WO2008124174A1 - Pompe à double aube à déplacement variable - Google Patents

Pompe à double aube à déplacement variable Download PDF

Info

Publication number
WO2008124174A1
WO2008124174A1 PCT/US2008/004616 US2008004616W WO2008124174A1 WO 2008124174 A1 WO2008124174 A1 WO 2008124174A1 US 2008004616 W US2008004616 W US 2008004616W WO 2008124174 A1 WO2008124174 A1 WO 2008124174A1
Authority
WO
WIPO (PCT)
Prior art keywords
vane
axis
series
vanes
pump
Prior art date
Application number
PCT/US2008/004616
Other languages
English (en)
Inventor
Chengyun Guo
Original Assignee
Borgwarner Inc.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Borgwarner Inc. filed Critical Borgwarner Inc.
Priority to US12/594,277 priority Critical patent/US20100119396A1/en
Priority to JP2010503055A priority patent/JP2010523896A/ja
Priority to EP08742711A priority patent/EP2150702A1/fr
Publication of WO2008124174A1 publication Critical patent/WO2008124174A1/fr

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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis

Definitions

  • the present invention relates to sliding vane pumps; more particularly, the present invention relates to sliding vane pumps having a stacked integrated vane configuration.
  • Sliding vane pumps are commonly used to transfer fluid from an inlet port to an outlet port.
  • they have a ring which is eccentric, and an inner rotor; the inner rotor is typically fixed to and rotates with a shaft, and a series of vanes slide in and out of a set of vane slots.
  • the vanes will slide along the inner surface of the eccentric ring.
  • the eccentricity between the inner rotor and the eccentric ring can be varied to vary the amount of fluid that is displaced by the pump.
  • the present invention includes a variable displacement pump having an inner rotor rotatable about a first axis having at least two slots, with the slots substantially extending diametrically through the width of the inner rotor.
  • the present invention also includes at least two vanes, each located in a distinct one of said at least two slots.
  • the pump also has an outer rotor rotatable about a second axis and operably associated with the inner rotor.
  • the outer rotor has two or more recesses, each configured to receive one of said at least two vanes.
  • the pump also includes an expandable chamber formed by the outer rotor and the inner rotor, and an eccentric ring surrounding the outer rotor.
  • a housing having an eccentric ring located within the housing for adjusting the relative relationship between the first axis and the second axis in order to vary the displacement of the pump.
  • Figure 1 is a sectional side view of a sliding vane pump with the outer rotor aligned with the inner rotor, according to the present invention
  • Figure 3 is an exploded view of a sliding vane pump, according to the present invention.
  • Figure 4 a perspective view of a vane used in a sliding vane pump, according to the present invention
  • Figure 5 is a side view of a vane used in a sliding vane pump, according to the present invention
  • Figure 6 is a perspective view of a hub and inner rotor used in a sliding vane pump according to the present invention
  • Figure 7 is a perspective view of an alternate embodiment of a sliding vane pump with the cover and housing removed, according to the present invention
  • Figure 8 is a perspective view of a rotor used in an alternate embodiment of a sliding vane pump, according to the present invention
  • Figure 9 is an first exploded view of an alternate embodiment of a sliding vane pump, according to the present invention.
  • Figure 10 is a second exploded view of an alternate embodiment of a sliding vane pump, according to the present invention.
  • a sliding vane pump according to the present invention is generally shown at 10.
  • the pump 10 has an inner rotor 12 which rotates about a first axis 14.
  • the inner rotor 12 also has a series of slots 16 for receiving a plurality of vanes 18.
  • the vanes 18 have a first side 20 which is offset and parallel to a second side 22.
  • the vanes 18 also have a third side 21 which is parallel to and equal in length compared to a fourth side 23. Both the third side 21 and fourth side 23 serve as a flat engagement 24.
  • the vane 18 also includes an extension 26 which is of a reduced width compared to the remainder of the vane 18.
  • the pump 10 also has an outer rotor 28 which rotates about a second axis 30, and has recesses 32 for receiving the flat engagements 24 of the vanes 18.
  • the first side 20 being offset from the second side 22 creates an angle
  • an eccentric ring 34 located within a housing 36.
  • the housing 36 also includes an inlet port 40 for delivering fluid into the expandable chamber 38, and an outlet port 42 for receiving fluid from the expandable chamber 38.
  • the eccentric ring 34 includes a flange 44, a pivot hole 46, and a pivot pin 47 received in the pivot hole 46.
  • the pivot hole 46 and pivot pin 47 connect the eccentric ring 34 to the housing 36, so as to allow the eccentric ring 34 to pivot about the pivot pin 47.
  • the flange 44 is also connected to a bias mechanism such as a spring on one side, and a piston on the opposite side, such that force can be applied to the flange 44, changing the eccentricity between the inner rotor 12 and the outer rotor 28, the function of which will more clearly be described later.
  • the inner rotor 12 is affixed to, and driven by a hub 48.
  • the inner rotor 12 turns and applies force to and drives the vanes 18.
  • the flat engagement 24 of the first end 20 and the second end 22 then applies force to the recesses 32 of the outer rotor 28.
  • the recesses 32 are located at an angle which is identical to the angle 27 of the vanes 18, the recesses 32 are in flush contact with the flat engagements 24, allowing the flat engagements 24 to apply force to the recesses 32, and drive the outer rotor 28.
  • the outer rotor 28 is allowed to rotate relative to the eccentric ring 34 because of a hydrodynamic journal bearing 50 located therebetween.
  • the hydrodynamic journal bearing 50 in this embodiment is a hydrodynamic film which minimizes friction between the outer rotor 28 and the eccentric ring 34.
  • the hydrodynamic journal bearing 50 could also be a ball bearing, a type of grease, or any other device which would reduce friction between the outer rotor 28 and the eccentric ring 34.
  • the pump 10 has the ability to vary the amount of fluid pumped from the inlet port 40 to the outlet port 42.
  • the first axis 14 of the inner rotor 12 and the second axis 30 of the outer rotor 28 are aligned.
  • the first axis 14 is aligned with the second axis 30, no fluid is transferred from the inlet port 40 to the outlet port 42.
  • the eccentric ring 34 will pivot about the pivot pin 47 located in the pivot hole 46.
  • the outer rotor 28 will move as well.
  • the outer rotor 28 can be moved to a maximum position shown in Figure 2.
  • the amount of fluid in the expandable chamber 38 will reach a maximum volume, and then the expandable chamber 38 will begin to compress the fluid.
  • the expandable chamber 38 will compress the fluid between the vanes 18 even further as the inner rotor 12 and outer rotor 28 rotate, and the vanes 18 move across the outlet port 42.
  • the contraction of the fluid between each of the vanes 18 will force the fluid through the outlet port 42.
  • the flat engagement 24 of the vanes 18 are allowed to slide in the recesses 32, while still transferring rotational force to the outer rotor 28.
  • each vane 18 has an extension 26 formed as a portion of each vane 18.
  • the width of each extension 26 is narrower than the overall width of the vane 18.
  • Each extension 26 is also located in a different location along the width of the vane 18. This allows the vanes 18 to "stack" together, allowing all the vanes 18 to be inserted into a corresponding slot 16 in the inner rotor 12.
  • the extension 26 of the first vane 52 is adjacent to the extension 26 of the second vane 54
  • the extension 26 of the second vane 54 is adjacent to the extension 26 of the third vane 56
  • the extension 26 of the third vane 56 is adjacent to the extension 26 of the fourth vane 58.
  • Each extension 26 is adjacent to one another, but will be at a different angle relative to one another because of each vane 18 being located in a corresponding slot 16 in the inner rotor 12.
  • the present invention is not limited to having four vanes 18, as described above.
  • the number of vanes 18 can be changed to suit any particular application requiring a sliding vane pump 10 of the present invention.
  • the width of each extension 26 is approximately 25% of the total width of each vane 18. If more or less vanes 18 were used, the width of the extension 26 would change proportionately. For example, if six vanes were used, each extension would be 1/6 of the total width of the vane 18; if two vanes 18 were used, the width of each extension 26 would be half of the total width of the vane 18.
  • the present invention has several advantages over other types of sliding vane pumps and articulated vane pumps.
  • the sliding vane pump 10 of the present invention has a lower number of vanes 18, but still performs as effectively, and has higher volumetric efficiency.
  • the vanes 18 having the flat engagements 24 driving the outer rotor 28 in the manner described by the present invention reduces the amount of wear on the flat engagements 24 and the outer rotor 28, the amount of contact stress on the vanes 18 is also reduced when compared to a conventional sliding vane pump.
  • the engagement between the flat engagements 24 of the vanes 18 and the recesses 32 also provides for the ability to prime the pump 10 at start up. This eliminates additional components such as guide rings and/or oil pressure, which are used to prime typical sliding vanes pumps.
  • the pump 10 of the present invention is also facilitates easier assembly during manufacturing, and is more packaging efficient.
  • the integrated structure of the vanes 18 also eliminates or reduces the centrifugal effect. Noise, vibration, and harshness (NVH) is improved because the vanes 18 are more dynamically balanced, and there is an increased resistance to contamination which can inhibit performance.
  • NDH Noise, vibration, and harshness
  • the pump 10 shown in Figures 7-10 includes a straddle support inner rotor, generally shown at 60.
  • the inner rotor 60 also includes a series of slots 62.
  • the slots 62 of this embodiment differ from the first embodiment in that two of the slots 62 are elongated slots 64, and two of the slots 62 are not elongated slots 66.
  • the inner rotor 60 also includes two hub portions 68, and a series of vane supports 70, which are used to support a series of vanes.
  • two of the vanes are multi-piece vanes 76, and two of the vanes are single piece vanes 78.
  • the single piece vanes 78 are similar to the first vane 52 and fourth vane 58, respectively, of the first embodiment.
  • the multi-piece vanes 76 are similar to the second vane 54 and third vane 56, respectively, with the exception that the multi-piece vanes 76 are divided into two parts.
  • the extensions 26 are divided in half.
  • the multi-piece vanes 76 are inserted into the non- elongated slots 66, and the single piece vanes 78 are inserted into the elongated slots 64.
  • the function of the elongated slots 64 is to allow the single piece vanes 78 to be inserted through the inner rotor 60. More specifically, the elongated slots 64 allow the widest part of the vane 78 to be inserted through the rotor 60 without being blocked by or receiving any interference from the extensions 26 of any of the other vanes.
  • the vanes will also engage the recesses 32 of the outer rotor 28 in a similar manner to the first embodiment. Once all of the vanes are inserted into the slots 62, the housing 36 will prevent the vanes from sliding out of the slots 62 because the inside surface of the housing 36 will be in sliding contact with each of the vanes.
  • the inner rotor 60 is supported on both sides of the vane supports 70 by the hub portions 68; this provides additional structural support and allows for an increased pressure capacity of the pump 10.
  • the inner rotor 60 is driven by the shaft; the rotor 60 turns and applies force to the vanes, and the vanes in turn apply force to the recesses 32, driving the outer rotor 60 in a similar manner compared to the previous embodiment.
  • the flange 44 is inserted into a recess 80 of a piston 82.
  • the piston 82 includes a hollow portion 84 which receives a portion of a return spring 86.
  • On the opposite side of the piston 82 is a flat portion 88 which receives pressure from fluid.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

La présente invention concerne une pompe à déplacement variable dotée d'un rotor interne pouvant tourner autour d'un premier axe et ayant au moins deux fentes. La pompe dispose également d'au moins deux aubes, chacune située dans l'une des fentes distinctes. La pompe présente également un rotor extérieur pouvant tourner autour d'un second axe, associé de manière opérationnelle au rotor interne, le rotor externe ayant deux cavités ou plus, chacune étant configurée pour recevoir l'une des aubes. La pompe comprend également une chambre expansible formée par le rotor extérieur et le rotor interne, une bague excentrique entourant le rotor extérieur, et un logement. La bague excentrique est située dans le logement de façon à régler la relation correspondante entre le premier axe et le second axe, afin de modifier le déplacement de la pompe.
PCT/US2008/004616 2007-04-10 2008-04-10 Pompe à double aube à déplacement variable WO2008124174A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US12/594,277 US20100119396A1 (en) 2007-04-10 2008-04-10 Variable displacement dual vane pump
JP2010503055A JP2010523896A (ja) 2007-04-10 2008-04-10 可変容量型デュアルベーンポンプ
EP08742711A EP2150702A1 (fr) 2007-04-10 2008-04-10 Pompe à double aube à déplacement variable

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US92268307P 2007-04-10 2007-04-10
US60/922,683 2007-04-10

Publications (1)

Publication Number Publication Date
WO2008124174A1 true WO2008124174A1 (fr) 2008-10-16

Family

ID=39831294

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US2008/004616 WO2008124174A1 (fr) 2007-04-10 2008-04-10 Pompe à double aube à déplacement variable

Country Status (5)

Country Link
US (1) US20100119396A1 (fr)
EP (1) EP2150702A1 (fr)
JP (1) JP2010523896A (fr)
CN (1) CN101605995A (fr)
WO (1) WO2008124174A1 (fr)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102575674B (zh) * 2010-07-08 2015-09-02 松下电器产业株式会社 回转式压缩机及制冷循环装置
WO2012004992A1 (fr) 2010-07-08 2012-01-12 パナソニック株式会社 Compresseur rotatif et dispositif de cycle de refroidissement
CN102788013B (zh) * 2011-05-19 2015-07-08 北汽福田汽车股份有限公司 变量泵、发动机及汽车
JP5897943B2 (ja) * 2012-03-22 2016-04-06 日立オートモティブシステムズ株式会社 ベーンポンプ
JP5897945B2 (ja) * 2012-03-22 2016-04-06 日立オートモティブシステムズ株式会社 ベーンポンプ
ITTO20121149A1 (it) * 2012-12-27 2014-06-28 Vhit Spa Pompa a palette a cilindrata regolabile e metodo per la regolazione della cilindrata di tale pompa.
CN104295489B (zh) * 2013-07-15 2017-03-01 上海通用汽车有限公司 一种可变排量叶片泵
DE102015213099B3 (de) * 2015-07-13 2016-08-04 Joma-Polytec Gmbh Kunststoffrotor für Vakuumpumpe
CN108825494B (zh) * 2018-06-26 2019-12-06 海南葆润石油化工有限公司 一种石油化工用转子泵
CN108825491B (zh) * 2018-06-26 2019-12-06 苏州理合文科技有限公司 一种节约汽车燃油的方法
CN109441800B (zh) * 2018-09-28 2020-06-23 浙江大学 高压大流量变量叶片泵
CN109185125B (zh) * 2018-09-28 2020-02-07 浙江大学 高性能变量多叶片泵
CN109538466B (zh) * 2018-09-28 2020-04-10 浙江大学 高压多叶片泵
CN109185040B (zh) * 2018-09-28 2020-02-07 浙江大学 一种高性能多叶片液压马达
CN109441710B (zh) * 2018-09-28 2020-04-10 浙江大学 高性能多叶片马达
CN109185039B (zh) * 2018-09-28 2020-04-10 浙江大学 一种高性能多叶片马达
CN109538410B (zh) * 2018-09-28 2020-04-17 浙江大学 高速大扭矩多叶片马达
CN109469610B (zh) * 2018-09-28 2021-04-06 浙江大学 高性能多叶片泵
CN111980914B (zh) * 2020-08-05 2022-04-08 宁波圣龙汽车动力系统股份有限公司 一种变排量双作用叶片泵

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5287706A (en) * 1976-01-16 1977-07-22 Kitatomi Yuatsu Kougiyou Kk High pressure vane pumps
JPH0727059A (ja) * 1993-07-01 1995-01-27 Kazunori Satake ベーンポンプ
JPH11148476A (ja) * 1997-11-17 1999-06-02 Sato Takeshi 回転ピストン構造の容積形ピストン機構
JP2004522902A (ja) * 2001-04-05 2004-07-29 アーゴ−テック・コーポレーション 回転カムリングを有する可変容積形ポンプ
WO2006045190A1 (fr) * 2004-10-25 2006-05-04 Magna Powertrain Inc. Pompe a palettes a cylindree variable comprenant une chambre reductrice de force sur la bague de reglage de cylindree

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1594035A (en) * 1923-01-08 1926-07-27 Austin F Burdick Rotary motor
US1719134A (en) * 1926-08-19 1929-07-02 Rotary Machine & Engineering C Rotary pump
US2127968A (en) * 1935-09-03 1938-08-23 Robert L Bailey Rotary steam engine
US3000324A (en) * 1958-10-06 1961-09-19 Rosaen Filter Co Vane for rotary pumps
US3158103A (en) * 1959-02-09 1964-11-24 Eickmann Karl Vane assembly in rotary fluid machines
US3065760A (en) * 1960-02-12 1962-11-27 Dimitrios J Cailas Stabilizing attachment for tank washing machines
US4342545A (en) * 1978-07-24 1982-08-03 General Motors Corporation Variable displacement pump
GB2127489B (en) * 1982-09-28 1986-08-13 Plenty Ltd Rotary pump
DE3909831A1 (de) * 1989-03-25 1990-09-27 Becker Kg Gebr Trockenlaufende drehschiebervakuumpumpe sowie verfahren zu deren herstellung
US6022201A (en) * 1996-05-14 2000-02-08 Kasmer Hydristor Corporation Hydraulic vane pump with flexible band control
US6470992B2 (en) * 2001-04-03 2002-10-29 Visteon Global Technologies, Inc. Auxiliary solenoid controlled variable displacement power steering pump
DE10352267A1 (de) * 2003-11-08 2005-06-16 Beez, Günther, Dipl.-Ing. Pendelschiebermaschine
JP4834734B2 (ja) * 2005-10-06 2011-12-14 ヨーマ−ポリテック ゲーエムベーハー ベーンセルポンプ
DE502006008468D1 (de) * 2006-10-10 2011-01-20 Joma Polytec Gmbh Flügelzellenmaschine, insbesondere flügelzellenpumpe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5287706A (en) * 1976-01-16 1977-07-22 Kitatomi Yuatsu Kougiyou Kk High pressure vane pumps
JPH0727059A (ja) * 1993-07-01 1995-01-27 Kazunori Satake ベーンポンプ
JPH11148476A (ja) * 1997-11-17 1999-06-02 Sato Takeshi 回転ピストン構造の容積形ピストン機構
JP2004522902A (ja) * 2001-04-05 2004-07-29 アーゴ−テック・コーポレーション 回転カムリングを有する可変容積形ポンプ
WO2006045190A1 (fr) * 2004-10-25 2006-05-04 Magna Powertrain Inc. Pompe a palettes a cylindree variable comprenant une chambre reductrice de force sur la bague de reglage de cylindree

Also Published As

Publication number Publication date
CN101605995A (zh) 2009-12-16
EP2150702A1 (fr) 2010-02-10
JP2010523896A (ja) 2010-07-15
US20100119396A1 (en) 2010-05-13

Similar Documents

Publication Publication Date Title
US20100119396A1 (en) Variable displacement dual vane pump
US8535030B2 (en) Gerotor hydraulic pump with fluid actuated vanes
US7997882B2 (en) Reduced rotor assembly diameter vane pump
US20090238707A1 (en) Vane pump
US7247008B2 (en) Cam ring bearing for fuel delivery system
US8016577B2 (en) Vane pump with vane biasing means
US10018199B2 (en) Variable displacement pump
US7118361B2 (en) Rotary pistons
JP5133333B2 (ja) ベーンポンプ
US10288156B1 (en) Transmission assembly
JP4960815B2 (ja) 可変容量形ポンプ
JP4338162B2 (ja) ベーンポンプ
KR101351115B1 (ko) 동력 전달 장치용 토크 제한 윤활 펌프
JP2012021430A (ja) 可変容量形ベーンポンプ
US6835056B2 (en) Roller vane pump incorporating a bearing bush
KR101692773B1 (ko) 베인펌프
JP6031311B2 (ja) 可変容量型ベーンポンプ
US20050249617A1 (en) Fuel pump having single sided impeller
KR101136626B1 (ko) 오일펌프
KR101218457B1 (ko) 오일펌프
JPS62276286A (ja) 可変容量型ベ−ンポンプ
EP2434158B1 (fr) Arbre d'entrainement pour une pompe volumétrique
WO2020259869A1 (fr) Plaque de soupape pour pompe à fluide
JP2004028013A (ja) ベーンポンプ
KR20050096590A (ko) 자동변속기의 오일펌프

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 200880004687.9

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 08742711

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 2010503055

Country of ref document: JP

Kind code of ref document: A

WWE Wipo information: entry into national phase

Ref document number: 12594277

Country of ref document: US

NENP Non-entry into the national phase

Ref country code: DE

WWE Wipo information: entry into national phase

Ref document number: 2008742711

Country of ref document: EP