US20100322810A1 - Pump assembly for synchronous pressurization of two fluid circuits - Google Patents

Pump assembly for synchronous pressurization of two fluid circuits Download PDF

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Publication number
US20100322810A1
US20100322810A1 US12/743,291 US74329108A US2010322810A1 US 20100322810 A1 US20100322810 A1 US 20100322810A1 US 74329108 A US74329108 A US 74329108A US 2010322810 A1 US2010322810 A1 US 2010322810A1
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United States
Prior art keywords
partition
pump assembly
internal gear
pump
channel
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.)
Abandoned
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US12/743,291
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English (en)
Inventor
Rene Schepp
Norbert Alaze
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.)
Robert Bosch GmbH
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Individual
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Filing date
Publication date
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Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ALAZE, NORBERT, SCHEPP, RENE
Publication of US20100322810A1 publication Critical patent/US20100322810A1/en
Abandoned legal-status Critical Current

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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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/101—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T8/00—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force
    • B60T8/32—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration
    • B60T8/34—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition
    • B60T8/40—Arrangements for adjusting wheel-braking force to meet varying vehicular or ground-surface conditions, e.g. limiting or varying distribution of braking force responsive to a speed condition, e.g. acceleration or deceleration having a fluid pressure regulator responsive to a speed condition comprising an additional fluid circuit including fluid pressurising means for modifying the pressure of the braking fluid, e.g. including wheel driven pumps for detecting a speed condition, or pumps which are controlled by means independent of the braking system
    • B60T8/4031—Pump units characterised by their construction or mounting
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/082—Details specially related to intermeshing engagement type machines or pumps
    • F04C2/086—Carter

Definitions

  • the invention is based on a pump assembly for synchronous pressurization of two fluid circuits as generically defined by the preamble to independent claim 1 .
  • One such pump assembly is known for instance from German Patent Disclosure DE 10053991 A1 as a so-called pump insert for a hydraulic, wheel slip control vehicle brake system; different brake circuits of the brake system, with diagonal brake circuit distribution, are supplied by the two internal gear pumps of the pump insert.
  • the two internal gear pumps are partitioned off from one another by a separately embodied partition of the multi-piece housing and a common drive shaft passes transversely through them.
  • the pinions of the two gear pumps are slipped onto this drive shaft and joined to it in a manner fixed against relative rotation via a slaving connection.
  • two shaft sealing rings are inserted, spaced apart from one another, into adapted annular chambers of the partition bore.
  • each internal gear pump is also assigned one suction channel and one pressure channel, which viewed in the axial direction are located on opposite end regions of the pump assembly, extend essentially radially, and with angling of their end region open into the suction side and compression side, respectively, of the associated pump chamber.
  • the pairs of channels belonging to the internal gear pumps because of their lateral disposition next to the face ends of the pump assembly, have a considerable spacing from one another, which must also be taken into account in the engineering design and dimensioning of the pump housing.
  • the pump assembly of the invention having the characteristics of independent claim 1 has the advantage over the prior art that the axial spacing of the pairs each of a suction channel and a pressure channel of the internal gear pumps from one another can be reduced markedly.
  • a more-compact structure of the pump assembly can be attained and may be associated with a simplified embodiment of the line system for the two fluid circuits.
  • the suction channel and the pressure channel can furthermore be disposed in a technically simpler manner with accurate positioning in the partition, since the partition acts as an axial runup disk for the wheel sets of the pumps.
  • the partition before installation in the pump housing is accessible from all sides, which for instance makes metal-cutting machining for creating or machining the hollow channels markedly easier.
  • the surrounding housing parts furthermore no longer need to be joined at a distance of their face ends from one another on the circumference of the partition by means of rolled-in regions or the like; instead, the dividing plane can extend next to the partition, and the annular face ends of the housing parts to be joined together can be butt-joined.
  • the connection intensity of the hollow-cylindrical housing parts can be improved substantially, so that the pump assembly does not have to be slid into a pump housing that stabilizes it.
  • the suction channels and the pressure channels of both internal gear pumps are integrated with the partition.
  • the pressure channels and suction channels of both internal gear pumps are located quite close together, which makes a correspondingly compact structure of the pump assembly possible.
  • the leakage channel is integrated with the partition, then the leakage channel can be shortened considerably and requires no outlet opening of its own, if it discharges into an outflow bore of one or both suction channels of the partition.
  • the fluid channels of the pump assembly that are immediately adjacent to the pump chambers or fluidically communicate with them are located, inside the partition along with the leakage channel, then the fluid channels can be introduced with a precise fit into the “partition” workpiece with little production effort or expense and in the case of integrally cast fluid channels can be easily machined.
  • the partition can have a relatively slight thickness, if the four fluid channels are disposed essentially in the same cross-sectional region of the partition. So that this is possible, the fluid channels can each be offset from one another by 90° in the partition, as a result of the fact that the internal gear pumps of the pump assembly are rotated by 180° from one another. This has the positive side effect that compressive forces acting in opposite directions in the internal gear pumps largely cancel one another out.
  • valve assembly is provided in the line system of one of the fluid circuits to be supplied, then this valve assembly can be integrated directly with the associated fluid channel of the partition.
  • This valve assembly can include one valve or even two valves in one or both of the fluid circuits to be supplied. Equipping the fluid circuit or circuits with two valves each, which is technically especially appropriate, happens if a pressure reduction valve is disposed in the suction channel or channels of the partition and an overpressure valve is disposed in the pressure channel or channels of the partition.
  • space that is already present anyway inside the partition is thus utilized, so that an external disposition of the valves in the system of the associated fluid circuit can be dispensed with. This saves a corresponding amount of space outside the pump assembly and may simplify the line system connected to it.
  • the partition comprises a cylindrical disk with plane-parallel face ends that extend at a right angle to the center longitudinal axis of the disk and parallel to one another, and it is pressed into a cylindrical hollow cross section of the associated housing part.
  • the plane face ends are polished which because of the disk shape can be done inexpensively with high surface quality, then they can serve directly as runup faces for the gear wheel sets.
  • the pressed-in partition can advantageously be braced axially between opposed annular face ends of two housing parts, and the outside diameter of one of the housing parts is largely equivalent to the outside diameter of the partition.
  • the tubular end region adapted in diameter to the partition can then, similarly to the partition, be pressed or thrust into the larger tubular end region of the other housing part, after which the tube ends overlap longitudinally in telescoping fashion. Given adequate axial securing, a very stable combination is obtained by putting together the hollow housing parts and the partition.
  • one thrust pad of a plastic material that is usual for thrust pads, can be disposed on each of the ends of the pump assembly; it is axially braced on the face ends of the associated wheel set on the one hand and on the opposed bore wall of the pump chamber on the other.
  • each of the thrust pads is structurally united with an associated bearing sleeve for the drive shaft, which leads to a desirable reduction in the number of parts in the pump assembly.
  • the bearing sleeve itself may be embodied in one piece with the thrust pad and can itself form a slide bearing. However, the bearing sleeve may alternatively receive or surround either a roller bearing or bearing shells of a slide bearing.
  • FIG. 1 shows a schematic center longitudinal section through a pump assembly of the invention.
  • FIG. 2 shows a pump chamber of the pump assembly of FIG. 1 in a side view.
  • FIG. 3 shows a vertical section through a partition of the pump assembly, taken along the section line in FIG. 1 .
  • a pump assembly 10 includes two internal gear pumps 11 and 11 ′, which are located laterally directly beside one another and are disposed in a common pump housing 12 .
  • the pump assembly 10 is component of a pressure control unit, not shown, for a vehicle brake system that has diagonally distributed brake circuits, and the internal gear pumps 11 and 11 ′ are each responsible for supplying pressure to one of the brake circuits in the course of brake interventions, known per se, for ABS or ESP applications.
  • the common pump housing 12 is composed on the outside of two cuplike hollow housing parts 13 and 14 , which each define one pump chamber of the internal gear pump 11 and 11 ′, respectively, on three sides and are joined together with their end regions overlapping longitudinally.
  • a partition 15 is fitted in as an internal housing part, which defines the pump chambers of the two internal gear pumps 11 and 11 ′ on the fourth side with its face ends.
  • the partition 15 comprises a cylindrical disk with plane-parallel face ends, which is pressed into a cylindrical hollow cross section of the associated housing part 13 .
  • the drive of the two internal gear pumps 11 and 11 ′ is effected via a common drive shaft 16 , which is driven to rotate by a direct current motor flanged to the outside; via a sealed-off shaft passage, the drive shaft 16 is introduced into the housing 12 and passes through coaxial bearing bores, which are recessed out of the face ends of the housing parts 13 and 14 as well as out of the partition 15 .
  • the drive shaft 16 is slidingly supported rotatably directly in the bore of the partition 15 , while at the lateral bearing points the drive shaft 16 is slidingly rotationally supported via a bearing sleeve 17 and a bearing sleeve 17 ′ of plastic.
  • the bearing sleeves 17 and 17 ′ are each embodied hollow-cylindrically and rest by positive engagement between the circumference of the drive shaft 16 and the associated bore wall of the respective housing part 13 and 14 .
  • the drive shaft 16 adjacent to the bearing sleeve 17 and 17 ′, respectively, passes through a respective thrust pad 18 and 18 ′, which is embodied in one piece with the associated bearing sleeve 17 and 17 ′, and after that passes through a central insertion opening in the associated pinion 19 and 19 ′ of the internal gear pumps 11 and 11 ′, and finally passes through an associated shaft seal ring 20 and 20 ′, which is pressed into an associated, stepped widened portion of the bearing bore for the drive shaft 16 in the partition 15 .
  • the drive shaft 16 passes through a hollow cross section, fitting it, of the pinion 19 , thus providing a slaved connection secure against relative rotation between the pinion 19 and the drive shaft 16 .
  • the outer toothing of the pinion 19 meshes with the inner toothing of an internal gear 21 , which in turn is supported by its round outer circumference rotatably in a bore portion of the associated housing part 13 .
  • the valve assembly is located exactly in the center in the upper region of the inner toothing internal gear 21 , as a result of which the tip circles of the pinion 19 and internal gear 21 define an overall crescent-shaped annular chamber.
  • This annular chamber is designed mirror-symmetrically with respect to the vertical center plane of the wheel set in which plane the axes of rotation of the pinion 19 and internal gear 21 extend.
  • a filler piece 22 is supported pivotably in the center by means of a centrally disposed axle bolt 23 .
  • the pivotability is limited to a minimum, since the outer circumferential side of the filler piece 22 is in contact with little play with the covered tooth tips of the inner toothing of the internal gear 21 , and the inner circumferential side of the filler piece 22 rests with little play on the covered tooth tips of the pinion 19 .
  • a suction channel 24 can also be seen on the right-hand suction side of the internal gear pump 11 , and an associated pressure channel 25 for the brake fluid can be seen on the left-hand compression side.
  • the drive shaft 16 rotates clockwise, for instance by means of an electric geared motor, then the pinion 19 rotates synchronously with it, as does the internal gear 21 in the same direction because of the valve assembly with the pinion 19 .
  • the tooth gaps covered by the filler piece 22 are sealed off on one face end by the thrust pad 18 subjected to corresponding axial force and on the opposite face end by running up against the partition 15 , the hollow volumes of brake fluid received by the tooth gaps can be transported, given adequate sealing of the tooth tips from the filler piece 22 , can be transported, with a corresponding pressure increase, from the suction channel 24 to the pressure channel 25 of the internal gear pump 11 .
  • the sealing required for this between the tooth tips and the filler piece 22 comes about solely because of a defined circumferential play of the filler piece 22 , by which play, in operation, a pressure distribution over the circumferential length of the filler piece 22 is brought about, which leads to an adequate rotational force of the filler piece 22 about the center longitudinal axis of the axle bolt 23 .
  • the internal gear pump 11 ′ is jointly driven by the drive shaft 16 , since the pinion 19 ′ is also penetrated by the drive shaft 16 and is connected to it in a manner fixed against relative rotation via a slaved connection corresponding to the pinion 19 .
  • the geometry of the internal gear pump 11 ′ per se is also largely the same as that of the internal gear pump 11 , and the wheel set comprising the pinion 19 ′ and the internal gear 21 ′ is disposed in a manner rotated by 180° relative to the wheel set comprising the pinion 19 and the internal gear 21 .
  • the suction channel 24 discharging into the pump chamber of the internal gear pump 11 and the associated pressure channel 25 are located essentially in the same cross-sectional plane as the suction channel 24 ′, discharging into the pump chamber of the internal gear pump 11 ′, and the associated pressure channel 25 ′. Moreover, they are disposed radially so far in the direction of the outer circumference that they can be in axial overlap with the pressed-in shaft seal rings 20 and 20 ′ without impairing the function. As a result, the partition 15 overall needs only a slightly greater thickness than is necessary anyway for the integration of the axial and radial channel portion of the respective suction channel 24 and 24 ′.
  • a leakage channel 26 for carrying away brake fluid that has forced its way into the bearing bore of the partition 15 ;
  • the leakage channel begins at the bearing bore of the partition 15 between the shaft seal rings 20 and 20 ′, extends diagonally through the partition 15 , and discharges into the two suction channels 24 and 24 ′.
  • a respective pressure reduction valve 27 and 27 ′ is disposed in the suction channels 24 and 24 ′, and a respective overpressure valve 28 and 28 ′ is disposed in the pressure channels 25 and 25 ′, and the arrangement is made such that all the valves 27 , 27 ′, 28 and 28 ′ received by the partition 15 are located inside voids in the partition in every switching state.
  • the overpressure valves 28 and 28 ′ are structurally identical, oppositely disposed overpressure valves of conventional construction, in which a ball is located in the flow path of the pressure channel and is pressed against its sealing seat by the force of a restoring spring. As soon as the fluid pressure at the sealing seat is greater than the spring force, the ball is positively displaced, and the flow path of the pressure channel is thus opened up.
  • the pressure channels 25 and 25 ′ which with their radial longitudinal portion are integrated with the partition 15 diametrically to one another and near the circumference, are thus, given corresponding pressure, moved radially outward counter to the spring loading and as a result communicate fluidically with the associated brake circuit, or given a corresponding change in pressure conditions are closed again by spring force and as a result fluidically disconnected from the brake system.
  • the pressure reduction valves 27 and 27 ′ are embodied as linear slide valves, which pass transversely through the radial flow path of the suction channel 24 and 24 ′, respectively, with a tapered control portion and are likewise inserted in the opposite direction.
  • the slide directions of the pressure reduction valves 27 and 27 ′ are parallel to one another and to the radial longitudinal portions of the pressure channels 25 and 25 ′.
  • the slides of the pressure reduction valves 27 and 27 ′ are also each kept in an axial outset position by the spring force of an associated helical compression spring, but this outset position corresponds to the open position of the pressure reduction valve 27 and 27 ′.
  • the helical compression spring is braced here on the respective annular end face of a piston portion adjoining the control portion, which piston portion is guided in sliding fashion, with sealing occurring, in its bore of the partition 15 , and the control portion, with an end region that has a middle bore, engages an associated blind bore in the partition 15 .
  • the components of the pressure reduction valves 27 and 27 ′ are adapted to one another in such a way that a pressure limit value of approximately 10 bar on the suction side of the internal gear pumps 11 and 11 ′ cannot be exceeded.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Transportation (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
US12/743,291 2007-11-16 2008-09-26 Pump assembly for synchronous pressurization of two fluid circuits Abandoned US20100322810A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007054808.9 2007-11-16
DE102007054808A DE102007054808A1 (de) 2007-11-16 2007-11-16 Pumpenbaugruppe zur synchronen Druckbeaufschlagung von zwei Fluidkreisen
PCT/EP2008/062919 WO2009062783A1 (de) 2007-11-16 2008-09-26 Pumpenbaugruppe zur synchronen druckbeaufschlagung von zwei fluidkreisen

Publications (1)

Publication Number Publication Date
US20100322810A1 true US20100322810A1 (en) 2010-12-23

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US12/743,291 Abandoned US20100322810A1 (en) 2007-11-16 2008-09-26 Pump assembly for synchronous pressurization of two fluid circuits

Country Status (6)

Country Link
US (1) US20100322810A1 (ja)
EP (1) EP2220373A1 (ja)
JP (1) JP5323080B2 (ja)
CN (1) CN101855452B (ja)
DE (1) DE102007054808A1 (ja)
WO (1) WO2009062783A1 (ja)

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US20120315175A1 (en) * 2009-10-12 2012-12-13 Dirk Foerch Double Internal Gear Pump
US20130071280A1 (en) * 2011-06-27 2013-03-21 James Brent Klassen Slurry Pump
US20130309120A1 (en) * 2011-01-31 2013-11-21 Robert Bosch Gmbh Double internal gear wheel pump
US20140090462A1 (en) * 2011-01-31 2014-04-03 Georg Blosch Method for circuit separation testing in a double gearwheel pump
US20140178219A1 (en) * 2012-12-21 2014-06-26 Chanseok Kim Electric pump
US10072656B2 (en) 2013-03-21 2018-09-11 Genesis Advanced Technology Inc. Fluid transfer device
EP3835585A1 (en) * 2019-12-02 2021-06-16 FTE automotive GmbH Liquid pump, in particular for providing a supply to a transmission or to a clutch in the drive train of a motor vehicle
US11067076B2 (en) 2015-09-21 2021-07-20 Genesis Advanced Technology Inc. Fluid transfer device
WO2021209222A1 (de) * 2020-04-14 2021-10-21 Hydraulik Nord Technologies GmbH Innenzahnradmaschine

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DE102009045227A1 (de) * 2009-10-01 2011-04-21 Robert Bosch Gmbh Innenzahnradpumpe für eine hydraulische Fahrzeugbremsanlage
DE102009047213B4 (de) 2009-11-27 2022-06-09 Robert Bosch Gmbh Verfahren zur Kreistrennungsprüfung einer Doppelzahnradpumpe
DE102009047636A1 (de) 2009-12-08 2011-06-09 Robert Bosch Gmbh Doppel-Innenzahnradpumpe
DE102011079860A1 (de) * 2011-07-26 2013-01-31 Robert Bosch Gmbh Bremssystem für ein Fahrzeug und Verfahren zum Betreiben eines Bremssystems eines Fahrzeugs
DE102013204616B4 (de) 2013-03-15 2021-12-09 Robert Bosch Gmbh 2Innenzahnradpumpe
WO2014147588A1 (en) * 2013-03-20 2014-09-25 Magna International Inc. Tandem electric pump
JP2016205290A (ja) * 2015-04-24 2016-12-08 株式会社ニッキ 内接歯車ポンプ
EP3724484A1 (en) * 2017-12-13 2020-10-21 Robert Bosch GmbH Pumping unit for feeding fuel, preferably diesel fuel, to an internal combustion engine
CN108644109A (zh) * 2018-03-20 2018-10-12 中国石油天然气股份有限公司 油气井用轴流式齿轮泵
DE102018212497A1 (de) 2018-07-26 2020-01-30 Eckerle Technologies GmbH Fluidfördereinrichtung
DE102022206319A1 (de) 2022-06-23 2023-12-28 Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg Elektrische Zahnradpumpe für ein Kraftfahrzeug, insbesondere Gerotor-Pumpe sowie Set aus mehreren Zahnradpumpen

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CN101855452B (zh) 2013-09-18
WO2009062783A1 (de) 2009-05-22
JP5323080B2 (ja) 2013-10-23
DE102007054808A1 (de) 2009-05-20
EP2220373A1 (de) 2010-08-25
JP2011503428A (ja) 2011-01-27

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