WO2005010368A1 - Aggregat zum fördern von kraftstoff zu einer brennkraftmaschine - Google Patents
Aggregat zum fördern von kraftstoff zu einer brennkraftmaschine Download PDFInfo
- Publication number
- WO2005010368A1 WO2005010368A1 PCT/DE2004/001257 DE2004001257W WO2005010368A1 WO 2005010368 A1 WO2005010368 A1 WO 2005010368A1 DE 2004001257 W DE2004001257 W DE 2004001257W WO 2005010368 A1 WO2005010368 A1 WO 2005010368A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rotor
- sections
- pump
- pressure
- ellipse
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
- F01C21/10—Outer members for co-operation with rotary pistons; Casings
- F01C21/104—Stators; Members defining the outer boundaries of the working chamber
- F01C21/106—Stators; Members defining the outer boundaries of the working chamber with a radial surface, e.g. cam rings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
- F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
- F04C2/3445—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the vanes having the form of rollers, slippers or the like
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2250/00—Geometry
- F04C2250/30—Geometry of the stator
- F04C2250/301—Geometry of the stator compression chamber profile defined by a mathematical expression or by parameters
Definitions
- the invention is based on a unit for delivering fuel according to the preamble of the main claim.
- a roller cell pump is already known from DE 28 35 457 C2, in which a molded raceway composed of elliptical sections results from two different equations.
- the form raceways that can be generated from the equations are all mathematically similar for different rotor diameters R 2 , not optimal with regard to the function of the aggregate, for example the hot gasoline delivery, the efficiency and the wear behavior, and discontinuous at the transitions between the ellipse halves in the case of eccentricities.
- features of the main claim have the advantage that an improvement in the function of the unit is achieved in a simple manner by a course of the radii of the ellipse sections, at least in sections, of one of the equations mentioned in the main claim equivalent.
- the mold path can be optimally adapted to the function required in the respective region of the mold path, for example the generation of a negative pressure in a suction area, the generation of an excess pressure in one Pressure range, the seal in a sealing area or the setting of a constant volume in a changeover area, are adjusted.
- the parameter n lies in a changeover range between greater than or equal to 1.9 and less than or equal to 2.1, since in this way the volume of the pump work spaces remains constant, so that no pressure peaks occur.
- Fig.l shows an aggregate for requesting fuel
- Fig.2 shows an aggregate with a molded track according to the invention
- Fig.3 shows a molded track according to the invention.
- Fig.l shows an inventive unit for requesting fuel to an internal combustion engine.
- the unit according to the invention has, for example, a cylindrical housing 1 with at least one input channel 2 and one output channel 3.
- the input channel 2 of the unit is connected, for example, via a suction line 6 to a storage container 7, in which, for example, fuel is stored.
- the unit is connected to an internal combustion engine 9, for example, via a pressure line 8.
- the unit is, for example, a so-called roller cell pump or a so-called vane pump.
- a roller cell pump is known for example from DE 101 15 866 AI, the content of which is expressly intended to be part of the disclosure of this application.
- the housing 1 of the unit has a pump part 12 and a drive part 13.
- the pump part 12 has a pump chamber 14 which is cylindrical, for example.
- a rotor 15 is rotatably mounted in the pump chamber 14, the rotor 15 and the pump chamber 14 being arranged eccentrically to one another.
- the rotor 15 is driven by an actuator 18 provided in the drive part 13, for example an armature of an electric motor, via a drive shaft 19.
- the pump chamber 14 is delimited by two end walls opposite one another in the direction of a rotationally symmetrical axis 20 of the rotor 15, a first one
- End channel 21 facing input channel 2 and a second end wall 22 facing output channel 3, and in the radial direction with respect to axis 20 from an annular wall 23.
- the first end wall 21 is formed on the inside of a, for example, disk-shaped suction cover 26 facing the rotor 15, and the second end wall 22 on the inside of a, for example, disk-shaped pressure cover 27 facing the rotor 15.
- the ring wall 23 is, for example, on the inside of an annular face facing the rotor 15 Intermediate cover 28 is provided.
- the ring wall 23 can, for example, be integrally connected to the intermediate cover 28 as a coating or be designed as a separate sliding ring.
- the separate glide can m the annular intermediate cover 28, for example, can be pressed in, glued in, welded in or screwed in.
- the intermediate cover 28 is arranged, for example, between the disc-shaped suction cover 26 and the disc-shaped pressure cover 28.
- the intermediate cover 28 can also be connected in one piece to the suction cover 26 or the pressure cover 27.
- the intermediate cover 28 with the ring wall 23 is arranged, for example, eccentrically to the rotor 15.
- Both the suction cover 26 and the intermediate cover 28 as well as the pressure cover 27 and the intermediate cover 28 are in each case non-positively connected, for example by means of a plurality of screws, or for final connection.
- the Geh use 1 has a cylinder portion 31 which has the suction cover 26 on the front side facing the pump part 12 and a connection cover 32 on the front side facing the drive part 13.
- the suction cover 26 and the connection cover 32 close the cylinder section 31 of the housing 1 tightly from the external environment, for example by engaging in the cylinder section 31 and with the circumference at least in sections abutting the inside of the cylinder section 31.
- the inlet channel 2 of the housing 1 is arranged, for example, on the suction cover 26 and is connected in the direction of flow to a pump chamber inlet 33 which flows into the pump chamber 14.
- the output channel 3 of the housing 1 is arranged, for example, on the connection cover 32.
- the connection cover 32 also has, for example, electrical connection elements 36 for contacting the actuator 18 provided in the housing 1.
- a pump chamber outlet 34 for example, is arranged in the pressure cover 27 of the unit and connects the pump chamber 14 to a pressure chamber 35 of the housing 1.
- the pump chamber outlet 34 can also be provided on the suction cover 26.
- the pressure chamber 35 is delimited radially by the cylinder section 31 and axially by the pressure cover 27 and the connection cover 32.
- the actuator 18 is arranged, which drives the drive shaft 19 in rotation.
- the pressure cover 27 has a drive shaft channel 37, through which the drive shaft 19 extends into the pump chamber 14 in order to drive the rotor 15 in rotation.
- the drive shaft 19 is mounted, for example, at the end facing away from the actuator 18 in a bearing recess 38 of the suction cover 26.
- Pressure chamber 35 is at least indirectly connected to internal combustion engine 9 via output channel 3 of housing 1 and pressure line 8.
- the rotor 15 is, for example, a cylindrical grooved disk.
- a plurality of sealing bodies 39 distributed over the circumference, which in the case of a roller cell pump are designed, for example, as cylindrical rollers.
- the sealing bodies 39 are, for example, m radial guide grooves 40 of the
- FIG. 2 shows an aggregate with a molding track according to the invention.
- a plurality of guide grooves 40 are arranged uniformly distributed over the circumference of the rotor 15.
- the number of guide grooves 40 is preferably odd.
- the guide grooves 40 pass through the rotor 15 in the axial direction from one end face of the rotor 15 to the other end face.
- the guide grooves 40 run radially inward from the outer circumference with two side flanks 43, for example arranged parallel to one another, and each end in an, for example, arcuate groove base 44.
- a sealing body 39 is provided in each guide groove 40.
- the sealing body 39 is movably mounted between the groove base 44 and the mold track 24 in the direction of the side flanks 43.
- the distance between the side flanks 43 of a guide groove 40 is, for example, only slightly larger than a dimension, for example the diameter, of the sealing body 39, since the sealing bodies 39 are guided laterally in the radial direction in this way.
- the sealing bodies 39 are moved in the direction of the mold race 24 during the rotation of the rotor 15 and are generally in contact with the mold race 24.
- At least one compensation pocket 51 is arranged, which extends axially and radially inwards from an end face of the rotor 15.
- the space delimited by the rare flanks 43, the groove base 44 and the sealing body 39 of a guide groove 40 forms a groove space 54, which is connected via the associated compensation pocket 51 to the adjacent gap space 49 which leads the direction of rotation of the rotor 15.
- the groove space 54, the equalization pocket 51 and the gap space 49 form a pump work space 50.
- the pump chamber inlet 33 and / or the pump chamber outlet 34 are designed, for example, as a kidney-shaped groove.
- the pump chamber inlet 33 has, for example, three kidney-shaped inlet grooves, with two inner inlet grooves 55 in the area of the groove space 54 radially outside the groove base 44 and an outer inlet groove 56, for example for example radially in the region of the ring wall 23.
- the pump chamber inlet 33 is arranged, for example, in such a way that each pump work chamber 50 is temporarily connected to the pump chamber inlet 33 by overlap when the rotor 15 rotates, and liquid flows into the respective pump work chamber 50 via the inlet channel 2 and the pump chamber inlet 33.
- the pump chamber outlet 34 has, for example, at least one outlet groove 57, which is arranged, for example, in the region of the groove space 54 radially outside the groove base 44 and at a distance in the circumferential direction from the inlet grooves 55, 56.
- the pump chamber outlet 34 is arranged, for example, such that everyone
- Pump work space 50 is temporarily connected to the pump chamber outlet 34 by overlap when the rotor 15 rotates and liquid flows from the respective pump work chamber 50 into the pump chamber outlet 34.
- the molding track 24 consists of a suction area 58, a reversing area 59, a pressure area 60 and a sealing area 61.
- the suction area 58 lies in the area of the pump chamber entrance 33 between the narrow gap 45 and the wide gap 46, the reversing area 59 in the area of the wide gap 46 between the pump chamber entrance 33 and the pump chamber outlet 34, the pressure region 60 in the region of the pump chamber outlet 34 and the sealing region 61 in the region of the narrow gap 45.
- the gap width of the gap 48 increases from the narrow gap 45 in the direction of rotation of the rotor 15 to the wide gap 46, so that the volume of the individual pump working spaces 50 in the direction of rotation of the rotor 05/010368
- the filling of the respective pump work space 50 is ended when the pump work space 50 is no longer connected to the pump chamber inlet 33 by rotating the rotor 15 further.
- the pump chamber 50 is then sealed off from the environment and entered the reversing area 59.
- the pump working space 50 is closed and in this way seals the pump chamber outlet 34 from the pump chamber inlet 33.
- the mold track 24 is designed such that the volume of the closed pump work space 50 remains at least approximately constant, so that there are no undesirable pressure increases in the closed pump work space 50.
- the reduction in volume of the closed pump work space 50 would cause a compression of the liquid and thereby an increase in pressure in the pump work space 50 in question.
- Large increases in pressure in the closed pump work space 50 lead to a strong oscillation of the sealing body 39, since these are initially pressed radially inward by the high pressure in the closed pump work space 50, so that a leak occurs in the pump work space 50 leading in advance, and through that Leakage caused pressure drop in the Pump working space 50 are suddenly printed again on the mold track 24.
- the impact of the sealing bodies 39 on the mold raceway 24 would result in a high degree of wear on the mold raceway 24 and / or on the sealing bodies 39.
- the occurrence of so-called cavitation is also at least reduced, which is caused by the formation of vapor bubbles caused by the liquid pressure falling below the vapor pressure and the sudden collapse of the vapor bubbles on the
- Mold raceway 24 or on surfaces of the rotor 15 can also cause wear on the mold raceway 24 or on the rotor 15. Since cavitation occurs in roller cell pumps mainly with hot gasoline, the function of the unit according to the invention is also improved with hot gasoline.
- the respective pump work space 50 is emptied in that a pressure is built up by reducing the volume of the respective pump work space 50 and the liquid is thus printed from the pump work space 50 into the pump chamber outlet 34. This happens as soon as the pump chamber outlet 34 overlaps with the respective pump working chamber 50 when the rotor 15 rotates. The pump chamber outlet 34 is then open to the relevant pump work space 50.
- the sealing area 61 seals the pressure area 60 from the suction area 58, so that as far as possible no leakage occurs from the pressure area 60 into the suction area 58.
- the radial gap width between the rotor 15 and the mold track 24 in the sealing area 61 is as small as possible and the sealing area 61 is to be as large as possible so that the liquid of the respective pump working chamber 50 is emptied as completely as possible in the direction of the pump chamber outlet 34 and not as 05/010368
- the mold track 24 is composed of at least two, for example four, different ellipse sections, the radii, the slopes and the curvatures of the different ellipse sections being the same at the transitions.
- the ellipse sections of the mold raceway 24 have a common ellipse center point M e , which sj by a double value of the eccentricity . is shifted from a center point M of the rotor 15 in the direction of an axis formed by the wide gap 46 and the narrow gap 45.
- FIG. 3 shows a molding track according to the invention.
- the radius of the cylindrical rotor 15 is designated R 2 in FIG. 3 and the radius of a circle 64 which extends through the wide gap 46 and the narrow gap 45 and has a center point M ⁇ is Rl.
- the center point M ⁇ is shifted by the eccentricity s x relative to the center point M of the rotor 15 in the direction of an axis formed by the wide gap 46 and the narrow gap 45.
- the mold path 24 can be separated from each other by changing the parameters n and Si contained in equations Gll and G12 for each ellipse section with regard to the function required in the respective region of the mold path 24, for example generating a negative pressure in the suction region 58, avoiding pressure increases and Cavitation in the reversing area 59, the generation of an overpressure in the pressure area 60 and the sealing function in the sealing area 61 can be optimized.
- the shape raceways 24 resulting from the equations Gll and G12 when the parameters n and s ⁇ are varied are at least partially not mathematically similar.
- the radius p of an elliptical section arranged in the sealing area 61 can be adapted in such a way that the molding track 24 extends very closely over a large angular area with a small radial gap dimension along the rotor 15.
- the sealing effect of the Sealing area 61 is very good in this way, so that the efficiency of the unit is higher than in the prior art.
- the radius p of an elliptical section arranged in the suction area 58 can be adapted by changing the parameter n such that the volume change of the pump work space 50 increases significantly in the direction of rotation, so that a high negative pressure in the pump work space 50 and a large gap space 49 arise. In this way, the
- the radius p of an ellipse section arranged in the reversing area 59 can be adapted such that the volume of the closed pump working space 50 remains approximately constant over a certain angular range, so that pressure peaks which arise are at least reduced.
- This angular range is 80 degrees, for example
- the at least approximately constant volume of the closed pump working space 50 avoids unnecessary radial acceleration of the sealing body 39 and cavitation.
- the molding track 24 is thereby less mechanically loaded, so that the wear is reduced and the life of the molding track 24 is increased.
- the parameter n is preferably in the range between greater than or equal to 1.9 and less than or equal to 2.1, since the volume of the closed pump working space 50 remains at least approximately constant in this interval. However, the parameter n can also be less than 1.9 or greater than 2.1.
- the eccentricity Si By changing the eccentricity si, the gap 48 n of the pump chamber 14 and thus the volume of the Pump workrooms 50 changed. If the eccentricity Si is changed in such a way that the gap 48 increases, the volume flow required by the unit at the same speed of the rotor 15 increases.
- the eccentricity Si is less than or equal to a radius R of the sealing body 39 and is preferably in the range between 0.9 and 1.4.
- the mold career 24 is divided into quadrants I to IV, for example.
- a first quadrant I begins in the wide gap 46 and lies in the angular range of ⁇ between 0 and 90 degrees, a second quadrant II in the angular range of ⁇ between 90 and 180 degrees up to the narrow gap 45, a third quadrant III in the angular range of ⁇ between 180 and 270 Degrees and a fourth quadrant IV in the angular range of ⁇ between 270 and 360 degrees.
- the mold path 24 can consist of two ellipse halves, for example the first ellipse section being arranged in the first quadrant I and in the fourth quadrant IV and the second ellipse section being arranged in the second quadrant II and in the third quadrant III.
- the course of the radius of the first ellipse section is calculated in this exemplary embodiment, for example according to equation Gll and the course of the radius of the second ellipse section according to equation G12.
- the molded track 24 can also have three ellipse sections, the first ellipse section running over two quadrants, for example, and the second ellipse section and the third ellipse section each running over a quadrant.
- the course of the radius of the first ellipse section and of the third ellipse section is calculated, for example, according to equation Gll and the course of the radius of the second ellipse section, for example according to equation G12.
- the mold path 24 can also have four ellipse sections, one ellipse section each taking up one of the quadrants I, II, III, IV.
- the course of the radius of the first ellipse section and the fourth ellipse section is calculated, for example, according to equation Gll and the course of the radius of the second ellipse section and the third
- the elliptical sections of the molding track 24 can run completely over one or more quadrants I, II, III, IV or only over part of one or more quadrants I, II, III, IV.
- Each section of the ellipse can be calculated using one of the two equations Gll and G12.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04738708A EP1687537A1 (de) | 2003-07-22 | 2004-06-17 | Aggregat zum fördern von kraftstoff zu einer brennkraftmaschine |
US10/565,560 US7300267B2 (en) | 2003-07-22 | 2004-06-17 | Unit for delivering fuel to an internal combustion engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10333190A DE10333190A1 (de) | 2003-07-22 | 2003-07-22 | Aggregat zum Fördern von Kraftstoff zu einer Brennkraftmaschine |
DE10333190.5 | 2003-07-22 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005010368A1 true WO2005010368A1 (de) | 2005-02-03 |
Family
ID=34088715
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2004/001257 WO2005010368A1 (de) | 2003-07-22 | 2004-06-17 | Aggregat zum fördern von kraftstoff zu einer brennkraftmaschine |
Country Status (5)
Country | Link |
---|---|
US (1) | US7300267B2 (de) |
EP (1) | EP1687537A1 (de) |
CN (1) | CN1826467A (de) |
DE (1) | DE10333190A1 (de) |
WO (1) | WO2005010368A1 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006031510B4 (de) * | 2006-07-07 | 2016-03-03 | Robert Bosch Gmbh | Förderaggregat |
DE102007011792A1 (de) | 2006-10-02 | 2008-04-03 | Robert Bosch Gmbh | Förderaggregat |
DE102007019283A1 (de) | 2007-04-24 | 2008-11-06 | Robert Bosch Gmbh | Förderaggregat |
DE102010041990A1 (de) | 2010-10-05 | 2012-04-05 | Robert Bosch Gmbh | Aggregat zum Fördern von Kraftstoff |
JP6227489B2 (ja) | 2014-06-18 | 2017-11-08 | 愛三工業株式会社 | ベーンポンプ |
DE102015224357A1 (de) | 2015-12-04 | 2017-06-08 | Robert Bosch Gmbh | Förderaggregat |
DE102016211596A1 (de) | 2016-06-28 | 2017-12-28 | Robert Bosch Gmbh | Förderaggregat |
US11701668B1 (en) | 2020-05-08 | 2023-07-18 | 10X Genomics, Inc. | Methods and devices for magnetic separation |
US11946038B1 (en) | 2020-05-29 | 2024-04-02 | 10X Genomics, Inc. | Methods and systems including flow and magnetic modules |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2835457A1 (de) * | 1978-08-12 | 1980-03-06 | Bosch Gmbh Robert | Foerderaggregat fuer fluessigkeiten |
US4480973A (en) * | 1981-07-13 | 1984-11-06 | Diesel Kiki Co., Ltd. | Vane compressor provided with endless camming surface minimizing torque fluctuations |
US4737090A (en) * | 1985-05-30 | 1988-04-12 | Nippondenso Co., Ltd. | Movable vane compressor |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5827895A (ja) * | 1981-08-12 | 1983-02-18 | Hitachi Ltd | ベ−ン形回転機 |
DE3824882A1 (de) * | 1988-07-19 | 1990-01-25 | Mannesmann AG, 4000 Düsseldorf | Fluegelzellenverdichter |
-
2003
- 2003-07-22 DE DE10333190A patent/DE10333190A1/de not_active Withdrawn
-
2004
- 2004-06-17 WO PCT/DE2004/001257 patent/WO2005010368A1/de not_active Application Discontinuation
- 2004-06-17 CN CNA2004800212739A patent/CN1826467A/zh active Pending
- 2004-06-17 EP EP04738708A patent/EP1687537A1/de not_active Withdrawn
- 2004-06-17 US US10/565,560 patent/US7300267B2/en not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2835457A1 (de) * | 1978-08-12 | 1980-03-06 | Bosch Gmbh Robert | Foerderaggregat fuer fluessigkeiten |
US4480973A (en) * | 1981-07-13 | 1984-11-06 | Diesel Kiki Co., Ltd. | Vane compressor provided with endless camming surface minimizing torque fluctuations |
US4737090A (en) * | 1985-05-30 | 1988-04-12 | Nippondenso Co., Ltd. | Movable vane compressor |
Also Published As
Publication number | Publication date |
---|---|
US20070003422A1 (en) | 2007-01-04 |
CN1826467A (zh) | 2006-08-30 |
EP1687537A1 (de) | 2006-08-09 |
US7300267B2 (en) | 2007-11-27 |
DE10333190A1 (de) | 2005-02-24 |
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