second closed pressure circuit when the gas pressure of the gas stored in the main storage tank falls below the reference pressure.

Here, the LPG compressor with the pressure-volume conversion device and the torque converter further comprises a working oil tank for supplying working oil to the first closed pressure circuit and the second closed pressure circuit and for storing working oil, which is output from the first closed pressure circuit and the second closed pressure circuit.

Here, the first closed pressure circuit comprises: one or more pairs of first vertical compression tubes whose interior is empty and round, wherein one end of each tube is supplied with gas via the first gas supply line, a first gas supply opening and a first gas outlet for discharging gas over the first first gas outlet line are installed, a first pressure fluid line connected to the first pressure fluid outlet is formed at the other end, and forcibly absorbed in the tube interior by raising and lowering the pressure fluid gas and compressed to a vacuum state; a first pressure-volume conversion means having an empty round inner space for storing pressurized fluid, having a first body at both ends of which a second pressure fluid outlet connected to each of the first pressure fluid conduits is formed; a second body for storing working oil due to a diameter smaller than that of the first body, wherein at both ends of the second body, a first working oil outlet is formed, which is connected to each of the first working oil lines; and a first bidirectional piston installed between the first body and the second body for compressing and discharging pressurized fluid with working oil; a first solenoid valve connected to each of the first working oil passages for moving the first bidirectional piston of the first pressure-volume conversion device by changing the flow path of the working oil according to the control of the control unit; one or more first hydraulic pumps installed in the first working oil line, pressurizing the working oil from the working oil tank and supplying it to the first working oil line; a first motor for providing a rotational force to the first hydraulic pump; a first pressure sensor installed on the first working oil pipe for measuring the pressure of the working oil and supplying the measured pressure value to the control unit; and a first torque converter installed on the first working oil passage for converting the rotational speed and the torque of the first hydraulic pump according to the control of the control unit.

Here, in the first pressure-volume conversion means, the diameter of both ends of the first bi-directional piston is set in accordance with the gas pressure of the gas flowing into the first gas supply pipe so that the gas compression amount is increased by supplying a large volume of hydraulic fluid when the gas flows out of the first gas supply pipe , and the first pressure-volume conversion means supplies pressure fluid to the first vertical compression tubes by causing the volume of the pressure fluid to be larger than that of the working oil in using the pressure of the first hydraulic pump to pressurize the pressure fluid the first pressure-volume conversion device.

Here, the second closed pressure circuit comprises: one or more pairs of second vertical compression tubes whose interior is empty and round, one end of the tubes being supplied with gas via the second gas supply line, a second gas supply opening, and a second gas outlet, respectively, for discharging gas over them second gas outlet line are installed, a second pressure fluid line connected to the second pressure fluid outlet is formed at the other end, and forcibly absorbed in the tube interior by raising and lowering the pressure fluid gas and compressed to a vacuum state; a second pressure-volume conversion means having an empty round interior for storing pressurized fluid having a third body at both ends of which is formed the second pressurized fluid exit connected to each of the second pressurized fluid conduits; a fourth body for storing working oil due to a diameter larger than that of the third body to increase the pressure of the pressurized fluid in the third body, at both ends of the fourth body being formed a second working oil port connected to each of the second working oil passages; a second bidirectional piston installed between the third body and the fourth body for compressing and discharging pressurized fluid with working oil; a second solenoid valve connected to each of the second working oil lines for moving the second bidirectional piston of the second pressure-volume conversion device by changing the flow path of the working oil according to the control of Control unit; one or more second hydraulic pumps installed on the second working oil line and pressurizing working oil of the working oil tank and supplying the second working oil line; a second motor for providing a rotational force to the second hydraulic pump; a second pressure sensor installed on the second working oil passage for measuring the pressure of the working oil and for supplying the pressure value to the control unit; and a second torque converter installed in the second working oil passage for converting the rotational speed and the torque of the second hydraulic pump according to the control of the control unit.

Here, in the second pressure-volume conversion means, the diameter of both ends of the second bi-directional piston is set in accordance with the gas pressure supplied to the second gas supply line to increase the pressure of the compressed gas by supplying high-pressure pressurized fluid when gas from the second gas supply line flows, and the second pressure-volume conversion device supplies pressure fluid to the second vertical compression tubes at a pressure which is higher than the delivery pressure of the second hydraulic pump, while pressure fluid is pressurized by the second hydraulic pump.

Here, the volume of the first body of the first pressure-volume conversion means and the third body of the second pressure-volume conversion device is configured so that no overflow occurs when the first vertical compression tube or the second vertical compression tube pressure fluid is supplied.

Here, the first and second hydraulic fluid line, the first and the second working oil line and the working oil tank each have a radiator for cooling.

Here, by detecting the moving position of the first bi-directional piston of the first pressure-volume conversion device or the second bi-directional piston of the second pressure-volume conversion device by operating oil pressure detected by the first pressure sensor or the second pressure sensor, the control unit causes the first solenoid valve or the second solenoid valve is moved to a predetermined position, thereby changing the flow path of the first solenoid valve or the second solenoid valve.

Here, the first gas supply line, the intermediate storage tank and the main storage tank on third to fifth pressure sensors.

Here, the first vertical compression tubes and the second vertical compression tube are closed tubes.

Advantageous effects

According to the liquid gas compressor according to the present invention having a pressure-volume conversion device and a torque converter having the configuration described above, when after the first compression operation, a large volume of gas supplied sequentially from the first closed pressure circuit which increases the volume is output Gas is discharged and stored in the second closed pressure circuit after the second compression operation, thereby allowing a large amount of gas having 7 to 10 times the volume of a hydraulic pump to be compressed and compressed to a pressure of 7 to 10 times higher than the pressure of the hydraulic pump.

Since according to the present invention, no mechanical drive device is present and gas is compressed only by a reciprocating motion of a cylinder, there is no mechanical friction or heat. In addition, since gas is compressed using a vertical compacting tube, manufacturing and maintenance costs can be reduced.

Further, according to the present invention, a fixed amount of discharged gas can be obtained by installing a torque converter on the hydraulic pump and automatically increasing the rotational speed of the hydraulic pump according to the setting of the gas inlet pressure.

Further, the present invention enables the configuration of a closed pressure circuit by completely separating a gas pipe and a working oil pipe, and the configuration of a closed vertical compression pipe by completely separating electronic devices such as a hydraulic motor and a solenoid valve. Thus, the manufacturing costs can be reduced and a gas safety system can be set up.

In addition, according to the present invention, the purity of the compressed gas is increased by completely separating a pressure fluid tube and a working oil tube and selecting a chemically and physically safe pressure fluid to be supplied to the vertical compression tube. Further, because no unnecessary working oil or oil is mixed, there is no need to use an oil separator and filter, so that the manufacturing and maintenance costs can be reduced.

Description of the drawings

1 Fig. 10 is a diagram showing the structure of a gas compressor without conventional pistons;

2 shows a diagram illustrating the structure of a gas compressor with a conventional rodless cylinder;

3 FIG. 12 is a diagram showing the structure of a liquid gas compressor having a pressure-volume conversion device and a torque converter according to the present invention; FIG.

4 and 5 10 are diagrams for explaining the operation of the liquid gas compressor having a pressure-volume conversion device and a torque converter according to the present invention;

6 FIG. 12 is a graph showing the volume increase rate of pressurized fluid according to the diameter ratio of a cylinder in a first closed pressure circuit according to the present invention; FIG.

7 FIG. 12 is a graph showing the volume increase rate of pressurized fluid according to the diameter ratio of a cylinder in a second closed pressure circuit according to the present invention; FIG. and

8th FIG. 12 is a graph showing a correlation between a flow ratio, a torque ratio and the rotational speed of a hydraulic pump in the present invention. FIG.

Description of the Preferred Embodiments

Hereinafter, the configuration of a liquid gas compressor having a pressure-volume conversion device and a torque converter according to the present invention will be described in detail with reference to the accompanying drawings.

In the following description of the present invention, a detailed description of known integrated functions and configurations will be omitted insofar as they were included, the subject matter of the present invention would become unclear. In addition, the terms used in the following description are defined in terms of the functions provided in the present invention. The definitions of these terms should be understood on the basis of the entire contents of this specification, as they may be changed in accordance with the option of a user or operator or common practice.

3 FIG. 12 is a diagram showing the structure of a liquid gas compressor having a pressure-volume conversion device and a torque converter according to the present invention. FIG.

According to 3 there is a liquid gas compressor with a pressure-volume converter and a torque converter 200 according to the present invention from a first closed pressure circuit 210 , a temporary storage container 220 , a second closed pressure circuit 230 , a main storage container 240 , a working oil container 250 and a control unit 260 ,

The first closed pressure circuit 210 has a first vertical compression tube 211 , a first pressure-volume conversion device 212 , a first solenoid valve SV1, a first hydraulic pump P1, a first hydraulic motor M1, a first pressure sensor PS1 and a first torque converter 213 on.

There are one or more pairs of first vertical compression tubes 211 installed, wherein the interior of each tube is empty and round, wherein one end of each tube is supplied with gas via a first gas supply line L1, a first gas supply opening 211 and a first gas outlet 211b are each installed to output gas via a first gas outlet line L2, a first pressure fluid outlet connected to a first pressure fluid line L3 211c is formed at another end of the pipe, and inside the pipe by forcibly absorbing and compressing gas to a vacuum state by raising and lowering pressurized liquid (such as water). Here is the first vertical compression tube 211 a closed pipe so that the first gas supply pipe L1, the first gas exhaust pipe L2, and a first working oil pipe L4 are completely separated and allowed to form a general electric device, not an explosion-proof electrical apparatus, by supplying a first solenoid valve SV1 with power , the first hydraulic pump P1 and the first hydraulic motor M1 are disconnected.

The first pressure-volume conversion device 212 having an empty round interior for storing pressurized fluid, comprises: a first body 212b at both ends of which is connected to each of the first hydraulic fluid lines L3 second hydraulic fluid output 212a is formed a second body 212d for storing working oil due to a diameter smaller than that of the first body 212b , and at both ends thereof a first connected to each of the first working oil lines L4 Working oil output 212c is formed, and one between the first body 212b and the second body 212d arranged first bidirectional piston 212e for compressing and dispensing pressurized fluid by working oil. Here, in the first pressure-volume conversion device 212 the diameter of the two ends of the first bidirectional piston 212e is set according to the gas pressure supplied to the first gas supply line L1 such that the gas compression amount is increased by supplying a large volume of pressurized fluid when gas is supplied from the first gas supply line L1, and the first pressure-volume conversion device leads to the first vertical compression tube 211 pressurizing fluid by using pressure of the first hydraulic pump P1 by causing the volume of the pressurized fluid to be larger than that of the working oil in the first pressure-to-volume converter 212 while the first hydraulic pump P1 pressurizes the hydraulic fluid. Further, the volume of the first body 212b the first pressure-volume conversion device 212 configured so that no overflow occurs when the first vertical compression tube 211 Pressure fluid is supplied.

The first solenoid valve SV1 is connected to each of the first working oil lines L4 to cause the first bi-directional piston 212e by changing the flow path of the working oil according to the control of the control unit 260 and then supplying and discharging working oil to each of the first working oil outlets 212c that in the second body 212d the first pressure-volume conversion device 212 are formed, reciprocated.

At least one or more first hydraulic pumps P1 are installed on the first working oil line L4 and set the working oil from the working oil tank 250 under pressure and supply the pressurized working oil to the first working oil line L4.

The first motor M1 transmits a rotational force to the first hydraulic pump P1. The first pressure sensor PS1 installed on the first working oil line L4 measures the pressure of the working oil and guides the measured pressure value of the control unit 260 to.

The first torque converter installed on the first hydraulic pump 213 converts a speed and a torque.

Further, the temporary storage container stores 220 temporarily compressed gas (with a pressure of more than about 40 kgf / cm ² ), which is output via the first gas outlet line L2.

Furthermore, the second closed pressure circuit 230 a second vertical compression tube 231 , a second pressure-volume conversion device 232 , a second solenoid valve SV2, a second hydraulic pump P2, a second motor M2, a second pressure sensor PS2 and a second torque converter 233 on.

There are one or more pairs of second vertical compression tubes 231 installed, wherein the interior of each tube is empty and round, one end of each tube is supplied via a second gas supply line L5 gas, a second gas supply opening 231 and a second gas outlet 231b are each installed to dispense gas via a second gas outlet line L6, a third pressure fluid outlet connected to a second pressure fluid line L7 231c is formed at another end of the tube, and forcibly absorbed in the interior of the tube by raising and lowering the pressurized liquid and compressed to a vacuum state. Here is the second vertical compression tube 231 is formed as a closed tube, whereby the second gas supply line L5, the second gas outlet line L6 and a second working oil line L8 are completely separated and allowed to construct a general electric device, no explosion-proof device by a second solenoid valve SV2, the power is supplied, the second hydraulic pump P2 and the second motor M2 are disconnected.

The second pressure-volume conversion device 232 , which has an empty round interior for storing pressurized fluid, comprises: a third body 232b at the two ends of which is connected to each of the second hydraulic fluid lines L7 fourth hydraulic fluid output 232a is formed, a fourth body 232d for storing working oil due to a diameter larger than that of the third body 232b to the pressure of the pressure fluid in the third body 232b to increase, the fourth body at both ends a second working oil outlet 232c which are connected to each of the second working oil lines L8, and one between the third body 232b and the fourth body 232d installed second bidirectional piston 232e for compressing and dispensing pressurized fluid by working oil. Here, in the second pressure-volume conversion device 232 the diameter of the two ends of the second bidirectional piston 232e is set according to the gas pressure supplied to the second gas supply line L5 to increase the pressure of the compressed gas by supplying high-pressure pressurized fluid when gas is supplied from the second gas supply line L5, and the second pressure-volume conversion device leads to the second vertical compression tube 231 Pressurized fluid with one pressure, is higher than the delivery pressure of the second hydraulic pump P2, while the hydraulic pump P2 pressurizes the hydraulic fluid. Further, the volume of the third body 232b the second pressure-volume conversion device 232 configured so that no overflow occurs when the second vertical compression tube 231 Pressure fluid is supplied.

The second solenoid valve SV2 is connected to each of the second working oil lines L8 to cause the second bi-directional piston 232e the second pressure-volume conversion device 232 by changing the flow path of working oil in accordance with the control of the control unit 260 is moved back and forth.

On the second working oil line L8, at least one or more second hydraulic pumps P2 are installed, which are the working oil from the working oil tank to be supplied to the second working oil line L8 250 put under pressure.

The second motor M2 supplies a rotational force to the second hydraulic pump P2.

The second pressure sensor PS2 installed on the second working oil line L8 measures the pressure of the working oil and guides the control unit 260 the measured pressure value too.

The second torque converter installed on the second working oil line L8 233 converts a torque by changing the rotational speed of the second hydraulic motor M2 according to the control of the control unit 260 based on the detected by the second pressure sensor PS2 pressure value.

Further, the main storage container stores 240 temporarily compressed gas discharged through the second gas outlet pipe L6 (at a pressure of more than 250 kgf / cm ² with respect to natural gas or more than 800 kgf / cm ² with respect to hydrogen gas).

Furthermore, the working oil tank leads 250 the first closed pressure circuit 210 and the second closed pressure circuit 230 Working oil and save working oil from the first closed pressure circuit 210 and the second closed pressure circuit 230 is issued.

Further, when the pressure of the main storage tank 240 stored gas falls below a reference pressure (for example, about 200 kgf / cm ² with respect to natural gas or about 750 kgf / cm ² with respect to hydrogen gas), by the control unit 260 caused by operating the first and second closed pressure circuit 210 . 230 Compressed gas in the main storage tank 240 is stored, wherein the torque of the torque converter and thus the pressure of the working oil by measuring the pressure of the first closed pressure circuit 210 and the second closed pressure circuit 230 supplied gas pressure is controlled. At this time, the control unit causes 260 by detecting the moving position of the first bidirectional piston moved by the pressure of the working oil 212e the first print volume conversion device 212 or the second bidirectional piston 232e the second pressure volume conversion device 232 detected by the first pressure sensor PS1 or the second pressure sensor PS2, the first solenoid valve SV1 or the second solenoid valve SV2 is moved to a predetermined position to change the flow path of the first solenoid valve SV1 or the second solenoid valve SV2.

In the liquid gas compressor according to the invention with a pressure-volume converter and a torque converter, a first and a second hydraulic fluid line L3, L7, a first and a second working oil line L4, L8 and the working oil tank 250 each having a radiator C for cooling, first and second gas supply lines L1, L5 and first and second gas outlet lines L2, L6 have a check valve CV for preventing backflow of gas, and have the first gas supply line L1, the buffer tank 220 and the main storage tank 240 third to fifth pressure sensors PS3 ~ 5 for measuring a gas pressure.

Hereinafter, operations of the liquid gas compressor according to the present invention having a pressure-volume conversion device and a torque converter will be described in detail with reference to the accompanying drawings.

The 4 and 5 10 are diagrams for explaining the operation of the liquid gas compressor according to the present invention having a pressure-volume conversion device and a torque converter. 6 FIG. 12 is a graph showing the volume increase rate of pressurized fluid according to the diameter ratio of a cylinder in a first closed pressure circuit according to the present invention. FIG. 7 FIG. 12 is a graph showing the volume increase rate of pressurized fluid according to the diameter ratio of a cylinder in a second closed pressure circuit according to the present invention. FIG. 8th FIG. 10 is a graph showing a correlation between the flow ratio, the torque ratio and the rotational speeds of a hydraulic pump in the present invention. FIG.

While the first solenoid valve SV1 according to the control of the control unit 260 is switched, the working oil on the first working oil line L4 and the first working oil outlet 212c that in the second body 212d the first pressure-volume conversion device 212 are provided, repeatedly supplied and removed, whereby the first bidirectional piston 212e is moved back and forth.

At this time, the first hydraulic pump P1, the first motor M1 and the first torque converter 213 according to the control of the control unit 260 operated, the control unit turns off 260 the first solenoid valve SV1 by detecting the position of the first bi-directional piston 212e by means of the pressure detected by the first pressure sensor PS1, and the rotational speed of the first motor M1 becomes in accordance with the pressure of the first torque converter 213 controlled, whereby the torque is converted. Ie, as in 8th is shown, when the pressure of the working oil is high and the flow decreases, increases the control unit 260 the torque by the rotational speed of the first hydraulic pump P1 passing through the first torque converter 213 was reduced, thereby pressurizing working oil and the first bidirectional piston 212e is moved. Then, the pressure fluid is under constant pressure, causing gas to be compressed at a constant pressure.

When the first bidirectional piston 212e moving forward becomes the one in the first body 212b stored pressure fluid to the interior of the vertical compression tube via the second pressure fluid outlet 212a , the first hydraulic fluid line L3 and the first hydraulic fluid outlet 211c of the first vertical compression tube 211 feeding and raising, whereby gas is compressed in the tube interior (for example, the gas is compressed to about 4 kgf / cm ² more than about 40 kgf / cm ² relative to natural gas), and the compressed gas is passed over the first gas outlet 211b and the first gas outlet line L2 in the buffer tank 220 saved. Here, the amount of the pressure fluid is configured to be supplied without being in the first vertical compression tube 211 an overflow occurs.

Ie, as in 6 is shown, the volume of the pressure fluid of the first body 212b becomes proportional to the diameter ratio of the first bidirectional piston 212e (Diameter ratio of the hydraulic fluid and the working oil) increased, whereby it is possible to compress a large volume of gas at once.

Further, when the first bi-directional piston 212e moving backwards, in the first body 212b stored pressure fluid via the first fluid outlet 211c of the adjacent first vertical compression tube 211 fed to the interior of the tube and raised. When the pressure fluid is raised, gas is recompressed and discharged.

The in the storage tank 220 stored first compressed gas is discharged into the second gas supply line L5, whereby it alternatively further second vertical compression tubes 231 for a compression is supplied.

That is, while the second solenoid valve SV2 according to the control of the control unit 260 is switched, the working oil is repeated via the second working oil line L8 and the second working oil outlet 232c fed and discharged in the fourth body 232d the second pressure-volume conversion device 232 are provided, whereby the second bidirectional piston ( 232e ) is moved back and forth.

At this time, the second hydraulic pump P2, the second hydraulic motor M2 and the second torque converter 233 according to the control of the control unit 260 operated, the control unit turns off 260 the second solenoid valve SV2 by detecting the position of the second bidirectional piston 232e by pressure detected by the second pressure sensor PS2, and the rotational speed of the second motor M2 according to the pressure of the second torque converter 233 controlled, whereby the torque is converted. Ie, as in 8th is shown, when the pressure of the working oil is high and the flow decreases, increases the control unit 260 the torque over the speed of the second hydraulic pump P2 passing through the second torque converter 233 was reduced, thereby pressurizing working oil and the second bidirectional piston 232e is moved. Then, the pressure fluid is under constant pressure, causing gas to be compressed at a constant pressure.

If the second bidirectional piston 232e moving forward becomes the third body 232b stored hydraulic fluid via the fourth hydraulic fluid outlet 232a , the second hydraulic fluid line L7 and the third hydraulic fluid outlet 231c the interior of the second vertical compression tube 231 feeding and raising, whereby gas in the interior of the tube is compressed (for example, the gas is compressed to about 40 kgf / cm ^{2 of} gas more than about 250 kgf / cm ^{2 in} terms of natural gas), and the compressed gas is passed through the second gas outlet 231b and the second gas outlet pipe L6 in the main storage tank 240 saved. Here, the amount of the hydraulic fluid is configured to be the second vertical compression tube 231 is supplied without an overflow occurs.

Ie, as in 7 is shown, the volume of the pressure fluid of the third body 232b becomes proportional to the diameter ratio of the second bidirectional piston 232e (Diameter ratio of hydraulic fluid and working oil) increased so that it is extremely high compressible (for example, to more than 3000 kgf / cm ² ).

Further, when the second bidirectional piston becomes 232e moves backwards, those in the third body 232b stored hydraulic fluid via the third hydraulic fluid outlet 231c the adjacent second vertical compression tube 231 fed to the interior of the tube. The pressure fluid is from the second vertical compression tube 231 output.

Then, because the interior of the second vertical compression tube 231 is changed to a vacuum state, gas in the second supply line L5 via the second gas supply opening 231 fed to the interior of the tube. When the pressure fluid is raised again, gas is compressed and discharged.

Although preferred embodiments of the present invention have been presented by way of illustration, it will be apparent to those skilled in the art that various modifications, additions and substitutions are possible within the scope of the invention as defined in the appended claims.

Industrial applicability

By the gas compression according to the present invention, working fluid and gas do not directly contact each other, so that the invention is applied to the compression of all kinds of gas, not only flammable gas, such as hydrogen, natural gas, etc., but also for breathing air.

LIST OF REFERENCE NUMBERS

210, 220

first and second closed pressure circuit

230

 Intermediate storage container

240

 Main storage tank

250

 Working oil tank

260

 control unit

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 6652243 B2 [0002, 0007]
• WO 2006/034748 A1 [0007]
• WO 20061034748 A1 [0007]
• KR 10-1422807 [0010]
• KR 10-1559108 [0017]

Claims (11)

 A liquid gas compressor having a pressure-to-volume converter and a torque converter, comprising: a first closed pressure circuit for outputting gas via a first gas outlet tube by forcibly absorbing and compressing gas to a vacuum state, while pressurized fluid supplied and discharged via a first pressure fluid line is supplied by gas supplied via a first gas supply line; is raised and lowered, and for pressurizing pressurized fluid by working oil, which is supplied and discharged via a first working oil line; a buffer tank for buffering compressed gas discharged via the first gas exhaust pipe; a second closed pressure circuit for outputting gas via a second gas outlet tube by forcibly absorbing and compressing gas to a vacuum state, while pressure fluid supplied and discharged via a first pressure fluid line is supplied by gas supplied from the intermediate reservoir via a second gas supply line; is raised and lowered, and for pressurizing pressurized fluid by working oil, which is supplied and discharged via a second working oil line; a main storage tank for storing compressed gas discharged via the second gas discharge pipe; and a control unit for storing compressed gas in the main storage tank and controlling the torque of the first and second hydraulic pumps in accordance with the pressure of gas compressed in the first closed pressure circuit and the second closed pressure circuit when the pressure of the gas stored in the main storage tank is below a reference pressure decreases.  The compressor of claim 1, further comprising a working oil tank for supplying working oil to the first closed pressure circuit and the second closed pressure circuit and storing working oil discharged from the first closed pressure circuit and the second closed pressure circuit.  The compressor of claim 2, wherein the first closed pressure circuit comprises: one or more pairs of first vertical compression tubes, wherein the interior of the tubes is empty and round, with gas supplied to one end of each tube via the first gas supply line, a first gas supply port and a first gas outlet, respectively, for discharging gas via the first gas outlet line, a first pressure fluid outlet connected to a first pressure fluid line is formed at the other end of each tube, and in the interior of each tube, gas is forcibly absorbed by raising and lowering the pressure fluid and compressed to a vacuum state; a first pressure-volume conversion means having an empty round interior for storing pressurized fluid, having a first body at both ends of which a second pressurized fluid exit connected to each of the first pressurized fluid conduits is formed, a second body for storing working oil due to a diameter smaller than that of the first body, wherein at both ends of the second body, a first working oil outlet connected to each of the first working oil passages is formed, and a first bidirectional piston installed between the first body and the second body for compressing and discharging pressurized fluid by working oil ; a first solenoid valve connected to each of the first working oil lines for moving the first bi-directional piston of the first pressure-volume conversion device by changing the flow path of the working oil according to the control by the control unit; at least one or more first hydraulic pumps installed on the first working oil pipe for pressurizing working oil from the working oil tank and supplying the working oil to the first working oil pipe; a first motor for providing a rotational force to the first hydraulic pump; a first pressure sensor installed on the first working oil pipe for measuring the pressure of the working oil and supplying the measured pressure value to the control unit; and a first torque converter installed on the first working oil passage for converting the rotational speed and the torque of the first hydraulic pump according to the control of the control unit.  The compressor according to claim 3, wherein in the first pressure-volume conversion means, the diameter of both ends of the first bi-directional piston is set in accordance with the gas pressure supplied to the first gas supply line to increase the gas compression amount by supplying a large volume of pressurized fluid when gas from the first one Gas supply line is supplied, and wherein the first pressure-volume conversion means the first vertical compression tube pressure fluid supplied by the volume of the pressure fluid in the first pressure-volume conversion device using the pressure of the first hydraulic pump is made larger than that of the working oil, while the first hydraulic pump pressurizes the hydraulic fluid. The compressor of claim 3, wherein the second closed pressure circuit comprises: one or more Pairs of second vertical compression tubes, wherein the interior of the tubes is empty and round, wherein one end of each tube via the second gas supply line gas is supplied, a second gas supply opening and a second gas outlet for discharging gas via the second gas outlet line are installed, one with a second Pressure fluid line connected second pressure fluid outlet is formed at another end of each tube, and forcibly absorbed in the interior of each tube by raising and lowering the pressure fluid gas and compressed to a vacuum state; a second pressure-volume conversion means having an empty round inner space for storing pressurized liquid having a third body at both ends of which the second pressurized liquid exit connected to each of the second pressurized liquid conduits is formed; a fourth body for storing working oil due to a diameter; is larger than that of the third body to increase the pressure of the pressurized fluid in the third body, wherein at both ends of the fourth body, a second working oil port connected to each of the second working oil passages is formed, and a second one installed between the third body and the fourth body bidirectional piston for compressing and dispensing hydraulic fluid through working oil; a second solenoid valve connected to each of the second working oil lines for moving the second bidirectional piston of the second pressure-volume conversion device by changing the flow path of the working oil according to the control of the control unit; at least one second hydraulic pump installed on the second working oil pipe for pressurizing the working oil from the working oil tank and supplying the working oil to the second working oil pipe; a second motor for providing a rotational force to the second hydraulic pump; a second pressure sensor installed on the second working oil passage for measuring the pressure of the working oil and supplying the measured pressure value to the control unit; and a second torque converter installed on the second working oil passage for converting the rotational speed and the torque of the second hydraulic pump according to the control of the control unit.  The compressor according to claim 5, wherein in the second pressure-volume conversion means, the diameter of both ends of the second bi-directional piston is set in accordance with the gas pressure supplied to the second gas supply line to increase the pressure of the compressed gas by supplying high-pressure pressurized fluid Gas is supplied from the second supply line, and to supply the pressure fluid to the second vertical compression tube with a pressure which is higher than the delivery pressure of the second hydraulic pump, while the second hydraulic pump pressurizes the pressure fluid.  A compressor according to claim 5, wherein the volume of the first body of the first pressure-volume conversion means or the third body of the second pressure-volume conversion means is configured such that the pressure fluid is supplied to the first vertical compression pipe or the second vertical compression pipe without overflow.  The compressor of claim 5, wherein the first and second hydraulic fluid lines, the first and second working oil lines, and the working oil tank each include a radiator for cooling.  The compressor according to claim 5, wherein the control unit detects the moving position of the first bi-directional piston of the first pressure-volume conversion device or the second bi-directional piston of the second pressure-volume conversion device by the pressure of working oil supplied by the first pressure sensor or the second pressure sensor is detected causes the first or second solenoid valve to be moved to change the flow path of the first solenoid valve or the second solenoid valve.  A compressor according to any one of claims 1 to 10, wherein the first gas supply line, the intermediate storage tank and the main storage tank have third to fifth pressure sensors.  The compressor of claim 5, wherein the first vertical compression tube and the second vertical compression tube are closed-type tubes.

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