WO2000034655A1 - Compressor arrangement - Google Patents
Compressor arrangement Download PDFInfo
- Publication number
- WO2000034655A1 WO2000034655A1 PCT/GB1999/004034 GB9904034W WO0034655A1 WO 2000034655 A1 WO2000034655 A1 WO 2000034655A1 GB 9904034 W GB9904034 W GB 9904034W WO 0034655 A1 WO0034655 A1 WO 0034655A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- fluid
- chamber
- compressor
- gas
- chambers
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/117—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other
- F04B9/1176—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor
- F04B9/1178—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers the pumping members not being mechanically connected to each other the movement of each piston in one direction being obtained by a single-acting piston liquid motor the movement in the other direction being obtained by a hydraulic connection between the liquid motor cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B15/00—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts
- F04B15/06—Pumps adapted to handle specific fluids, e.g. by selection of specific materials for pumps or pump parts for liquids near their boiling point, e.g. under subnormal pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/008—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being a fluid transmission link
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
Definitions
- the invention relates to a compressor arrangement for compressing a fluid, such as natural gas.
- the invention is concerned with providing a reduced cost arrangement with other advantages over the known arrangements .
- a fluid compressor having at least one stage of compression including two chambers each for receiving a first fluid to be compressed and means for receiving a source of second fluid under pressure to effect compression of the first fluid by reducing the volume within the chamber.
- the compressor includes partition means in each chamber for separating the first and second fluids and switching means are provided to allow the source of pressurised fluid to alternate between each chamber to compress the first and second chambers alternatively by operating on the partition means .
- a method of compressing a fluid comprising the steps -of providing the fluid to be compressed to a first or second fluid chamber, providing a source of pressurised second fluid to the first or second chamber to reduce the volume within the respective chamber to compress the other fluid.
- the method includes the steps of: allowing the first chamber to open to receive the first fluid; thereafter reducing the size of the chamber to compress the fluid by means of the second pressurised fluid, and at the same time allowing the first fluid into the second chamber; and thereafter reducing the volume of the second chamber to compress the fluid by means of the second pressurised fluid, and at the same time allowing the first fluid into the first chamber.
- a slow moving hydraulically operated piston type compressor device is proposed. This utilises the ability of compact hydraulic pumps to deliver significant energy with a low volume flowrate of fluid at a pressure similar to the final gas pressure required (200 bar) .
- the speed of operation of the pistons is around 10 cycles/min rather than 10 cycles/sec (i.e. 60 times slower) thus reducing the wear rate on seals and allowing time for heat to dissipate.
- a higher speed version, with additional liquid cooling, for mounting on the vehicle could be employed but still of significantly lower speed.
- a further advantage of these designs is that the piston seals have more uniform pressures across them with the gas pressure being balanced by a similar or even higher hydraulic fluid pressure eliminating gas leakage across the seals.
- High gas compression ratios up to 250:1, can be achieved in a single stage compressor.
- a two stage version with up to 15:1 compression ratio in each stage is possible with the added advantage of lower hydraulic oil flow rate and less peak power requirement, than in a single stage version, typically lL/min of oil flow for every 8L/min of swept gas volume.
- Figure 1 shows a schematic simplified diagram of the hydraulic gas compressor
- FIG. 2 shows a two stage compressor in more detail
- FIG. 3 shows the single stage compressor alternative
- Figure 4 shows details of a supercharger for a single stage compressor.
- the simplified compressor system of Figure 1 shows the mechanisms employed to produce the slow moving compressor operated by hydraulic power by means of a bidirectional hydraulic pump 7, typically electrically driven.
- the hydraulic compressor is envisaged as a direct replacement for any size of conventional multi-stage reciprocating compressor, however, in the proposal under consideration, the aim typically is to fill a 16 litre vehicle tank with compressed gas from a domestic supply as follows: Low pressure gas via valve 30 is drawn into a hydraulic ram A, through a Non Return Valve (NRV) 13, as fluid via pump 7 is pumped to push gas out of a second ram B and NRV 16 into a vehicle fuel tank 2 with a volume reduction of 240:1 (the compression ratio for natural gas at 200 bar) .
- the high pressure delivery hose 1 is connected to the tank inlet 2a via a quick release coupling 3.
- the pumping rate is 8 litres/minute.
- Figure 3 shows a single stage version and Figure 2 shows a two stage version.
- the system consists of an hydraulic power circuit linked directly and integrally with a gas compression circuit.
- a flexible hose delivery mechanism 1 with quick release coupling 3 is provided to deliver compressed gas to an external storage cylinder or tank 2 (partially shown in broken lines) .
- the hydraulic power circuit consists of a small electric motor 4 coupled to an hydraulic gear or piston pump 7.
- High pressure fluid output from the pump is connected to a spool type shuttle valve 8, pressure relief valves and two hydraulically opposed cylinders or rams A, B.
- Each ram has one fluid connection for flow/discharge to the shuttle valve.
- the low pressure or discharge from the shuttle valve is connected to a sump 5, containing a reservoir of hydraulic fluid.
- the hydraulic pump intake is connected via a filter 6 to a point on the sump which is gravitationally well below the fluid level.
- the gas compression circuit consists of the two opposed cylinders or rams 12, 15 which are integral with the hydraulic rams. Each gas ram has two gas connections. One is for the gas inlet and the other is for higher pressure gas discharge. A non return valve 13 or 17 is fitted to the inlet and a non return valve 16 is at the outlet connection of each gas ram.
- the high pressure gas delivery pipe is of a small bore flexible type fitted with a quick release coupling 3.
- a matching coupling is fitted to each high pressure gas storage cylinder.
- the storage cylinder is usually mounted under the vehicle body.
- a bypass and relief circuit is provided to reduce the gas pressure in the delivery hose after filling of the cylinder is complete.
- the hydraulic pump motor 4 is electrically operable and is energised by means of a trip relay switch (not shown) .
- Hydraulic oil is drawn from the sump 5 at atmospheric pressure, via the filter 6, into the hydraulic pump 7. Rotation of the gears within the pump forces oil to flow into the spool valve 8 at high pressure. If the pressure exceeds a set value, typically 275 bar, then the relief valve 9 opens to allow oil to bypass the spool valve and flow back to the sump .
- the spool valve is a shuttle operated type whereby oil may flow from one port and return to the other port or vice versa.
- the direction of flow is determined by the position of the spool inside the valve.
- This is a pressure operated bistable device.
- a relief valve 21 allows oil at this pressure to actuate the spool. This reverses the direction of flow through the outlet ports until the outlet pressure at port II reaches the pressure set by its relief valve 22, whereupon the flow reverts back to the original direction.
- pistons A and B and their respective hydraulic oil and gas chambers are identical in size.
- the maximum piston travel distance or stroke 18 is the same for each piston.
- the gas outlets from each chamber A and B are connected in parallel to the high pressure gas discharge hose 1.
- piston A is inducing gas
- piston B is compressing gas and vice versa.
- the volume flowrates of hydraulic oil to induced gas are typically in the ratio 8:9.
- the peak hydraulic pressure is slightly larger than the peak gas discharge pressure, typically in the ratio 9:8. For a gas discharge pressure of 225 bar, the peak oil pressure might be 253 bar.
- the pistons A and B and their respective hydraulic oil and gas chambers are different in size.
- the oil and gas volumes and their respective volume ratios refer to the maximum or swept volumes.
- Piston B has a large diameter providing a large volume 12 in gas chamber B.
- the oil volume in hydraulic ram B is much smaller than the gas volume since the connecting rod 19, at this point, is of large diameter creating an annulus of small hydraulic volume 14.
- the high ratio of gas to oil volume typically 15:1 enables a small volume of hydraulic oil at high pressure, typically 225 bar, to compress a large volume of gas to medium pressure, typically 15 bar.
- piston A has a smaller diameter than piston B so that the ratio of volume 12 in gas chamber B to volume 15 in gas chamber A is typically 15:1.
- the oil volume 10 in hydraulic ram A is slightly smaller than the volume 15 in gas chamber A typically by the ratio 21:25 since the connecting rod 11, at this point, is of small diameter.
- a small volume of oil at high pressure, typically 268 bar is able to compress gas from medium pressure, typically 15 bar, to high pressure, typically 225 bar.
- the gas outlet from chamber B, the first stage is connected via passageway 20 and a non return valve 17 to the gas inlet to chamber A, the second stage.
- the effective stroke will reduce by 0.24 metres for every 1 mm of effective residual volume - because it is necessary to get the induction chamber pressure low enough through the displacement of the piston in order to allow a new charge of low pressure supply gas in.
- the modification is intended to relieve the residual gas pressure by venting it into the opposing compression chamber at the point of fluid reversal when its induction stroke is complete and thus providing a small supercharge .
- This feature is achieved , typically as shown, by incorporating a valve 20 within the piston (inner piston 21 and outer piston shell 22) which is opened at the instant of fluid reversal by the trapped pressure and remains open as the piston 21 is towed through its induction stroke - allowing high pressure trapped residual gas from the end of the compression stroke to pass along a hollow piston connecting rod 23 to supercharge gas in the opposing chamber which at the time of fluid reversal has completed its induction stroke.
- the opposing split piston re-seals as the hydraulic pressure builds for the compression stroke allowing the next charge of gas to be drawn in by the induction stroke - thereby maintaining an effective high swept volume at all pressures of compression and providing a small supercharge to the induction gas charge and thus ensuring a high pumping efficiency.
- the piston is retained by clip 24 and abuts the soft seat 25.
- a number of ring seals 26 prevent unwanted fluid flow.
- the rams of the single stage device could be interconnected by a flexible tensile member so that the chambers need not be in line, or some other mechanism could be employed to operate the rams which form the separators in the chambers.
- the hydraulic fluid from the compressor could be passed to an external cooling device (e.g. heat exchanger or cooling coil) to further assist in cooling this fluid. This would be expedient at speeds in the region of 20 cycles/min.
- the piston areas for hydraulic fluid could be identical or larger in the second stage compression portion to provide a longer stroke period to assist with cooling -of the high pressure compression chamber.
- valves 21 and 22 may be set at different values to allow the system to operate at two distinct control pressures.
- the compressor although shown horizontally in the drawings, may typically operate in a vertical mode.
- the entire hydraulic circuit including the spool valve, relief valves and associated pipework could be enclosed within the external shell of the compressor so that any leakage of hydraulic fluid would only occur if the pump shaft seal failed or the external shell fractured.
- the hose could be configured to include coaxial bores so that any high pressure gas remaining on decoupling can be vented back to the compressor system or when the tank becomes full.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
- Filling Or Discharging Of Gas Storage Vessels (AREA)
Abstract
Description
Claims
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CA002353391A CA2353391A1 (en) | 1998-12-04 | 1999-12-02 | Compressor arrangement |
BR9915853-1A BR9915853A (en) | 1998-12-04 | 1999-12-02 | Arrangement for hydraulic compressor |
US09/856,170 US6568911B1 (en) | 1998-12-04 | 1999-12-02 | Compressor arrangement |
IL14346399A IL143463A0 (en) | 1998-12-04 | 1999-12-02 | Compressor arrangement |
DE69910821T DE69910821T2 (en) | 1998-12-04 | 1999-12-02 | COMPRESSOR DEVICE |
AU14010/00A AU762331B2 (en) | 1998-12-04 | 1999-12-02 | Compressor arrangement |
EP99973318A EP1135608B1 (en) | 1998-12-04 | 1999-12-02 | Compressor arrangement |
JP2000587078A JP3768405B2 (en) | 1998-12-04 | 1999-12-02 | Compression device |
AT99973318T ATE248294T1 (en) | 1998-12-04 | 1999-12-02 | COMPRESSOR DEVICE |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GBGB9826566.3A GB9826566D0 (en) | 1998-12-04 | 1998-12-04 | Hydraulic gas compressor |
GB9826566.3 | 1998-12-04 | ||
GBGB9912233.5A GB9912233D0 (en) | 1998-12-04 | 1999-05-27 | Hydrualically driven compressor |
GB9912233.5 | 1999-05-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2000034655A1 true WO2000034655A1 (en) | 2000-06-15 |
Family
ID=26314779
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/GB1999/004034 WO2000034655A1 (en) | 1998-12-04 | 1999-12-02 | Compressor arrangement |
Country Status (14)
Country | Link |
---|---|
US (1) | US6568911B1 (en) |
EP (1) | EP1135608B1 (en) |
JP (1) | JP3768405B2 (en) |
AR (1) | AR025817A1 (en) |
AT (1) | ATE248294T1 (en) |
AU (1) | AU762331B2 (en) |
BR (1) | BR9915853A (en) |
CA (1) | CA2353391A1 (en) |
DE (1) | DE69910821T2 (en) |
EG (1) | EG23099A (en) |
GB (2) | GB9912233D0 (en) |
IL (1) | IL143463A0 (en) |
MY (1) | MY123318A (en) |
WO (1) | WO2000034655A1 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002101238A1 (en) * | 2001-06-13 | 2002-12-19 | Bg Intellectual Property Limited | A gas compressor and relief valve |
WO2003083298A1 (en) * | 2002-03-28 | 2003-10-09 | Westport Research Inc. | Method and apparatus for compressing a gas to a high pressure |
WO2009146316A1 (en) * | 2008-05-27 | 2009-12-03 | Neogas Inc. | Variable frequency drive for gas dispensing system |
ITUD20090011A1 (en) * | 2009-01-16 | 2010-07-17 | Michele Ongaro | PLANT FOR THE COMPRESSION OF A GAS, AND ITS COMPRESSION PROCEDURE |
EP3418564A1 (en) * | 2017-06-21 | 2018-12-26 | Valeo Systèmes d'Essuyage | Gas compression system for drying at least one sensor of a motor vehicle |
Families Citing this family (34)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB0219595D0 (en) * | 2002-08-22 | 2002-10-02 | Lattice Intellectual Property | Two stage double acting hydraulic/gas compressor |
US20050042111A1 (en) * | 2003-02-05 | 2005-02-24 | Zaiser Lenoir E. | Fluid pump |
DE10321771C5 (en) * | 2003-05-15 | 2017-01-19 | Continental Teves Ag & Co. Ohg | Method for limiting the power of a multi-stage compressor and compressor for carrying out the method |
CN100337031C (en) * | 2005-10-13 | 2007-09-12 | 南京全章液力科技有限公司 | Hydraulic reciprocating pump |
US7604064B2 (en) * | 2006-01-17 | 2009-10-20 | ABI Technology, Inc | Multi-stage, multi-phase unitized linear liquid entrained-phase transfer apparatus |
ITBO20060196A1 (en) * | 2006-03-20 | 2007-09-21 | G I & E S P A | STATION FOR SUPPLYING TANKS WITH GAS IN PRESSURE, IN PARTICULAR OF TANKS INSTALLED ON VEHICLES. |
BRPI0916907A2 (en) * | 2008-08-04 | 2019-09-24 | Cameron Int Corp | underwater differential area accumulator |
CA2644346A1 (en) * | 2008-11-12 | 2010-05-12 | Global Energy Services Ltd. | Multiphase pump |
CA2762980A1 (en) * | 2009-05-22 | 2010-11-25 | General Compression Inc. | Compressor and/or expander device |
US8454321B2 (en) | 2009-05-22 | 2013-06-04 | General Compression, Inc. | Methods and devices for optimizing heat transfer within a compression and/or expansion device |
US9134225B2 (en) * | 2009-08-14 | 2015-09-15 | Halliburton Energy Services, Inc. | Additive photometric analysis |
AU2010336383B2 (en) | 2009-12-24 | 2015-05-28 | General Compression Inc. | Methods and devices for optimizing heat transfer within a compression and/or expansion device |
US8567303B2 (en) | 2010-12-07 | 2013-10-29 | General Compression, Inc. | Compressor and/or expander device with rolling piston seal |
US8997475B2 (en) | 2011-01-10 | 2015-04-07 | General Compression, Inc. | Compressor and expander device with pressure vessel divider baffle and piston |
US8572959B2 (en) | 2011-01-13 | 2013-11-05 | General Compression, Inc. | Systems, methods and devices for the management of heat removal within a compression and/or expansion device or system |
EP2663758A1 (en) | 2011-01-14 | 2013-11-20 | General Compression Inc. | Compressed gas storage and recovery system and method of operation systems |
US8272212B2 (en) | 2011-11-11 | 2012-09-25 | General Compression, Inc. | Systems and methods for optimizing thermal efficiencey of a compressed air energy storage system |
US8522538B2 (en) | 2011-11-11 | 2013-09-03 | General Compression, Inc. | Systems and methods for compressing and/or expanding a gas utilizing a bi-directional piston and hydraulic actuator |
US9291161B2 (en) | 2012-10-02 | 2016-03-22 | James Victor Hogan | Compact linear actuator |
WO2014194059A1 (en) * | 2013-05-31 | 2014-12-04 | Intellectual Property Holdings, Llc | Natural gas compressor |
US9541236B2 (en) | 2013-07-12 | 2017-01-10 | Whirlpool Corporation | Multi-stage home refueling appliance and method for supplying compressed natural gas |
US20140182561A1 (en) * | 2013-09-25 | 2014-07-03 | Eghosa Gregory Ibizugbe, JR. | Onboard CNG/CFG Vehicle Refueling and Storage Systems and Methods |
CN105889154A (en) * | 2014-11-28 | 2016-08-24 | 陕西鼎基能源科技有限公司 | High-pressure gas pressure energy isentropic supercharger |
US10429095B2 (en) * | 2015-02-04 | 2019-10-01 | Todd Gerard Schmidt | Schmitty compressor |
WO2017201261A1 (en) * | 2016-05-18 | 2017-11-23 | Liftwave, Inc. Dba Rise Robotics | Load normalized air pump |
CA2948018C (en) | 2016-09-22 | 2023-09-05 | I-Jack Technologies Incorporated | Lift apparatus for driving a downhole reciprocating pump |
US11339778B2 (en) | 2016-11-14 | 2022-05-24 | I-Jack Technologies Incorporated | Gas compressor and system and method for gas compressing |
US10544783B2 (en) | 2016-11-14 | 2020-01-28 | I-Jack Technologies Incorporated | Gas compressor and system and method for gas compressing |
WO2020157538A1 (en) * | 2019-01-28 | 2020-08-06 | Wärtsilä Services Switzerland Ltd | Fuel injection system and method of operating piston engine |
WO2020219007A1 (en) * | 2019-04-22 | 2020-10-29 | Cummins Inc. | Methods and systems for residual fluid release in fuel pumps |
US11480165B2 (en) * | 2019-09-19 | 2022-10-25 | Oshkosh Corporation | Reciprocating piston pump comprising a housing defining a first chamber and a second chamber cooperating with a first piston and a second piston to define a third chamber and a fourth chamber |
CN110805550B (en) * | 2019-11-08 | 2020-12-15 | 江苏科技大学 | Vehicle-mounted air pump control system and control method thereof |
CA3074365A1 (en) | 2020-02-28 | 2021-08-28 | I-Jack Technologies Incorporated | Multi-phase fluid pump system |
US11519403B1 (en) | 2021-09-23 | 2022-12-06 | I-Jack Technologies Incorporated | Compressor for pumping fluid having check valves aligned with fluid ports |
Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2411020A (en) * | 1943-10-27 | 1946-11-12 | Denison Eng Co | Fluid compressing apparatus |
GB624556A (en) * | 1944-05-23 | 1949-06-13 | Joseph Lambert Jameson | Improvements in the making of gas tight joints for the pistons of gas compressors |
GB1359821A (en) * | 1971-06-14 | 1974-07-10 | Hedley Saw M R | Reciprocating pumps and compressors |
EP0064481A1 (en) * | 1981-04-30 | 1982-11-10 | SAFE S.r.l. | A reciprocating, hydraulically operated, positive displacement compressor |
US4515516A (en) * | 1981-09-30 | 1985-05-07 | Champion, Perrine & Associates | Method and apparatus for compressing gases |
US4653986A (en) * | 1983-07-28 | 1987-03-31 | Tidewater Compression Service, Inc. | Hydraulically powered compressor and hydraulic control and power system therefor |
US4750869A (en) * | 1984-05-09 | 1988-06-14 | Booster Technologies, Inc. | Method and apparatus for boosting gas from a low-pressure source to a high-pressure receptacle |
US5366350A (en) * | 1993-04-13 | 1994-11-22 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Gas guiding mechanism in a piston type compressor |
US5387089A (en) * | 1991-09-17 | 1995-02-07 | Tren Fuels, Inc. | Method and apparatus for compressing gases with a liquid system |
US5551488A (en) * | 1993-03-30 | 1996-09-03 | Process System International, Inc. | Method of filling a two-compartments storage tank with cryogenic fluid |
US5626463A (en) * | 1992-10-05 | 1997-05-06 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Axial multi-piston compressor having rotary valve for allowing residual part of compressed fluid to escape |
US5676180A (en) * | 1996-03-13 | 1997-10-14 | Teel; James R. | Method and system for storing and hydraulically-pressurizing compressed natural gas (CNG) at an automotive re-fuel station |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3838941A (en) * | 1973-05-29 | 1974-10-01 | V Roschupkin | Pumping unit |
US4236875A (en) * | 1979-10-04 | 1980-12-02 | General Motors Corporation | Pressure operated hydraulic control valve |
US4334833A (en) * | 1980-10-28 | 1982-06-15 | Antonio Gozzi | Four-stage gas compressor |
US4390322A (en) * | 1981-02-10 | 1983-06-28 | Tadeusz Budzich | Lubrication and sealing of a free floating piston of hydraulically driven gas compressor |
US4383804A (en) * | 1981-02-10 | 1983-05-17 | Tadeusz Budzich | Lubrication and sealing of a free floating piston of hydraulically driven gas compressor |
CA1145728A (en) * | 1981-04-21 | 1983-05-03 | Antonio Gozzi | Three or four stage gas compressor |
IT1187318B (en) * | 1985-02-22 | 1987-12-23 | Franco Zanarini | VOLUMETRIC ALTERNATE COMPRESSOR WITH HYDRAULIC OPERATION |
DE3674778D1 (en) * | 1986-02-13 | 1990-11-08 | Methane Technologies Ltd | GAS COMPRESSION PROCESS. |
US5324175A (en) * | 1993-05-03 | 1994-06-28 | Northern Research & Engineering Corporation | Pneumatically operated reciprocating piston compressor |
US5584664A (en) * | 1994-06-13 | 1996-12-17 | Elliott; Alvin B. | Hydraulic gas compressor and method for use |
KR200153232Y1 (en) * | 1996-08-08 | 1999-08-02 | 허남종 | Reciprocating compressor for transport of a vicous liquid |
US5863186A (en) * | 1996-10-15 | 1999-01-26 | Green; John S. | Method for compressing gases using a multi-stage hydraulically-driven compressor |
US5993170A (en) * | 1998-04-09 | 1999-11-30 | Applied Materials, Inc. | Apparatus and method for compressing high purity gas |
US6125680A (en) * | 1998-10-21 | 2000-10-03 | Emhart Inc. | Rivet tool adjustable rivet delivery device |
-
1999
- 1999-05-27 GB GBGB9912233.5A patent/GB9912233D0/en not_active Ceased
- 1999-12-01 GB GB9928345A patent/GB2346938B/en not_active Expired - Fee Related
- 1999-12-02 AU AU14010/00A patent/AU762331B2/en not_active Ceased
- 1999-12-02 JP JP2000587078A patent/JP3768405B2/en not_active Expired - Fee Related
- 1999-12-02 EP EP99973318A patent/EP1135608B1/en not_active Expired - Lifetime
- 1999-12-02 BR BR9915853-1A patent/BR9915853A/en not_active Application Discontinuation
- 1999-12-02 WO PCT/GB1999/004034 patent/WO2000034655A1/en active IP Right Grant
- 1999-12-02 IL IL14346399A patent/IL143463A0/en unknown
- 1999-12-02 AT AT99973318T patent/ATE248294T1/en not_active IP Right Cessation
- 1999-12-02 DE DE69910821T patent/DE69910821T2/en not_active Expired - Fee Related
- 1999-12-02 CA CA002353391A patent/CA2353391A1/en not_active Abandoned
- 1999-12-02 US US09/856,170 patent/US6568911B1/en not_active Expired - Fee Related
- 1999-12-03 MY MYPI99005277A patent/MY123318A/en unknown
- 1999-12-03 AR ARP990106186A patent/AR025817A1/en active IP Right Grant
- 1999-12-04 EG EG154899A patent/EG23099A/en active
Patent Citations (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2411020A (en) * | 1943-10-27 | 1946-11-12 | Denison Eng Co | Fluid compressing apparatus |
GB624556A (en) * | 1944-05-23 | 1949-06-13 | Joseph Lambert Jameson | Improvements in the making of gas tight joints for the pistons of gas compressors |
GB1359821A (en) * | 1971-06-14 | 1974-07-10 | Hedley Saw M R | Reciprocating pumps and compressors |
EP0064481A1 (en) * | 1981-04-30 | 1982-11-10 | SAFE S.r.l. | A reciprocating, hydraulically operated, positive displacement compressor |
US4515516A (en) * | 1981-09-30 | 1985-05-07 | Champion, Perrine & Associates | Method and apparatus for compressing gases |
US4653986A (en) * | 1983-07-28 | 1987-03-31 | Tidewater Compression Service, Inc. | Hydraulically powered compressor and hydraulic control and power system therefor |
US4750869A (en) * | 1984-05-09 | 1988-06-14 | Booster Technologies, Inc. | Method and apparatus for boosting gas from a low-pressure source to a high-pressure receptacle |
US5387089A (en) * | 1991-09-17 | 1995-02-07 | Tren Fuels, Inc. | Method and apparatus for compressing gases with a liquid system |
US5626463A (en) * | 1992-10-05 | 1997-05-06 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Axial multi-piston compressor having rotary valve for allowing residual part of compressed fluid to escape |
US5551488A (en) * | 1993-03-30 | 1996-09-03 | Process System International, Inc. | Method of filling a two-compartments storage tank with cryogenic fluid |
US5366350A (en) * | 1993-04-13 | 1994-11-22 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Gas guiding mechanism in a piston type compressor |
US5676180A (en) * | 1996-03-13 | 1997-10-14 | Teel; James R. | Method and system for storing and hydraulically-pressurizing compressed natural gas (CNG) at an automotive re-fuel station |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002101238A1 (en) * | 2001-06-13 | 2002-12-19 | Bg Intellectual Property Limited | A gas compressor and relief valve |
WO2003083298A1 (en) * | 2002-03-28 | 2003-10-09 | Westport Research Inc. | Method and apparatus for compressing a gas to a high pressure |
US7527482B2 (en) | 2002-03-28 | 2009-05-05 | Westport Power Inc. | Method and apparatus for compressing a gas to a high pressure |
WO2009146316A1 (en) * | 2008-05-27 | 2009-12-03 | Neogas Inc. | Variable frequency drive for gas dispensing system |
ITUD20090011A1 (en) * | 2009-01-16 | 2010-07-17 | Michele Ongaro | PLANT FOR THE COMPRESSION OF A GAS, AND ITS COMPRESSION PROCEDURE |
EP3418564A1 (en) * | 2017-06-21 | 2018-12-26 | Valeo Systèmes d'Essuyage | Gas compression system for drying at least one sensor of a motor vehicle |
FR3068087A1 (en) * | 2017-06-21 | 2018-12-28 | Valeo Systemes D'essuyage | SYSTEM FOR COMPRESSING A GAS FOR DRYING AT LEAST ONE SENSOR OF A MOTOR VEHICLE |
CN109094531A (en) * | 2017-06-21 | 2018-12-28 | 法雷奥***公司 | For drying the gas compression system of at least one sensor of motor vehicles |
Also Published As
Publication number | Publication date |
---|---|
AU1401000A (en) | 2000-06-26 |
DE69910821D1 (en) | 2003-10-02 |
DE69910821T2 (en) | 2004-08-19 |
GB2346938A (en) | 2000-08-23 |
BR9915853A (en) | 2001-08-21 |
CA2353391A1 (en) | 2000-06-15 |
US6568911B1 (en) | 2003-05-27 |
EP1135608B1 (en) | 2003-08-27 |
AU762331B2 (en) | 2003-06-26 |
JP3768405B2 (en) | 2006-04-19 |
MY123318A (en) | 2006-05-31 |
IL143463A0 (en) | 2002-04-21 |
GB9928345D0 (en) | 2000-01-26 |
JP2002531772A (en) | 2002-09-24 |
AR025817A1 (en) | 2002-12-18 |
EG23099A (en) | 2004-03-31 |
GB9912233D0 (en) | 1999-07-28 |
ATE248294T1 (en) | 2003-09-15 |
GB2346938B (en) | 2002-12-18 |
EP1135608A1 (en) | 2001-09-26 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US6568911B1 (en) | Compressor arrangement | |
CA1147205A (en) | Tandem long stroke reciprocating mud pump assembly | |
CN100337031C (en) | Hydraulic reciprocating pump | |
US4913809A (en) | Concentrating apparatus with reverse osmosis membrane | |
EP0272137B1 (en) | Hydraulic pneumatic power transfer unit | |
US4565501A (en) | Two-stage volumetric pump for liquefied petroleum gases in liquid phase | |
CN206017110U (en) | A kind of multi-stage compression commutation valve type diaphragm type compressor | |
CN1006925B (en) | Multipurpose fluid drive piston pump | |
CA2031034C (en) | Self lubricating, two stage variable compressor | |
WO1988001021A1 (en) | Single and double acting fluid intensifier pump | |
US20230184238A1 (en) | Pumping system having remote valve blocks | |
CN213360338U (en) | Hydraulic drive booster and hydraulic drive sleeve pipe gas supercharging device | |
CN2533340Y (en) | Automatic piston reciprocating hydraulic oil cylinder | |
RU2220323C1 (en) | Compressor with hydraulic drive | |
CN217841958U (en) | Lubricating system of diaphragm compressor and diaphragm compressor | |
WO1990008897A1 (en) | Hydraulic piston pump for the compression of multiphase fluid | |
CN2479243Y (en) | Hydraulic driven oil-gas mixing transfer pump | |
CN212615198U (en) | Advection metering pump | |
RU223079U1 (en) | COMPRESSOR UNIT FOR GASES COMPRESSION | |
CN218439650U (en) | Direct-drive pressurizing unit, direct-drive pressurizing module, direct-drive pressurizing system, reciprocating pump, compressor and hydrogenation station | |
CN210949014U (en) | Corrosion-resistant high-pressure pump for injecting oil-soluble chemical agent | |
CN115506988B (en) | Gas drive liquid booster pump for oil exploitation | |
RU2151911C1 (en) | Installation for injection of liquid-gas mixture | |
CN208719067U (en) | A kind of novel frame hydraulic station structure | |
CN2531130Y (en) | Superhigh pressure gas compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
ENP | Entry into the national phase |
Ref document number: 2000 14010 Country of ref document: AU Kind code of ref document: A |
|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): AU BR CA IL IN JP SG US |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
DFPE | Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 1999973318 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 143463 Country of ref document: IL |
|
ENP | Entry into the national phase |
Ref document number: 2353391 Country of ref document: CA Ref document number: 2353391 Country of ref document: CA Kind code of ref document: A |
|
ENP | Entry into the national phase |
Ref document number: 2000 587078 Country of ref document: JP Kind code of ref document: A |
|
WWE | Wipo information: entry into national phase |
Ref document number: IN/PCT/2001/780/CHE Country of ref document: IN |
|
WWE | Wipo information: entry into national phase |
Ref document number: 09856170 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 14010/00 Country of ref document: AU |
|
WWP | Wipo information: published in national office |
Ref document number: 1999973318 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 1999973318 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 14010/00 Country of ref document: AU |