CN101233318B - Compressor, particularly piston compressor - Google Patents
Compressor, particularly piston compressor Download PDFInfo
- Publication number
- CN101233318B CN101233318B CN2006800275402A CN200680027540A CN101233318B CN 101233318 B CN101233318 B CN 101233318B CN 2006800275402 A CN2006800275402 A CN 2006800275402A CN 200680027540 A CN200680027540 A CN 200680027540A CN 101233318 B CN101233318 B CN 101233318B
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- China
- Prior art keywords
- compressor
- pressure
- piston
- stage
- volume
- 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.)
- Expired - Fee Related
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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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
An apparatus and method for compressing a gas is disclosed. A compressor, in particular a piston compressor, has a low pressure stage for compressing the medium from an inlet pressure to an intermediate pressure, and has a high pressure stage for compressing the medium from the intermediate pressure to a high pressure. A compensating volume with an adjustable dead volume is connected upstream of the high pressure stage.
Description
The present invention relates to a kind of compressor, especially piston compressor, be used for the compressed gaseous medium, this compressor has the low pressure stage and the high pressure stage that is used for this medium is compressed to from middle pressure high pressure that are used for this medium is compressed to from incoming pressure intermediate pressure.
Be used for the compressor that is configured to piston compressor of gaseous medium, stage pressure is than being determined by the cylinder size.In having two compressor stages being made of a low pressure stage and high pressure stage and stage pressure than the piston compressor in being in 17 scope, medium for example can be compressed to the intermediate pressures of 17 crust and have the high pressure that are compressed to 300 crust in the high pressure stage of 17.6 stage pressure ratio from the incoming pressure of 1 crust during having the low pressure stage of 17 stage pressure ratio.
This piston compressor is designed on definite incoming pressure, and wherein, the incoming pressure of medium only can change in narrow boundary.If be designed in the piston compressor of described type on the incoming pressure of 1 crust and be not under the incoming pressure of 1 crust but under the incoming pressures of 5 crust, work, then at stage pressure than being can produce 85 intermediate pressures that cling to that cause low pressure stage overheated in the back of low pressure stage at 17 o'clock.
By DE 199 33 989 A1 known a kind of piston compressor of two-stage, the piston compressor of this two-stage is applicable to different incoming pressures.For this reason, low pressure stage and the high pressure stage for this piston compressor is provided with drive unit separately.But the piston compressor with this two-stage of a drive unit that is used for low pressure stage and a drive unit that separates that is used for high pressure stage has high construction cost.
Task of the present invention is, a kind of compressor that starts described type is provided, and this compressor is applicable to different incoming pressures with little construction cost.
According to the present invention, this task solves like this: be connected with a compensation volume with adjustable dead volume in the high pressure stage front.By this that be connected the high pressure stage front and be thus connected to be implemented in simple mode an adjustable dead volume is set on the high pressure stage in the compensation volume on the high pressure stage.Gaseous medium partly flows to compensation volume at this during the compression stroke of low pressure stage.When medium during the ensuing aspiration stroke in high pressure stage when compensation volume then is transported to high pressure stage, gaseous medium adiabatic expansion and turning back in this cooling below the suction temperatures of low pressure stage.Can change the suction volume of high pressure stage and can realize simultaneously the additional cooling of compressor with simple mode by this compensation volume thus.In simple mode compressor is worked under different incoming pressures thus, wherein, also avoid overheat of compressor.
If a form of implementation according to the present invention can be regulated with incoming pressure relatively by the dead volume that compensation volume forms, then obtain a special advantage.Can realize the dead space control of high pressure stage thus with incoming pressure relatively by compensation volume with little cost.
If compensation volume is adjusted to minimum dead volume when incoming pressure is maximum and along with the decline of incoming pressure can then obtain a special advantage towards the direction adjustment of dead volume maximum.Realize the additional cooling effect of realizing by compensation volume being increased in simple mode thus along with the reduction of incoming pressure.Along with the decline of incoming pressure, the stage pressure of high pressure stage is than increasing, and wherein, the heat load of compressor increases simultaneously.Thus, give high pressure stage and be formed for the compensation volume of the dead volume of high pressure stage by configuration---the cooling effect of this compensation volume can make the compressor temperature of the compressor that uses under different incoming pressures reduce in simple mode along with the reduction of the incoming pressure increase by dead volume increases.
Compensation volume conforms with the destination and is configured to compensating cylinder, and this compensating cylinder has a cylinder that can move in housing.As this structural type of regulating cylinder, available simple mode produces adjustable dead volume by compensation volume.
According to a preferred configuration form of the present invention, described cylinder conforms with the destination as step piston and is provided with first chain of command, this first chain of command is arranged in the compensation volume and by intermediate pressure and loads, and described cylinder has second chain of command, and this second chain of command is loaded by incoming pressure.By this cylinder that is configured to step piston, size that can be by correspondingly selecting first chain of command and second chain of command with simple mode when incoming pressure is maximum on the direction of dead volume minimum and when incoming pressure descends the direction towards the dead volume maximum load described cylinder.
According to a further configuration of the present invention, compensation volume is provided with a cooling unit, and thus, the medium that is in the compensation volume can cool off and can further improve thus by the cooling effect that compensation volume realizes with simple mode.
According to a preferred implementing form of the present invention, cooling unit is made of the cooling ribs that some are arranged on the housing, and thus, the cooling unit of compensation volume can be made with little construction cost.
According to a favourable configuration form of the present invention, this compressor has a piston that can vertically move in housing, and this piston can be by hydraulic driving.
Low pressure stage conforms with the destination and comprises one first pressure chamber and one second pressure chamber, thus, and two pressure chambers of piston control low pressure stage.Thus can be under the low situation of structure space demand the pulsation in the pipeline of guide pressure be reduced by two pressure chambers.
According to a further configuration of the present invention, high pressure stage comprises one first pressure chamber and one second pressure chamber.Therefore, also control two pressure chambers of high pressure stage, wherein, can under the low situation of compressor arrangement space requirement, realize little pulsation by piston.
If housing is provided with an external refrigeration device, then available simple mode realizes the cooling of compressor in the zone of low pressure stage and high pressure stage.
In order to improve cooling, conform with the destination piston and be provided with an inner cooling unit.
Piston has been advantageously provided at least one elongated hole at this, and described elongated hole is in a driving pressure chamber and is connected.Available thus simple mode realizes the inside cooling of piston by the pressure medium of the hydraulic pressure of Driven Compressor.
In the mode of structure of compressor with a high pressure stage---this high pressure stage has two pressure chambers, advantageously gives compensation volume of each pressure chamber's configuration of high pressure stage.
When compressor is used for compressed hydrogen, obtains a special advantage during especially at hydrogenation station compressed hydrogen.
Describe other advantage of the present invention and details in detail by means of the embodiment shown in the schematic accompanying drawing.Accompanying drawing is represented:
Fig. 1 reaches according to the longitudinal section of compressor of the present invention
The zoomed-in view of the part of Fig. 2 Fig. 1.
Illustrated one among Fig. 1 according to the longitudinal section that is configured to the compressor of straight line piston compressor 1 of the present invention.
Piston compressor 1 has that can vertically move, a step-like piston 4 in the housing bore 2 of housing 3, wherein, be configured with a low pressure stage 5 and a high pressure stage 6 between piston 4 and housing bore 2.
High pressure stage 6 is configured in the central region of piston compressor 1 and has two 6a of pressure chamber, 6b, and these pressure chambers are configured between the seal element 7 and piston 4 on the central region that is arranged on housing 3.For this reason, be provided with some piston section 8a, 8b in the zone in diameter transition on the step-like piston 4, wherein, the 6a of pressure chamber, the 6b of high pressure stage 6 is configured in the zone that the diameter of piston 4 increases.Shown in the position, wherein piston 4 is loaded to the right in Fig. 1, the 6a of pressure chamber in left side has the minimum 6b of pressure chamber that squeezes volume and right side and has the maximum volume that squeezes.
Low pressure stage 5 is configured in the zone that the diameter of piston 4 reduces in the both sides of high pressure stage 6 and has two 5a of pressure chamber, 5b, and these pressure chambers are at housing bore 3 and be arranged in the zone that is configured in the diameter that having of piston reduce between piston section 8a, the 8b on the piston 4.
In position shown in the piston 4, the 5a of pressure chamber in left side has the maximum 5b of pressure chamber that squeezes volume and right side and has the minimum volume that squeezes.
Piston compressor 1 can be by hydraulic driving, wherein, but at the driving pressure chamber 9a, the 9b that on the perimeter adjacent with low pressure stage 5, are configured with some hydraulic loaded on the piston 4.In position shown in the piston rod 4 with the pressure medium load driver 9a of pressure chamber of hydraulic pressure.When driving pressure chamber 9b was loaded, piston rod 4 was correspondingly loaded left in Fig. 1.
For control piston formula compressor, respectively dispose low-pressure suction valve 10a, a 10b and low pressure valve 11a, a 11b for the 5a of pressure chamber, the 5b of low pressure stage 5.Correspondingly respectively dispose a high pressure suction valve and a high-pressure valve for the 6a of pressure chamber, the 6b of high pressure stage 6, wherein, in Fig. 1, only show high pressure suction valve 12a and high-pressure valve 13a that the 6a of pressure chamber is given in configuration.
In the zone of low pressure stage 5 and high pressure stage 6, be provided with external refrigeration device 15a, 15b on the excircle of housing 2.
For further cooling piston formula compressor, piston 4 has elongated hole 16a, the 16b of the blind hole of being configured to, these elongated holes are in and are connected with driving pressure chamber 9a, 9b, thus, obtain the inside cooling of piston compressor 1 by the pressure medium of driven plunger formula compressor 1.
In addition, piston compressor 1 is provided with a stroke measurment system 17.
According to the present invention, connect compensation volume 20a, a 20b with adjustable dead volume in each 6a of pressure chamber, the 6b front of high pressure stage.
Show the compensation volume 20a that is connected 6a front, pressure chamber with the longitudinal section among Fig. 1 and Fig. 2.Configuration has identical structure for the compensation volume 20b of the 6b of pressure chamber.
Thus, by the corresponding adjusting of cylinder 23 in housing bore 28, form an adjustable dead volume that is used for the 6a of pressure chamber of high pressure stage 6 by compensation volume 20a.
Be provided with a cooling unit 27 on the housing 22 in the zone of compensation volume 20a, this cooling unit for example is made of the cooling ribs that some are arranged on the excircle of housing 22.
Shown under the situation of the incoming pressure minimum of piston compressor 1 in the position, compensation volume 20a has at cylinder 23 maximum dead volume under the situation of skew upwards in Fig. 2.The incoming pressure that on second chain of command 25 of the cylinder 23 that is configured to step piston, exists increase along with low pressure stage 5, cylinder 23 is loaded downwards in Fig. 2, thus, compensation volume 20a direction of dead volume minimum under the situation of the incoming pressure maximum of piston compressor 1 is loaded.
In piston compressor 1 work, gaseous medium flows to the 6a of pressure chamber of the high pressure stage 6 that is in the aspiration stroke via pressure valve 11a and suction valve 13a from the 5a of pressure chamber of low pressure stage 5 in compression stroke after aspiration stroke.Connect compensation volume 20a by the connecting pipeline that leads to high pressure stage 6 from low pressure stage 5, also make the medium transport that is compressed to intermediate pressure by low pressure stage 5 give compensation volume 20a and flow to adjustable dead volume thus and by cooling unit 27 coolings in the high pressure suction valve 13a downstream of high pressure stage 6.During the next aspiration stroke of high pressure stage 6, its medium is sucked into the 6a of pressure chamber of high pressure stage 6 from compensation volume 20a, come the self-forming dead volume compensation volume 20a the gaseous medium adiabatic expansion and be cooled to below the suction temperatures at this.
By making the suction volume-variation of high pressure stage 6 and compressor worked under different incoming pressures with compensation volume 20a that incoming pressure is controlled relatively, wherein, temperature by can making compressor by means of the described medium of the additional cooling of compensation volume 20a and especially cooling unit 27 especially when incoming pressure descends in the reduction of the back of low pressure stage 5, wherein, the stage pressure ratio and the heat load increase of high pressure stage 6 thus.
Claims (16)
1. compressor, be used for the compressed gaseous medium, this compressor has one and is used for that this medium is compressed to the low pressure stage of intermediate pressure and one from incoming pressure and is used for this medium is compressed to the high pressure stage of high pressure from middle pressure, is connected with a compensation volume (20a with adjustable dead volume in this high pressure stage (6) front; 20b),
It is characterized in that: by this compensation volume (20a; 20b) dead volume of Xing Chenging can be regulated relatively with incoming pressure.
2. according to the compressor of claim 1, it is characterized in that: this compensation volume (20a; 20b) when incoming pressure is maximum, be adjusted to minimum dead volume and along with the decline of incoming pressure can be towards the direction adjustment of dead volume maximum.
3. according to the compressor of claim 1 or 2, it is characterized in that: this compensation volume (20a; 20b) be configured to compensating cylinder (21), this compensating cylinder has a cylinder (23) that can move in the housing (22) of this compensation volume.
4. according to the compressor of claim 3, it is characterized in that: this cylinder (23) is provided with first chain of command (24) as step piston, and this first chain of command is arranged on this compensation volume (20a; Load 20b) and by intermediate pressure, and this cylinder has second chain of command (25), this second chain of command is loaded by incoming pressure.
5. according to one compressor in claim 1 or 2, it is characterized in that: this compensation volume (20a; 20b) be provided with a cooling unit (27).
6. according to the compressor of claim 5, it is characterized in that: this cooling unit (27) is made of the cooling ribs that some are arranged on this housing (22).
7. according to one compressor in claim 1 or 2, it is characterized in that: this compressor has a piston (4) that can vertically move in the housing (3) of compressor, this piston can be by hydraulic driving.
8. according to one compressor in claim 1 or 2, it is characterized in that: this low pressure stage (5) has one first pressure chamber (5a) and one second pressure chamber (5b).
9. according to the compressor of claim 1 or 2, it is characterized in that: this high pressure stage (6) has one first pressure chamber (6a) and one second pressure chamber (6b).
10. according to the compressor of claim 7, it is characterized in that: the housing of this compressor (3) is provided with an external refrigeration device (15a; 15b).
11. the compressor according to claim 7 is characterized in that: this piston (4) is provided with an inner cooling unit.
12. the compressor according to claim 11 is characterized in that: this piston (4) is provided with at least one elongated hole (16a; 16b), described elongated hole and a driving pressure chamber (9a; 9b) be in connection.
13. the compressor according to claim 9 is characterized in that: the each (6a of pressure chamber that gives this high pressure stage (6); 6b) compensation volume (20a of configuration; 20b).
14. the compressor according to claim 1 is characterized in that: this compressor is a piston compressor.
15. according to one the application of compressor in the above claim, this compressor is used for compressed hydrogen.
16. according to the application of the compressor of claim 15, it is characterized in that: this compressor is used in the hydrogenation station.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102005034907A DE102005034907A1 (en) | 2005-07-26 | 2005-07-26 | Compressor, in particular reciprocating compressor |
| DE102005034907.2 | 2005-07-26 | ||
| PCT/EP2006/006520 WO2007012384A1 (en) | 2005-07-26 | 2006-07-04 | Compressor, in particular piston compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101233318A CN101233318A (en) | 2008-07-30 |
| CN101233318B true CN101233318B (en) | 2011-10-19 |
Family
ID=36992587
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006800275402A Expired - Fee Related CN101233318B (en) | 2005-07-26 | 2006-07-04 | Compressor, particularly piston compressor |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US20080199327A1 (en) |
| EP (1) | EP1907701B1 (en) |
| JP (1) | JP5065267B2 (en) |
| KR (1) | KR20080025059A (en) |
| CN (1) | CN101233318B (en) |
| AU (1) | AU2006274301A1 (en) |
| DE (1) | DE102005034907A1 (en) |
| WO (1) | WO2007012384A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ITTO20120395A1 (en) * | 2012-05-03 | 2012-08-02 | Electro Power Systems Spa | BOOSTER DEVICE FOR GAS COMPRESSION |
| DE102014217897A1 (en) | 2014-09-08 | 2016-03-10 | Pressure Wave Systems Gmbh | A compressor device, a cooling device equipped therewith, and a method of operating the compressor device and the cooling device |
| CN104595155B (en) * | 2014-12-30 | 2016-06-15 | 成都烃源科技有限责任公司 | A kind of long stroke hydraulic control natural gas compressor |
| CN106988989B (en) * | 2017-05-24 | 2019-12-03 | 安徽寅时压缩机制造有限公司 | A kind of anti-reversing clutch for split-compressor |
| US20190145395A1 (en) * | 2017-11-10 | 2019-05-16 | Haskel International, Llc | Method of Construction for High Cycle Fatigue Resistant Pressure Vessels in Hydrogen Service |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1939424A (en) * | 1931-06-23 | 1933-12-12 | Chicago Pneumatic Tool Co | Variable volume control mechanism for compressors |
| US4976591A (en) * | 1990-03-02 | 1990-12-11 | Intevep, S.A. | Self lubricating, two stage variable compressor |
| CN1080027A (en) * | 1992-06-17 | 1993-12-29 | 德莱塞·兰特公司 | Gas compressor |
| CN2202804Y (en) * | 1994-01-26 | 1995-07-05 | 陈永江 | Nitrogen hydrogen compressor |
| CN1564910A (en) * | 2001-10-05 | 2005-01-12 | 韦斯特波特研究公司 | High pressure pump system for supplying a cryogenic fluid from a storage tank |
| CN1677369A (en) * | 2004-02-13 | 2005-10-05 | 英特尔公司 | Method, system and apparatus for hierarchical cache line replacement |
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| US1677369A (en) * | 1927-06-13 | 1928-07-17 | Edward A Rix | Fluid compressor |
| 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 (en) * | 1961-07-05 | 1965-06-24 | Basf Ag | Three-stage high pressure gas compressor with a piston seal |
| 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 |
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| JPS6138176A (en) * | 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 | Fluid pressure type compressor and fluid pressure control-power device of said compressor |
| US4705460A (en) * | 1985-02-26 | 1987-11-10 | Anton Braun | Bounce chambers for multi-cylinder linear engine compressors |
| US5863186A (en) * | 1996-10-15 | 1999-01-26 | Green; John S. | Method for compressing gases using a multi-stage hydraulically-driven compressor |
| BR0103443A (en) * | 2001-08-21 | 2004-03-09 | Petroleo Brasileiro Sa | Multiphase Pumping System and Method |
-
2005
- 2005-07-26 DE DE102005034907A patent/DE102005034907A1/en not_active Withdrawn
-
2006
- 2006-07-04 KR KR1020077029045A patent/KR20080025059A/en not_active Application Discontinuation
- 2006-07-04 AU AU2006274301A patent/AU2006274301A1/en not_active Abandoned
- 2006-07-04 WO PCT/EP2006/006520 patent/WO2007012384A1/en active Application Filing
- 2006-07-04 JP JP2008523163A patent/JP5065267B2/en not_active Expired - Fee Related
- 2006-07-04 CN CN2006800275402A patent/CN101233318B/en not_active Expired - Fee Related
- 2006-07-04 US US11/996,842 patent/US20080199327A1/en not_active Abandoned
- 2006-07-04 EP EP06762401.5A patent/EP1907701B1/en not_active Not-in-force
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1939424A (en) * | 1931-06-23 | 1933-12-12 | Chicago Pneumatic Tool Co | Variable volume control mechanism for compressors |
| US4976591A (en) * | 1990-03-02 | 1990-12-11 | Intevep, S.A. | Self lubricating, two stage variable compressor |
| CN1080027A (en) * | 1992-06-17 | 1993-12-29 | 德莱塞·兰特公司 | Gas compressor |
| CN2202804Y (en) * | 1994-01-26 | 1995-07-05 | 陈永江 | Nitrogen hydrogen compressor |
| CN1564910A (en) * | 2001-10-05 | 2005-01-12 | 韦斯特波特研究公司 | High pressure pump system for supplying a cryogenic fluid from a storage tank |
| CN1677369A (en) * | 2004-02-13 | 2005-10-05 | 英特尔公司 | Method, system and apparatus for hierarchical cache line replacement |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2009503321A (en) | 2009-01-29 |
| DE102005034907A1 (en) | 2007-02-01 |
| EP1907701A1 (en) | 2008-04-09 |
| AU2006274301A1 (en) | 2007-02-01 |
| US20080199327A1 (en) | 2008-08-21 |
| WO2007012384A1 (en) | 2007-02-01 |
| KR20080025059A (en) | 2008-03-19 |
| CN101233318A (en) | 2008-07-30 |
| JP5065267B2 (en) | 2012-10-31 |
| EP1907701B1 (en) | 2017-01-25 |
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| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20111019 Termination date: 20190704 |