WO2005047703A1 - Pendelschiebermaschine - Google Patents
Pendelschiebermaschine Download PDFInfo
- Publication number
- WO2005047703A1 WO2005047703A1 PCT/DE2004/002448 DE2004002448W WO2005047703A1 WO 2005047703 A1 WO2005047703 A1 WO 2005047703A1 DE 2004002448 W DE2004002448 W DE 2004002448W WO 2005047703 A1 WO2005047703 A1 WO 2005047703A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- pendulum
- groove
- head
- webs
- foot
- Prior art date
Links
Classifications
-
- 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
- F04C2/348—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 vanes positively engaging, with circumferential play, an outer rotatable member
-
- 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
- F04C2/32—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members
- F04C2/332—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 both the movement defined in groups F04C2/02 and relative reciprocation between co-operating members with vanes hinged to the outer member and reciprocating with respect to the inner member
-
- 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
- F04C2240/00—Components
- F04C2240/20—Rotors
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/18—Mechanical movements
- Y10T74/18056—Rotary to or from reciprocating or oscillating
Definitions
- the invention relates to a pendulum slide machine working by means of an eccentric orbital movement.
- the object of the invention is to develop a novel pendulum slide machine that works by means of an eccentric orbital movement, which eliminates these aforementioned disadvantages of the prior art and, in conjunction with the use of asymmetrical pendulum drivers, significantly improves the running properties, produces a uniform torque curve, and clearly causes the pulsation reduced and at the same time the maximum eccentricity compared to conventional pendulum slide machines with the same installation space significantly increased, the delivery volume increased, thereby avoiding the stability problems in the area of the pendulum web even with a significant increase in the offset angle, and also ensures optimal power transmission between the individual components of the pendulum slide machine in all speed ranges , at the same time significantly reduces susceptibility to cavitation even in very high speed ranges, thereby improving controllability the conveying effect of the pendulum slide machine is significantly increased, also the overall wear, but especially significantly reduced in the critical area of the
- a pendulum slide machine with at least one rotor set, consisting of an inner rotor (5) arranged on a drive shaft (4), which is rotatable directly in the housing by means of pendulum webs (6) provided with pendulum heads (7) and pendulum feet (12) (1) or indirectly, for example in a spool (2) mounted outer rotor (3), the pendulum webs (6) being constructed such that at the Pendulum back on the pendulum head, opposite the connection line between the center of the pendulum head circle and the pendulum foot center, a pendulum head plate (9) inclined in the direction of the pendulum foot (12) is arranged, which at its free end merges approximately at right angles into a pendulum backside sliding curve (11), the circular pendulum head (7) on the other hand merges via a pendulum head groove (8) into a pendulum front sliding curve (10) extending to the pendulum foot (12).
- pendulum webs (6) constructed in this way are arranged with their pendulum heads (7) in pan grooves (14) distributed evenly over the circumference of the outer rotor (3), a pendulum receiving web (15) on the front of the pan groove (14) and on the back of the Pan groove (14) an inclined pendulum stop surface (16) is arranged, and the pendulum webs (6) with their pendulum feet (12) are arranged in pendulum guide grooves (19), which is characterized in that the pendulum guide grooves (19) of the inner rotor (5 ) are provided with differently high groove leading edges (20) and groove trailing edges (21) such that the imaginary connecting circle diameter (17) of all groove leading edges (20) is smaller than the connecting circle diameter of all groove trailing edges (21).
- the respective required inventive difference of the connecting circle diameter is determined from the pendulum web cross section required for the power transmission and the dynamic stability and the "cranking" of the pendulum required for optimal conveyance.
- the height difference according to the invention makes it possible, on the one hand, to significantly increase the load-bearing material thickness of the pendulum webs (6) in the neck area and at the same time to realize “a larger tilt angle”.
- the rear sliding curve (11) of the pendulum is also redefined, so that, as a result of the arrangement according to the invention of groove front edges (20) and groove rear edges (21) of different heights, all problems which have hitherto appeared to be unsolvable are almost optimally solved at the same time.
- the solution according to the invention made it possible for the first time to carry out a dimensioning of the cranked pendulum geometry which at the same time met the occurring loads as well as optimal conveying, so that in all speed ranges an optimal power transmission between the individual components of the pendulum slide machine with a significant increase in the maximum eccentricity compared to conventional pendulum slide machines with the same installation space, a significantly reduced pulsation and susceptibility to cavitation, with minimized friction losses, significantly improved running properties and a significantly increased delivery volume with a significant improvement in efficiency.
- the imaginary connecting circle diameter (17) of all pendulum receiving webs (15) is clearly within the other inner contour of the outer rotor (3), and an outer rotor groove between each pendulum stop surface (16) and the pendulum receiving web (15) of the adjacent pendulum (6) (18) is arranged.
- an inner rotor groove (23) is also arranged between the groove rear edge (21) and the groove front edge (20) of the next following pendulum guide groove (19).
- the pendulum front sliding curve (10) is connected to the pendulum rear sliding curve (11) in the region of the pendulum foot (12) via a pendulum foot groove (13).
- the pendulum foot groove (13) stabilizes and at the same time guides the pendulum web (6) during the entire movement sequence in the pendulum guide groove (19) filled with the medium to be conveyed, and thus helps to ensure that a pendulum web (6), even with very large manufacturing tolerances, jams in the pendulum guide groove (19). to avoid, and at the same time minimizes the friction losses in the pendulum guide groove (19).
- the pendulum head plate (9) arranged on the pendulum head on the pendulum webs (6) on the pendulum head, relative to the connecting line between the center of the pendulum head circle and the pendulum foot center, by an angle ⁇ of 40 ° to 55 ° in the direction of the pendulum foot (12) is arranged inclined, the circular pendulum head (7) between the line of contact with the pendulum head plate (9) and a pendulum head groove (8) arranged on the front of the pendulum forming an angle ⁇ of 280 ° to 310 °.
- Figure 1 a possible embodiment of the pendulum slide machine according to the invention in a side view in section
- Figure 2 the side view of a pendulum web used according to the invention
- Figure 3 the detailed representation of a rotor set constructed according to the invention of the pendulum slide machine according to Figure 1, in side view
- Figure 4 the inner rotor of the pendulum slide machine according to the invention according to Figure 1 in side view
- Figure 5 the outer rotor of the pendulum slide machine according to the invention according to Figure 1 in side view.
- a control slide 2 is arranged in a housing 1.
- the outer rotor 3 of a rotor set is rotatably arranged therein. This rotor set consists of one arranged on a drive shaft 4
- Inner rotor 5 which is rotatable with seven pendulum webs 6
- Pendulum webs 2, the outer rotor 3 and the inner rotor 5 formed
- Pump chambers 24 are successively brought to a maximum and immediately afterwards to a minimum volume (or vice versa) with each revolution of the drive shaft 4.
- Suction kidney (s) 25 are sucked into the pump chambers 24.
- the pendulum web 6 according to the invention shown in Figure 2 is constructed such that on the back of the pendulum on the pendulum head 7, opposite the
- Pendulum foot 12 inclined pendulum head plate 9 is arranged.
- the circular pendulum head 7 sweeps between the line of contact with the pendulum head plate 9 and one arranged on the front of the pendulum
- Pendulum head groove 8 an angle ⁇ of 296 °.
- Pendulum foot 12 extending pendulum front slip curve 10 over.
- the pendulum front slip curve 10 is connected in the region of the pendulum foot 12 to the pendulum back slide curve 11 by means of a pendulum foot groove 13.
- Figure 3 shows the detailed representation of the constructed according to the invention
- the seven pendulum webs 6 are arranged with their pendulum heads 7 in pan grooves 14 evenly distributed over the circumference of the outer rotor 3.
- Pendulum receiving web 15 and on the back of each pan groove 14 an inclined pendulum stop surface 16 which merges into the outer rotor groove 18.
- An outer rotor groove 18 is arranged in each case in the pendulum receiving web 15.
- the pendulum webs 6 are with their pendulum feet 12 in the pendulum guide grooves
- Figure 4 shows the inner rotor 5 of the invention
- Pendulum slide machine according to FIGS. 1 and 3 in a side view with the pendulum guide grooves 19.
- pendulum guide grooves 19 As shown in FIG. 4, have groove front edges 20 and groove rear edges of different heights
- the imaginary connecting circle diameter of all groove leading edges 20 is always smaller than the connecting circle diameter 17 of all groove trailing edges 21.
- An inner rotor groove 23 is arranged between each groove rear edge 21 and the next groove leading edge 20.
- the outer rotor 3 is the one according to the invention
- Pendulum slide machine shown in Figure 1 in side view.
- the pendulum head groove 8 of the pendulum web 6 is almost in contact with the pendulum reception web 15 of the outer rotor 3 and ensures optimum force transmission in this end position due to its form-fitting positioning.
- the “immersion process” causes Solution presented here that the line of action of the radial thrust force acting on the respective pendulum web 6 always acts within the pendulum guide groove area on the pendulum web 6, so that even with very large eccentricity and high operating pressures in connection with the arrangement of a pendulum foot groove 13 on the pendulum foot 12, there is always optimal guidance of the pendulum web 6 is guaranteed with “flying clamping”, whereby tilting and / or bracing of the pendulum webs 6 in the pendulum guide groove 19 is excluded.
- the pendulum foot groove 13 arranged on the pendulum foot 12 also has the effect that the medium located under the pendulum foot groove 13 and to be conveyed by the pendulum foot 12 can be optimally displaced during the conveying process while avoiding pressure peaks.
- the "lowered” groove leading edge 20 according to the invention rests on the pendulum front sliding curve 10 and, due to the design according to the invention, guarantees synchronous running up to very high speed ranges with optimized power transmission properties.
- all the pendulum webs 6 move into an almost similar position which inevitably would lead to the pendulum webs 6 jamming in the respective pendulum guide grooves 19.
- the solution according to the invention ensures that even with almost centric running that do not jam the pendulum webs 6 in the associated pendulum guide grooves 19.
- pendulum slide machine which, in conjunction with the use of asymmetrical pendulum drivers, significantly improves the running properties, causes an even torque curve, significantly reduces the pulsation and, at the same time, also maximizes the eccentricity
- the delivery volume increased, while avoiding the stability problems in the area of the pendulum web even with a significant increase in the offset angle, and in addition, in all speed ranges, an optimal transmission of force between the individual components of the pendulum slide machine is effected, at the same time, the susceptibility to cavitation is very high high speed ranges significantly reduced, the controllability improved, the conveying effect of the pendulum slide machine significantly increased, also the overall wear, but significantly reduced in particular in the critical area of the pendulum foot, at the same time minimizing friction losses, and also significantly increasing the efficiency, and at the same time significantly increasing the efficiency for one Functionally reliable continuous operation, the required manufacturing accuracy is significantly reduced, at the same time the manufacturing costs are significantly reduced and not only d
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
- Centrifugal Separators (AREA)
- Compressor (AREA)
- Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
- Transmission Devices (AREA)
- Details Of Valves (AREA)
- Hydraulic Motors (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04818376A EP1687538B1 (de) | 2003-11-08 | 2004-11-05 | Pendelschiebermaschine |
DE112004002648T DE112004002648D2 (de) | 2003-11-08 | 2004-11-05 | Pendelschiebermaschine |
JP2006537061A JP4909078B2 (ja) | 2003-11-08 | 2004-11-05 | 振り子式ベーン機械 |
DE502004005927T DE502004005927D1 (de) | 2003-11-08 | 2004-11-05 | Pendelschiebermaschine |
US10/547,635 US7438543B2 (en) | 2003-11-08 | 2004-11-05 | Oscillating slide machine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10352267.0 | 2003-11-08 | ||
DE10352267A DE10352267A1 (de) | 2003-11-08 | 2003-11-08 | Pendelschiebermaschine |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005047703A1 true WO2005047703A1 (de) | 2005-05-26 |
Family
ID=34584947
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2004/002448 WO2005047703A1 (de) | 2003-11-08 | 2004-11-05 | Pendelschiebermaschine |
Country Status (7)
Country | Link |
---|---|
US (1) | US7438543B2 (de) |
EP (1) | EP1687538B1 (de) |
JP (1) | JP4909078B2 (de) |
CN (1) | CN100406735C (de) |
AT (1) | ATE383515T1 (de) |
DE (3) | DE10352267A1 (de) |
WO (1) | WO2005047703A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006061326A1 (de) | 2006-12-22 | 2008-07-03 | Beez, Günther, Dipl.-Ing. | Stelleneinrichtung für eine mengenregelbare Zellenpumpe |
CN101147001B (zh) * | 2005-10-06 | 2011-03-23 | 约马-综合塑料技术有限公司 | 叶片泵 |
EP3336358A1 (de) * | 2016-12-13 | 2018-06-20 | MAHLE Filter Systems Japan Corporation | Pumpe |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4795437B2 (ja) * | 2005-10-06 | 2011-10-19 | ヨーマ−ポリテック ゲーエムベーハー | ベーンセルポンプ |
DE102006021251B4 (de) * | 2005-10-06 | 2008-12-04 | Joma-Hydromechanic Gmbh | Flügelzellenpumpe |
DE502006008468D1 (de) * | 2006-10-10 | 2011-01-20 | Joma Polytec Gmbh | Flügelzellenmaschine, insbesondere flügelzellenpumpe |
CN101605995A (zh) * | 2007-04-10 | 2009-12-16 | 博格华纳公司 | 可变排量的双叶片泵 |
WO2009014651A1 (en) * | 2007-07-20 | 2009-01-29 | Borgwarner Inc. | Articulated vane pump with conjugate action provided by a cam profile |
WO2009014661A1 (en) * | 2007-07-20 | 2009-01-29 | Borgwarner Inc. | Articulated vane pump having multiple vanes to drive an outer rotor and provide an increased contact ratio |
DE102008054009B4 (de) * | 2008-10-30 | 2014-11-20 | Bayerische Motoren Werke Aktiengesellschaft | Flügelzellenpumpe |
DE102009004456B4 (de) * | 2009-01-13 | 2012-01-19 | Mahle International Gmbh | Mengenregelbare Zellenpumpe mit schwenkbarem Steuerschieber |
US9394893B2 (en) * | 2010-02-26 | 2016-07-19 | Mahle International Gmbh | Oscillating slide machine that pumps different fluid mediums at different pressures |
DE102010023068A1 (de) * | 2010-06-08 | 2011-12-08 | Mahle International Gmbh | Flügelzellenpumpe |
WO2012112567A1 (en) | 2011-02-15 | 2012-08-23 | Georgetown University | Small molecule inhibitors of agbl2 |
DE102011077094A1 (de) * | 2011-06-07 | 2012-12-13 | Mahle International Gmbh | Pendelschieberpumpe |
DE102011083278A1 (de) * | 2011-09-23 | 2013-03-28 | Mahle International Gmbh | Schmiermittelsystem |
JP6108967B2 (ja) * | 2013-06-06 | 2017-04-05 | 株式会社デンソー | 回転型圧縮機構 |
DE102014208579A1 (de) * | 2014-05-07 | 2015-11-12 | Mahle International Gmbh | Verfahren zum Herstellen eines Pendels einer Pendelschieberzellenpumpe |
DE102014220766B4 (de) * | 2014-10-14 | 2017-11-02 | Continental Automotive Gmbh | Pendelschiebermaschine |
JP6295923B2 (ja) * | 2014-11-12 | 2018-03-20 | アイシン精機株式会社 | オイルポンプ |
JP6444166B2 (ja) * | 2014-12-25 | 2018-12-26 | 株式会社マーレ フィルターシステムズ | 可変容量ポンプ |
JP2017048681A (ja) * | 2015-08-31 | 2017-03-09 | 株式会社マーレ フィルターシステムズ | ポンプ |
CN106401950B (zh) * | 2016-11-09 | 2018-12-18 | 浙江科博达工业有限公司 | 叶片铰链活塞复合式变排量泵 |
CN106884792B (zh) * | 2017-02-16 | 2018-08-07 | 罗金 | 一种多功能摆动叶片式多压输出旋转机械机构 |
WO2018153468A1 (en) | 2017-02-24 | 2018-08-30 | Pierburg Pump Technology Gmbh | Automotive liquid pendulum vane pump |
Citations (3)
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DE942314C (de) * | 1952-10-01 | 1956-05-03 | Otto Pfrengle | Drehkolbenpumpe mit einem in einem Zylinder exzentrisch umlaufenden Drehkolben |
DE19532703C1 (de) * | 1995-09-05 | 1996-11-21 | Guenther Beez | Pendelschiebermaschine |
EP1225337A2 (de) * | 2001-01-20 | 2002-07-24 | Günther Beez | Mengenregelbare Zellenpumpe |
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US1370810A (en) | 1919-03-08 | 1921-03-08 | Harvey F Hansen | Pump |
US1350159A (en) * | 1919-08-01 | 1920-08-17 | Sven A Johnson | Air-compressor |
US1961592A (en) * | 1929-01-18 | 1934-06-05 | Muller Wolfgang Carl | Variable capacity pump or motor |
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DE668362C (de) | 1935-05-22 | 1938-12-01 | Fluvario Ltd | Drehkolbenmaschine, bei welcher der Laeufer mit radial beweglichen Fluegeln versehen und in einem zwecks Leistungsaenderung verschiebbaren Laufgehaeuse angeordnet ist |
FR980766A (fr) * | 1943-02-26 | 1951-05-17 | Pompe à alluchons oscillants | |
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EP0601218B1 (de) | 1992-11-27 | 1997-01-22 | Andro Caric | Drehkolbenmaschine |
DE4434430C2 (de) | 1994-09-27 | 1998-12-17 | Guenther Dipl Ing Beez | Regelbare hydraulische Pendelschiebermaschine |
JP2996343B1 (ja) * | 1999-02-05 | 1999-12-27 | 威 佐藤 | 回転ピストン構造の容積形ピストン機構における屈曲ベ―ンスライド構造。 |
ES2232341T3 (es) * | 2000-03-31 | 2005-06-01 | Otice Establishment | Motor de combustion interna. |
EP1334264B1 (de) * | 2000-11-17 | 2005-02-09 | Honeywell International Inc. | Flügelzellenmaschine |
-
2003
- 2003-11-08 DE DE10352267A patent/DE10352267A1/de not_active Withdrawn
-
2004
- 2004-11-05 DE DE502004005927T patent/DE502004005927D1/de active Active
- 2004-11-05 US US10/547,635 patent/US7438543B2/en active Active
- 2004-11-05 CN CNB2004800324594A patent/CN100406735C/zh active Active
- 2004-11-05 AT AT04818376T patent/ATE383515T1/de not_active IP Right Cessation
- 2004-11-05 WO PCT/DE2004/002448 patent/WO2005047703A1/de active IP Right Grant
- 2004-11-05 EP EP04818376A patent/EP1687538B1/de active Active
- 2004-11-05 JP JP2006537061A patent/JP4909078B2/ja not_active Expired - Fee Related
- 2004-11-05 DE DE112004002648T patent/DE112004002648D2/de not_active Expired - Fee Related
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE942314C (de) * | 1952-10-01 | 1956-05-03 | Otto Pfrengle | Drehkolbenpumpe mit einem in einem Zylinder exzentrisch umlaufenden Drehkolben |
DE19532703C1 (de) * | 1995-09-05 | 1996-11-21 | Guenther Beez | Pendelschiebermaschine |
EP1225337A2 (de) * | 2001-01-20 | 2002-07-24 | Günther Beez | Mengenregelbare Zellenpumpe |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101147001B (zh) * | 2005-10-06 | 2011-03-23 | 约马-综合塑料技术有限公司 | 叶片泵 |
DE102006061326A1 (de) | 2006-12-22 | 2008-07-03 | Beez, Günther, Dipl.-Ing. | Stelleneinrichtung für eine mengenregelbare Zellenpumpe |
DE102006061326B4 (de) * | 2006-12-22 | 2012-02-16 | Mahle International Gmbh | Stelleneinrichtung für eine mengenregelbare Zellenpumpe |
EP3336358A1 (de) * | 2016-12-13 | 2018-06-20 | MAHLE Filter Systems Japan Corporation | Pumpe |
Also Published As
Publication number | Publication date |
---|---|
JP4909078B2 (ja) | 2012-04-04 |
DE502004005927D1 (de) | 2008-02-21 |
JP2007510082A (ja) | 2007-04-19 |
EP1687538B1 (de) | 2008-01-09 |
DE10352267A1 (de) | 2005-06-16 |
EP1687538A1 (de) | 2006-08-09 |
CN1875190A (zh) | 2006-12-06 |
US7438543B2 (en) | 2008-10-21 |
CN100406735C (zh) | 2008-07-30 |
ATE383515T1 (de) | 2008-01-15 |
US20060191360A1 (en) | 2006-08-31 |
DE112004002648D2 (de) | 2006-09-21 |
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