EP2404062A1 - Pompe à ailettes à déplacement variable linéaire et à commande directe - Google Patents

Pompe à ailettes à déplacement variable linéaire et à commande directe

Info

Publication number
EP2404062A1
EP2404062A1 EP10748251A EP10748251A EP2404062A1 EP 2404062 A1 EP2404062 A1 EP 2404062A1 EP 10748251 A EP10748251 A EP 10748251A EP 10748251 A EP10748251 A EP 10748251A EP 2404062 A1 EP2404062 A1 EP 2404062A1
Authority
EP
European Patent Office
Prior art keywords
slide
pump
pumping system
fluid pumping
actuator shaft
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.)
Withdrawn
Application number
EP10748251A
Other languages
German (de)
English (en)
Other versions
EP2404062A4 (fr
Inventor
Florin Stratulat
Peter Lit Ming Chang
Gil Hadar
Peter Krug
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
STT Technologies Inc
Original Assignee
STT Technologies 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 STT Technologies Inc filed Critical STT Technologies Inc
Publication of EP2404062A1 publication Critical patent/EP2404062A1/fr
Publication of EP2404062A4 publication Critical patent/EP2404062A4/fr
Withdrawn legal-status Critical Current

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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M1/00—Pressure lubrication
    • F01M1/16—Controlling lubricant pressure or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16N—LUBRICATING
    • F16N13/00—Lubricating-pumps
    • F16N13/20—Rotary pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/0434—Features relating to lubrication or cooling or heating relating to lubrication supply, e.g. pumps ; Pressure control
    • F16H57/0436—Pumps

Definitions

  • the present disclosure relates to a fluid pumping system for an automobile. More specifically, the present disclosure relates to a variable displacement vane pump and control system for providing a continuously variable output flow independent of the operating speed of the pump.
  • Mechanical systems such as internal combustion engines and automatic transmissions, typically include a lubrication pump to provide lubricating oil, under pressure, to many of the moving components and/or subsystems of the mechanical systems.
  • the lubrication pump is driven by a rotating component of the mechanical system.
  • the operating speed and output of the pump varies with the operating speed of the mechanical system.
  • the lubrication requirements of the mechanical system typically do not directly correspond to the operating speed of the mechanical system.
  • Previously known fixed displacement lubricating pumps were generally designed to provide sufficient flow at a relatively low speed corresponding to an engine idle speed and a maximum operating lubricant temperature. This design philosophy resulted in an oversupply of lubricating oil during a large portion of vehicle operation.
  • a pressure relief valve was provided to return the surplus lubricating oil back into the pump inlet or oil sump to avoid over pressure conditions in the mechanical system.
  • the overproduction of pressurized lubricating oil may be 500% of the mechanical system's needs. The result is a significant amount of energy being used to pressurize the lubricating oil which is subsequently exhausted through the relief valve.
  • variable displacement vane pumps have been employed as lubrication oil pumps.
  • Such pumps generally include a control ring, or other mechanism, which can be operated to alter the volumetric displacement of the pump and thus its output at an operating speed.
  • a feedback mechanism is supplied with pressurized lubricating oil from the output of the pump to alter the displacement of the pump to avoid over pressure situations in the engine throughout the expected range of operating conditions of the mechanical system.
  • variable displacement pumps provide some improvements in energy efficiency over fixed displacement pumps, a significant energy loss may result due to pump displacement being controlled, directly or indirectly, by the output pressure of the pump which changes with the operating speed of the mechanical system, rather than with the changing requirements of the mechanical system.
  • Another variable displacement pump control system is described within U.S. Patent No. 7,018,178.
  • the control system includes an electric solenoid coupled to a variable displacement pump for varying the displacement of the pump during engine operation. While an electric solenoid may provide an additional degree of pump control, several disadvantages from its use exist. In particular, a solenoid typically requires a continuous supply of current to keep it active through operation of the pump.
  • the electrical power consumption may offset the benefit of controlling the pump to minimize the amount of time that the pump provides excess lubricant flow.
  • the maximum force capability of the solenoid is limited by the size of the electromagnet and the current applied thereto.
  • the size of the electromagnet required to provide the desired force may be prohibitive for packaging the solenoid within an automotive environment. Accordingly, a need exists for an improved lubrication system for producing a desired lubricant flow while minimizing the energy required to do so.
  • a fluid pumping system for a power transmission device includes a variable displacement vane pump having a housing containing a rotor, a plurality of vanes coupled to the rotor and a linearly translatable slide for varying the displacement of the pump by changing its eccentricity.
  • a control system varies the displacement of the pump and provides a fluid output pressure selected from a continuously variable range of output pressures that are independent from the operating speed of the pump.
  • the control system includes a linear actuator for moving the slide between minimum and maximum pump displacement positions.
  • the linear actuator includes an electric stepper motor for bi-directionally translating an actuator shaft acting on the slide.
  • the present disclosure describes a fluid pumping system for a power transmission device including a variable displacement vane pump having a linearly moveable slide for varying the displacement of the pump.
  • a linear actuator moves the slide between maximum and minimum pump displacement positions.
  • the linear actuator includes an electric motor for rotating a drive member.
  • the drive member engages a driven actuator shaft to cause linear translation of the actuator shaft in response to rotation of the drive member.
  • a control system includes a controller for signaling the actuator to extend or retract the actuator shaft to vary the pump displacement.
  • Figure 1 is a cross-sectional view of an exemplary directly controlled variable displacement vane pump
  • Figure 2 is an enlarged fragmentary perspective view of the pumping system depicted in Figure 1
  • Figure 3 is a fragmentary perspective view of a connector coupling the actuator shaft and the slide;
  • Figure 4 is a schematic of an open loop control system for controlling the variable displacement vane pump
  • Figure 5 is a schematic depicting a closed loop control system cooperating with the variable displacement vane pump
  • Figure 6 is a fragmentary perspective view of another variable displacement vane pump
  • Figure 7 is a plan view of a slide and actuator arrangement of the pump depicted in Figure 6;
  • Figure 8 is a plan view of the housing for the pump shown in Figure 6.
  • a pumping system 10 is shown plumbed in communication with an exemplary power transmission device 12.
  • Power transmission device 12 is shown schematically and may include any number of devices including an internal combustion engine, a transmission, a transfer case, an axle assembly or the like.
  • Pumping system 10 includes a variable displacement pump 14 including a housing 16 with a flange 17 for mounting pump 14 to power transmission device 12. Alternatively, housing 16 may be integrally formed with the power transmission device.
  • An inlet 18 extends through housing 16 interconnecting a low pressure gallery 20 with a sump 22 storing the fluid to be pumped.
  • An outlet 24 of housing 16 interconnects a high pressure chamber 26 with power transmission device 12.
  • Pump 14 includes a pump rotor 28 rotatably mounted within a rotor chamber 32.
  • a drive shaft 34 is part of power transmission device 12 and is fixed for rotation with pump rotor 28 to provide energy for pumping the lubricant.
  • a plurality of pump vanes 36 are coupled to rotor 28 and radially slidable relative thereto. The radial outer end of each vane 36 engages an inner surface 38 of a slide 40.
  • a plurality of pumping chambers 44 are defined by inner surface 38, pump rotor 28 and vanes 36.
  • Slide 40 includes a first arm 46 slidably positioned within a first recess 48 formed in housing 16. Slide 40 also includes a second arm 50 slidably positioned within a second housing recess 52. Slide 40 also includes substantially parallel opposite walls 54, 56 positioned in close proximity to walls 58, 60 of housing 16, respectively. Based on the geometric features previously described, slide 40 may linearly translate between first and second positions but is restricted from rotation relative to housing 16.
  • Inner surface 38 of slide 40 has a circular cross-sectional shape.
  • An outer surface 61 of rotor 28 also has a circular cross-sectional shape.
  • a centerline of cylindrical surface 38 is eccentrically located with respect to the center of outer surface 61. Accordingly, the volume of each pumping chamber 44 changes as rotor 28 rotates.
  • the volume of chambers 44 increases at the low pressure side of the pump in communication with inlet 18.
  • Pumping chambers 44 decrease in size at the high pressure side in communication with outlet 24 of pump 14.
  • the change in volume of pumping chambers 44 generates the pumping action by drawing working fluid from sump 22 and delivering pressurized fluid from outlet port 24.
  • the output of pump 14 may be varied by translating slide 40.
  • the amount of eccentricity between inner surface 38 of slide 40 and the outer surface 61 of rotor 28 is a maximum when slide 40 is at the first position shown in Figure 1. Pump output flow is greatest at this position.
  • eccentricity and the output of pump 14 are minimized and may be zero.
  • a linear actuator assembly 62 is coupled to second arm 50 and is operable to move slide 40 along an axis 63 to the first position, the second position and any point therebetween. Accordingly, pump 14 may be controlled to output a fluid pressure selected from a continuously variable range of output pressures that are independent from the operating speed of the pump.
  • a pressure balance chamber 64 surrounds a portion of slide 40. Pressure balance chamber 64 is in fluid communication with pressurized fluid provided from outlet 24. The shape and position of pressure balance chamber 64 effectively balances the forces acting on slide 40 thereby minimizing the force required to move slide 40 and vary the pump output.
  • Pressure balance chamber 64 extends along one side of slide 40 on opposite sides of a line perpendicularly intersecting axis 63 and extending through the centerline of surface 38. It should be appreciated that the pressure balanced arrangement may be desirable but is not a requisite portion of pumping system 10. Without the pressure balancing chamber, actuator 62 may function but may be tasked to provide a greater input force to move slide 40.
  • actuator assembly 62 includes an electric stepper motor 70 including a stator 72 and a rotor 74 supported in a housing 75.
  • Rotor 74 is coupled to a nut 76 that is threadingly engaged with an externally threaded actuator shaft 78.
  • Housing 75 includes a flange 79 coupled to pump housing 16. Flange 79 may alternatively be fixed to power transmission device 12.
  • Figure 3 depicts actuator shaft 78 including a distal end 80 coupled to second arm 50 by a clip 82.
  • Actuator shaft 78 includes a groove 84 in receipt of a semi-circular portion 86 of clip 82.
  • Clip 82 also includes an elongated upper portion 88 that may be translated into a slot 90 formed within second arm 50 to couple actuator shaft 78 to slide 40.
  • actuator assembly 62 is in communication with a controller 100, a power supply 102 and a drive 104.
  • Controller 100 may be programmed with an algorithm or algorithms referencing speed, pressure, flow or temperature maps to enable the controller to control the flow of the pump using an open loop control system as depicted in Figure 4.
  • Figure 5 depicts a closed loop control system including a pressure sensor 106 in communication with controller 100.
  • drive shaft 34 begins to rotate and drive rotor 28.
  • Lubricant pressure and flow begin to increase at outlet 24.
  • controller 100 locates slide 40 in the first position to provide maximum flow. As such, flow increases linearly with the speed of drive shaft 34. At a particular speed, the flow produced by pump 14 will exceed the lubrication requirements of power transmission device 12.
  • controller 100 provides a signal to drive 104.
  • Drive 104 is in receipt of electrical power from power supply 102.
  • Drive 104 generates electrical pulses and supplies pulses to electric stepper motor 70 causing nut 76 to rotate in one of two directions to extend or retract actuator shaft 78 as signaled by controller 100. Because actuator shaft 78 is directly coupled to slide 40, the linear motion of actuator shaft 78 and slide 40 changes the eccentricity of the pump and thus the pump output flow.
  • controller 100 continues to signal drive 104 to position slide 40 based on any one or more of speed, pressure, flow or temperature mappings of the control algorithm.
  • a dedicated pressure sensor associated with pump 14 is not required.
  • the closed loop feedback system depicted in Figure 5 includes pressure sensor 106 providing a signal indicative of the pressure output by pump 14 to controller 100. Controller 100 outputs a signal to drive 104 to position slide 40 and cause pump 14 to output a desired lubricant pressure.
  • a coupling technique has been described to facilitate a ridged mounting of actuator housing 75 to pump housing 16 or another portion of power transmission device 12.
  • the connection allows actuator shaft 78 to linearly translate and transfer a force to linearly moveable slide 40.
  • any number of methods for fixing actuator shaft 78 to slide 40 such as pinning, riveting, welding, press-fitting, adhesive bonding or the like, are contemplated as being within the scope of the present disclosure.
  • the closed loop control system was previously described as being in communication with a pressure sensor, it should be appreciated that any number of other sensors may be implemented to provide controller 100 with data for decision making relating to the control of actuator 62 and pumping system 10.
  • FIGS. 6 and 7 depict an alternate variable displacement pump identified at reference numeral 150.
  • Pump 150 is substantially similar to pump 14. Accordingly, like elements will retain their previously introduced reference numerals including a prime suffix. Pump 150 differs from pump 14 in the manner in which slide 40' is urged toward the first or maximum eccentricity position.
  • One end of a compression spring 152 is positioned within a pocket 154 formed within slide 40'.
  • An opposite end of spring 152 is positioned within a recess 156 formed in housing 16".
  • Spring 152 is continuously under compression to urge slide 40' toward the first position.
  • actuator 62' is no longer required to move slide 40" toward the first position.
  • Actuator 62" applies a force to move slide 40' toward the second position.
  • an adapter 158 may be fixed to actuator shaft 78'.
  • Adapter 158 includes an end face 160 in contact with a land 162 formed on slide 40'. End face 160 and land 162 remain in contact with one another due to the force provided by compression spring 152. At the first or most eccentric position, land 162 is forced into contact with a seat 164 formed on housing 16'.
  • actuator 62' may be selectively energized to extend actuator shaft 78' and move slide 40' from the first position toward the second position.
  • actuator 62' Once electrical energy is no longer supplied to actuator 62', the position of slide 40' will be maintained due to the internal configuration of stepper motor 70'. To move slide 40' toward the first position, actuator 62' is energized once again to allow slide 40' to translate under the force provided by spring 152. An infinite number of positions between the first position providing maximum flow and the second position providing minimum flow may be obtained through control of actuator 62' as previously discussed.

Landscapes

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

Abstract

L'invention concerne un système de pompage de fluide pour un dispositif de transmission d'énergie, comprenant une pompe à ailettes à déplacement variable possédant un logement qui contient un rotor, une pluralité d'ailettes accouplées à ce rotor et une glissière à déplacement linéaire destinée à modifier le déplacement de la pompe. Un système de commande modifie le déplacement de la pompe et délivre une pression de sortie de fluide sélectionnée dans une plage continûment variable de pressions de sortie qui sont indépendantes de la vitesse de fonctionnement de la pompe. Le système de commande comprend un actionneur linéaire destiné à déplacer la glissière entre des positions de déplacement minimale et maximale de la pompe. Cet actionneur linéaire intègre un moteur pas à pas électrique destiné à effectuer le déplacement bidirectionnel d'un arbre d'actionneur agissant sur la glissière.
EP10748251.5A 2009-03-05 2010-02-23 Pompe à ailettes à déplacement variable linéaire et à commande directe Withdrawn EP2404062A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US15760109P 2009-03-05 2009-03-05
PCT/CA2010/000269 WO2010099599A1 (fr) 2009-03-05 2010-02-23 Pompe à ailettes à déplacement variable linéaire et à commande directe

Publications (2)

Publication Number Publication Date
EP2404062A1 true EP2404062A1 (fr) 2012-01-11
EP2404062A4 EP2404062A4 (fr) 2014-01-15

Family

ID=42709165

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10748251.5A Withdrawn EP2404062A4 (fr) 2009-03-05 2010-02-23 Pompe à ailettes à déplacement variable linéaire et à commande directe

Country Status (8)

Country Link
US (1) US20120093672A1 (fr)
EP (1) EP2404062A4 (fr)
JP (1) JP2012519253A (fr)
KR (1) KR20120006977A (fr)
CN (1) CN102333956A (fr)
BR (1) BRPI1010521A2 (fr)
CA (1) CA2753511A1 (fr)
WO (1) WO2010099599A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103363279B (zh) * 2012-04-05 2016-09-07 同济大学 一种步进电机控制的叶片式无级变量机油泵
KR101333959B1 (ko) * 2012-05-31 2013-11-27 울산대학교 산학협력단 액추에이터 내장형 가변 오일펌프
ITTO20130735A1 (it) * 2013-09-11 2015-03-12 Vhit Spa Pompa a cilindrata variabile con comando elettrico della regolazione e metodo di regolazione della sua cilindrata
CN103742775A (zh) * 2013-12-30 2014-04-23 东风汽车公司 叶片式可变排量机油泵
CN104314637B (zh) * 2014-08-19 2018-03-02 湖南机油泵股份有限公司 内燃机的机油泵
US10253772B2 (en) 2016-05-12 2019-04-09 Stackpole International Engineered Products, Ltd. Pump with control system including a control system for directing delivery of pressurized lubricant
DE102016209171A1 (de) * 2016-05-25 2017-11-30 Mahle International Gmbh Pendelschiebermaschine, insbesondere Ölpumpe, für eine Brennkraftmaschine eines Kraftfahrzeugs
DE102017106546A1 (de) * 2017-03-27 2018-09-27 Robert Bosch Gmbh Ölpumpe mit elektrisch verstellbarer Verdrängung
CN110714917B (zh) * 2019-10-09 2021-05-28 太原理工大学 一种连续比例调节流量的单作用叶片泵的变量机构

Citations (3)

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Publication number Priority date Publication date Assignee Title
WO1993012424A1 (fr) * 1991-12-13 1993-06-24 Abbott Laboratories Detection de medicaments antidepresseurs tricycliques en presence de substances d'interference
WO2006032132A1 (fr) * 2004-09-20 2006-03-30 Magna Powertrain Inc. Pompe a pression de sortie selectionnable
US20080010984A1 (en) * 2005-07-22 2008-01-17 Ashradan Holdings Ltd. Self-Contained Hydraulic Actuator System

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US3650642A (en) * 1970-04-14 1972-03-21 Chandler Evans Inc Pumping system including variable displacement vane pump
US4439117A (en) * 1982-08-17 1984-03-27 The Bendix Corporation Variable displacement vane pump
JPS6131675A (ja) * 1984-07-24 1986-02-14 Nippon Denso Co Ltd 可変容量ポンプ
GB9012848D0 (en) * 1990-06-08 1990-08-01 Lucas Ind Plc Fuel pump
DE4302610C2 (de) * 1993-01-30 1996-08-08 Daimler Benz Ag Verfahren zum Regeln der Pumpleistung von Schmiermittelpumpen und Schmiermittelpumpe hierfür
DE4319200C1 (de) * 1993-06-09 1994-07-21 Glyco Metall Werke Mehrstufenregler für Schmiermittelpumpen mit kontinuierlich veränderbarem Fördervolumen
DE10103386A1 (de) * 2001-01-26 2002-10-10 Audi Ag Volumenstromgeregelte Schmiermittelpumpe
FR2829535B1 (fr) * 2001-09-12 2005-08-12 Pierburg Pompe a palettes a cylindree variable
US6763797B1 (en) * 2003-01-24 2004-07-20 General Motors Corporation Engine oil system with variable displacement pump
ITBO20040008A1 (it) * 2004-01-09 2004-04-09 Pierburg Spa Impianto di pompaggio
US7614858B2 (en) * 2004-10-25 2009-11-10 Magna Powertrain Inc. Variable capacity vane pump with force reducing chamber on displacement ring
US8011909B2 (en) * 2007-03-28 2011-09-06 Goodrich Pump & Engine Control Systems, Inc. Balanced variable displacement vane pump with floating face seals and biased vane seals
US8128386B2 (en) * 2008-06-26 2012-03-06 Hamilton Sundstrand Corporation Variable flow pumping system

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993012424A1 (fr) * 1991-12-13 1993-06-24 Abbott Laboratories Detection de medicaments antidepresseurs tricycliques en presence de substances d'interference
WO2006032132A1 (fr) * 2004-09-20 2006-03-30 Magna Powertrain Inc. Pompe a pression de sortie selectionnable
US20080010984A1 (en) * 2005-07-22 2008-01-17 Ashradan Holdings Ltd. Self-Contained Hydraulic Actuator System

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2010099599A1 *

Also Published As

Publication number Publication date
BRPI1010521A2 (pt) 2016-03-15
WO2010099599A1 (fr) 2010-09-10
KR20120006977A (ko) 2012-01-19
JP2012519253A (ja) 2012-08-23
EP2404062A4 (fr) 2014-01-15
US20120093672A1 (en) 2012-04-19
CN102333956A (zh) 2012-01-25
CA2753511A1 (fr) 2010-09-10

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