EP1907701B1 - Verdichter, insbesondere kolbenverdichter - Google Patents
Verdichter, insbesondere kolbenverdichter Download PDFInfo
- Publication number
- EP1907701B1 EP1907701B1 EP06762401.5A EP06762401A EP1907701B1 EP 1907701 B1 EP1907701 B1 EP 1907701B1 EP 06762401 A EP06762401 A EP 06762401A EP 1907701 B1 EP1907701 B1 EP 1907701B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- volume
- compressor
- compressor according
- piston
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
Links
Images
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
- F04B25/00—Multi-stage pumps
- F04B25/005—Multi-stage pumps with two 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
- F04B25/00—Multi-stage pumps
-
- 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
- F04B37/00—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00
- F04B37/10—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use
- F04B37/18—Pumps having pertinent characteristics not provided for in, or of interest apart from, groups F04B25/00 - F04B35/00 for special use for specific elastic fluids
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/16—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by adjusting the capacity of dead spaces of working chambers
Definitions
- the invention relates to a compressor, in particular reciprocating compressor, for compressing a gaseous medium with a low pressure stage for compressing the medium from an inlet pressure to an intermediate pressure, and a high pressure stage for compressing the medium from the intermediate pressure to a high pressure.
- the step pressure ratio is determined by the cylinder dimensions.
- a medium may be pressurized from an input pressure of 1 bar in the low pressure stage having a stage pressure ratio of 17 to an intermediate pressure of 17 bar the high pressure stage, which has a stage pressure ratio of 17.6, are compressed to a high pressure of 300 bar.
- Such reciprocating compressors are designed for a certain inlet pressure, wherein the inlet pressure of the medium can be varied within narrow limits. If a generic reciprocating compressor, which is designed for an inlet pressure of 1 bar, operated instead of an inlet pressure of 1 bar at an inlet pressure of 5 bar, would be after the Niederducklace at the stage pressure ratio of 17, an intermediate pressure of 85 bar set, which is used to overheat the Niederducklace leads.
- the present invention has for its object to provide a compressor of the type mentioned available, which is suitable for different input pressures with low construction costs.
- the high pressure stage is preceded by a compensating volume with adjustable dead volume.
- the high-pressure stage upstream and thus connected to the high-pressure level compensation volume, it is easily possible to provide an adjustable dead volume at the high-pressure stage.
- gaseous medium is partially supplied to the compensation volume.
- the gaseous medium expands adiabatically and in this case cools back below the intake temperature of the low-pressure stage.
- the suction volume of the high-pressure stage can thus be changed in a simple manner and, at the same time, additional cooling of the compressor can be achieved. This makes it possible in a simple manner to operate the compressor at different input pressures, further overheating of the compressor is avoided.
- the dead volume formed by the compensating volume is adjustable as a function of the inlet pressure.
- a dead space control of the high-pressure stage in dependence on the inlet pressure can be achieved with little effort with the compensation volume.
- the compensation volume is set to minimum dead volume at maximum inlet pressure and is adjustable with decreasing inlet pressure in the direction of a maximum dead volume.
- the additional cooling effect increases due to the equalization volume.
- the step pressure ratio increases with the high pressure stage, while increasing the thermal load on the compressor.
- the compensating volume is designed as a compensating cylinder, which has a displaceable in a housing cylinder.
- this design of the compensating volume as adjusting an adjustable dead volume can be easily produced.
- the cylinder is provided according to a preferred embodiment of the invention as a stepped piston with a first control surface, which is arranged in the compensating volume and is acted upon by the intermediate pressure and having a second control surface, which is acted upon by the inlet pressure.
- a cylinder designed as a stepped piston can be made possible by decreasing the inlet pressure by appropriate choice of the sizes of the first and second control surface in a simple manner an admission of the cylinder in the direction of the minimum dead volume at maximum inlet pressure and in the direction of the maximum dead volume.
- the compensation volume is provided with a cooling device, whereby the medium located in the compensation volume can be cooled in a simple manner and thus the cooling effect can be further increased by the compensation volume.
- the cooling device is formed by arranged on the housing cooling fins, whereby a cooling device of the compensation volume can be produced with low construction costs.
- the compressor has according to an advantageous embodiment of the invention a longitudinally displaceable in a housing piston, which is hydraulically driven.
- the low-pressure stage expediently comprises a first pressure chamber and a second pressure chamber, as a result of which the piston has two pressure chambers of the low-pressure stage controls.
- pulsations in the pressure-carrying lines can be reduced with a small space requirement by two pressure chambers.
- the high-pressure stage comprises a first pressure chamber and a second pressure chamber.
- two pressure chambers of the high-pressure stage are still actuated by the piston, it being possible to achieve low pulsations with a small space requirement of the compressor.
- a cooling of the compressor in the region of the low-pressure stage and the high-pressure stage can be achieved in a simple manner, if external cooling is provided on the housing.
- the piston is advantageously provided with at least one longitudinal bore, which is in communication with a drive pressure chamber.
- FIG. 1 is a longitudinal section of an inventive designed as a linear piston compressor 1 compressor shown.
- the piston compressor 1 has a longitudinally displaceable in a housing bore 2 of a housing 3, stepped piston 4, wherein between the piston 4 and the housing bore 2, a low-pressure stage 5 and a high pressure stage 6 is formed.
- the high-pressure stage 6 is formed in the central region of the piston compressor 1 and has two pressure chambers 6a, 6b which are formed between a sealing element 7 arranged at the middle region of the housing 3 and the piston 4.
- Piston sections 8a, 8b are arranged on the stepped piston 4 in the region of a diameter transition, the pressure chambers 6a, 6b of the high-pressure stage 6 being formed in the area of the enlarged diameter of the piston 4.
- the piston 4 after in the FIG. 1 is acted upon right, the left pressure chamber 6a minimum displacement volume and the right pressure chamber 6b maximum displacement volume.
- the low-pressure stage 5 is formed on both sides of the high-pressure stage 6 in the region of the reduced diameter of the piston 4 and has two pressure chambers 5a, 5b, which are arranged between the housing bore 3 and arranged on the piston 4 piston portions 8a, 8b in the region of the piston reduced diameter are formed.
- the piston compressor 1 is hydraulically driven, wherein on the piston 4 at the outer regions adjacent to the low-pressure stage 5 hydraulically acted upon drive pressure chambers 9a, 9b are formed.
- the drive pressure chamber 9a is acted upon by hydraulic pressure medium.
- the piston rod 4 Upon actuation of the drive pressure chamber 9b, the piston rod 4 according to in the FIG. 1 applied to the left.
- the pressure chambers 5a, 5b of the low-pressure stage 5 are each assigned a low-pressure suction valve 10a, 10b and a low-pressure pressure valve 11a, 11b.
- the pressure chambers 6a, 6b of the high-pressure stage 6 are respectively associated with a high-pressure suction valve and a high-pressure pressure valves, wherein in the FIG. 1 only the pressure chamber 6a associated high pressure suction valve 12a and high pressure pressure valve 13a is shown.
- an external cooling 15a, 15b is provided in the region of the low-pressure stage 5 and the high-pressure stage 6.
- the piston 4 designed as blind bores longitudinal bores 16a, 16b, which communicate with the drive pressure chambers 9a, 9b, whereby by the piston compressor 1 driving pressure means internal cooling of the reciprocating compressor 1 is achieved.
- the reciprocating compressor 1 is provided with a path measuring system 17.
- each pressure chamber 6a, 6b of the high-pressure stage is preceded by a compensation volume 20a, 20b with adjustable dead volume.
- FIGS. 1 and 2 is the pressure chamber 6a upstream compensating volume 20a shown in a longitudinal section.
- the pressure chamber 6b associated equalization volume 20b has an identical structure.
- the compensating volume 20a is designed as a compensating cylinder 21 which has a cylinder 23 longitudinally displaceable in a housing bore 28 of a housing 22, wherein the adjustable dead volume formed by the compensating volume 20a is formed between the housing bore 28 of the housing 22 and the cylinder 23, by means of a conduit 26 is connected to the input of the pressure chamber 6a of the high pressure stage 6, in particular to the pressure chamber 5a of the low pressure stage 5 with the pressure chamber 6a of the high pressure stage 6 connecting connecting line downstream of the high pressure suction valve 12a of the pressure chamber 6a of the high pressure stage 6.
- the cylinder 23 is a stepped piston formed and has at a arranged in the compensating volume 20a end face of a first control surface 24 which generated by that of the low pressure side, in the compensating volume 20a pending intermediate pressure is applied.
- a second control surface 25 is formed, is acted upon by the inlet pressure of the low pressure stage.
- the second control surface 25 is larger than the first control surface 24.
- a cooling device 27 is arranged in the region of the compensation volume 20a, which is formed for example by arranged on the outer circumference of the housing 22 cooling fins.
- the compensating volume 20 a in after in the FIG. 2 top deflected cylinder 23 maximum dead volume.
- the cylinder 23 With increasing at the second control surface 25 of the designed as a stepped piston cylinder 23 input pressure of the low pressure stage 5, the cylinder 23 is in the FIG. 2 acted upon below, whereby the compensating volume 20a is applied in the direction of a minimum dead volume at maximum inlet pressure of the reciprocating compressor 1.
- gaseous medium is fed to the pressure chamber 6a of the high-pressure stage 6 after the intake stroke in the compression stroke from the pressure chamber 5a of the low-pressure stage 5 via the pressure valve 11a and the suction valve 13a, which is in the intake stroke.
- the pressurized medium is also supplied to the compensating volume 20a and thus the adjustable dead volume by the low-pressure stage 5 to the intermediate pressure and through the cooling device 27 cooled.
- the inlet pressure compensation volume 20a By controlled as a function of the inlet pressure compensation volume 20a, it is possible to change the intake volume of the high pressure stage 6 and thus to operate the compressor at different input pressures, with the additional cooling of the medium by means of the compensation volume 20a and in particular the cooling device 27, the temperature of Compressor, in particular after the low pressure stage 5 with decreasing input pressure, wherein the step pressure ratio and thus the thermal load of the high pressure stage 6 increases, can be lowered.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005034907A DE102005034907A1 (de) | 2005-07-26 | 2005-07-26 | Verdichter, insbesondere Kolbenverdichter |
PCT/EP2006/006520 WO2007012384A1 (de) | 2005-07-26 | 2006-07-04 | Verdichter, insbesondere kolbenverdichter |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1907701A1 EP1907701A1 (de) | 2008-04-09 |
EP1907701B1 true EP1907701B1 (de) | 2017-01-25 |
Family
ID=36992587
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06762401.5A Not-in-force EP1907701B1 (de) | 2005-07-26 | 2006-07-04 | Verdichter, insbesondere kolbenverdichter |
Country Status (8)
Country | Link |
---|---|
US (1) | US20080199327A1 (ja) |
EP (1) | EP1907701B1 (ja) |
JP (1) | JP5065267B2 (ja) |
KR (1) | KR20080025059A (ja) |
CN (1) | CN101233318B (ja) |
AU (1) | AU2006274301A1 (ja) |
DE (1) | DE102005034907A1 (ja) |
WO (1) | WO2007012384A1 (ja) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ITTO20120395A1 (it) * | 2012-05-03 | 2012-08-02 | Electro Power Systems Spa | Dispositivo booster per la compressione di gas |
DE102014217897A1 (de) | 2014-09-08 | 2016-03-10 | Pressure Wave Systems Gmbh | Kompressorvorrichtung, eine damit ausgerüstete Kühlvorrichtung und ein Verfahren zum Betreiben der Kompressorvorrichtung und der Kühlvorrichtung |
CN104595155B (zh) * | 2014-12-30 | 2016-06-15 | 成都烃源科技有限责任公司 | 一种长冲程液控天然气压缩机 |
CN106988989B (zh) * | 2017-05-24 | 2019-12-03 | 安徽寅时压缩机制造有限公司 | 一种用于二级压缩机的防逆装置 |
US20190145395A1 (en) * | 2017-11-10 | 2019-05-16 | Haskel International, Llc | Method of Construction for High Cycle Fatigue Resistant Pressure Vessels in Hydrogen Service |
Family Cites Families (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1677369A (en) * | 1927-06-13 | 1928-07-17 | Edward A Rix | Fluid compressor |
US1939424A (en) * | 1931-06-23 | 1933-12-12 | Chicago Pneumatic Tool Co | Variable volume control mechanism for compressors |
US2456386A (en) * | 1946-05-07 | 1948-12-14 | Howell C Cooper | Cascade refrigeration unit with controls therefor |
US2593316A (en) * | 1946-12-23 | 1952-04-15 | Dole Valve Co | Reciprocating pump assembly |
US2698576A (en) * | 1951-10-06 | 1955-01-04 | Du Pont | Automatic control of interstage pressures in pumps |
US3084847A (en) * | 1960-09-07 | 1963-04-09 | Nordberg Manufacturing Co | Automatic clearance pockets for compressors |
DE1195427B (de) * | 1961-07-05 | 1965-06-24 | Basf Ag | Dreistufiger Hochdruckgaskompressor mit einer Kolbendichtung |
US3804125A (en) * | 1972-09-28 | 1974-04-16 | Bendix Corp | Pump pulsation dampener |
US4173433A (en) * | 1978-02-06 | 1979-11-06 | Anderson John M | Two-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 |
US4369633A (en) * | 1981-09-03 | 1983-01-25 | Snyder David A | Multiple stage compressor with flash gas injection assembly |
US4811558A (en) * | 1981-10-13 | 1989-03-14 | Baugh Benton F | System and method for providing compressed gas |
US4479377A (en) * | 1983-03-24 | 1984-10-30 | Arcstart, Inc. | Method and apparatus for measuring gas flow |
DE3410911A1 (de) * | 1983-04-06 | 1984-10-11 | Ernst Dipl.-Ing. 4600 Dortmund Korthaus | Kolbenpumpe |
JPS6138176A (ja) * | 1984-07-27 | 1986-02-24 | タイドウオ−タ− コンプレツシヨン サ−ビス,インコ−ポレ−テツド | 液体圧式圧縮機とその流体圧制御−動力装置 |
US4705460A (en) * | 1985-02-26 | 1987-11-10 | Anton Braun | Bounce chambers for multi-cylinder linear engine compressors |
US4976591A (en) * | 1990-03-02 | 1990-12-11 | Intevep, S.A. | Self lubricating, two stage variable compressor |
US5209647A (en) * | 1992-06-17 | 1993-05-11 | Dresser-Rand Company | Straight cylinder gas compressor with a reduced diameter compression chamber |
CN2202804Y (zh) * | 1994-01-26 | 1995-07-05 | 陈永江 | 一种氮氢气压缩机 |
US5863186A (en) * | 1996-10-15 | 1999-01-26 | Green; John S. | Method for compressing gases using a multi-stage hydraulically-driven compressor |
US6659730B2 (en) * | 1997-11-07 | 2003-12-09 | Westport Research Inc. | High pressure pump system for supplying a cryogenic fluid from a storage tank |
BR0103443A (pt) * | 2001-08-21 | 2004-03-09 | Petroleo Brasileiro Sa | Sistema e método de bombeio multifásico |
US7711901B2 (en) * | 2004-02-13 | 2010-05-04 | Intel Corporation | Method, system, and apparatus for an hierarchical cache line replacement |
-
2005
- 2005-07-26 DE DE102005034907A patent/DE102005034907A1/de not_active Withdrawn
-
2006
- 2006-07-04 KR KR1020077029045A patent/KR20080025059A/ko not_active Application Discontinuation
- 2006-07-04 JP JP2008523163A patent/JP5065267B2/ja not_active Expired - Fee Related
- 2006-07-04 WO PCT/EP2006/006520 patent/WO2007012384A1/de active Application Filing
- 2006-07-04 CN CN2006800275402A patent/CN101233318B/zh not_active Expired - Fee Related
- 2006-07-04 EP EP06762401.5A patent/EP1907701B1/de not_active Not-in-force
- 2006-07-04 US US11/996,842 patent/US20080199327A1/en not_active Abandoned
- 2006-07-04 AU AU2006274301A patent/AU2006274301A1/en not_active Abandoned
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
US20080199327A1 (en) | 2008-08-21 |
KR20080025059A (ko) | 2008-03-19 |
AU2006274301A1 (en) | 2007-02-01 |
JP2009503321A (ja) | 2009-01-29 |
DE102005034907A1 (de) | 2007-02-01 |
JP5065267B2 (ja) | 2012-10-31 |
WO2007012384A1 (de) | 2007-02-01 |
EP1907701A1 (de) | 2008-04-09 |
CN101233318B (zh) | 2011-10-19 |
CN101233318A (zh) | 2008-07-30 |
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