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EP1292773A1 - Pompe - Google Patents

Pompe

Info

Publication number
EP1292773A1
EP1292773A1 EP01945237A EP01945237A EP1292773A1 EP 1292773 A1 EP1292773 A1 EP 1292773A1 EP 01945237 A EP01945237 A EP 01945237A EP 01945237 A EP01945237 A EP 01945237A EP 1292773 A1 EP1292773 A1 EP 1292773A1
Authority
EP
European Patent Office
Prior art keywords
pump
connection
pressure
particular according
intermediate capacity
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.)
Granted
Application number
EP01945237A
Other languages
German (de)
English (en)
Other versions
EP1292773B1 (fr
Inventor
Ivo Agner
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.)
ixetic Bad Homburg GmbH
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co KG
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 LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP1292773A1 publication Critical patent/EP1292773A1/fr
Application granted granted Critical
Publication of EP1292773B1 publication Critical patent/EP1292773B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface

Definitions

  • the invention relates to a pump with a pump chamber, in which a pump element which can be driven in rotation is arranged, at least one suction and at least one pressure connection opening into the pump chamber and with revolving, volume-variable delivery cells which, depending on the rotational position of the pump element, have the suction or pressure connection are connected.
  • Pumps of the type mentioned here are known, for example, as vane and roller cell pumps, in which the delivery cells are delimited by the pump chamber wall and the delivery elements, the delivery elements being designed either as vanes or rollers which are received by the rotatably driven pump element. which thus forms the rotor of the pump.
  • pressure pulsations occur during operation, which arise on the one hand from the funding law and, on the other hand, from pressure equalization processes during the transition of the delivery cells from the suction connection to the pressure connection or from the pressure connection to the suction connection.
  • attempts have been made to control the pressure equalization processes by means of small notches which are formed in the pump chamber wall and are connected to the suction or pressure connection.
  • a pump which has a pump chamber in which a pump element which can be driven in rotation is arranged.
  • the pump also has at least one suction and at least one pressure connection opening into the pump chamber.
  • the pump has revolving, volume-variable delivery cells that are connected to the suction or pressure connection depending on the rotational position of the pump element.
  • the pump according to the invention is characterized in particular by a hydraulic intermediate capacity, which can be acted upon via its first connection with the medium pressure present at the pressure connection, and which can be acted upon with the medium pressure present at the pressure connection via its second connection or with a delivery cell is connected, which has no direct connection to the pressure connection. Are both connections of the intermediate capacity with the conveying connected intermediate pressure, this intermediate capacity is charged.
  • the intermediate capacity has a certain elasticity, which is dependent on the one hand on the size of its volume and on the other hand on the degree of foaming of the conveying medium itself.
  • the storage capacity of the intermediate capacity is low at low degrees of foaming and large at high degrees of foaming is.
  • the pressure equalization process is mainly determined by the size of the resistors connected in series in the two connections.
  • the first connection of the intermediate capacitance is connected to the pressure connection.
  • the first connection is directly connected to the pressure connection on the pump chamber side.
  • the intermediate capacity can be arranged in the immediate vicinity of the pressure connection, so that very long connection connections between the pressure connection and the intermediate capacity are not necessary.
  • the second connection of the intermediate capacitance opens into the wall of the pump chamber and is swept by conveying elements delimiting the conveying cells.
  • the charging or discharging process is controlled solely by the conveying elements sliding over the opening openings of the connections, so that the Mouth opening of the second connection is closed or released by the conveying element in such a way that both connections are connected to the medium pressure or the first connection is pressurized by the medium pressure and the second connection is connected to the feed cell to be filled.
  • the intermediate capacity has approximately twice the volume of a delivery cell.
  • the above-mentioned elasticity of the intermediate capacity can be adjusted by varying the volume, so that the storage effect of the intermediate capacity can be matched to the degree of foaming that is present.
  • An embodiment is particularly preferred in which there is a hydraulic resistance in the first and / or second connection of the intermediate capacitance. This results in advantages in the case of low degrees of foaming of the conveyed medium, in which the pressure equalization process is mainly due to the size of the preferably in series with the intermediate capacitance switched resistors is determined. The intermediate capacity itself has a rather lower effect with these degrees of foaming.
  • the intermediate capacitance is formed by at least two partial capacitances which are connected in series in a particularly preferred embodiment.
  • a hydraulic resistance can be arranged between the two partial capacitances. In a preferred embodiment, this results in a series connection of partial capacitance, hydraulic resistance and partial capacitance. If there are also hydraulic resistors in the first and / or second connections, they are also preferably connected in series, so that overall there is a pure series connection of the hydraulic resistors and partial capacitances.
  • the intermediate capacitances are formed in the pump housing.
  • the intermediate capacities can, however, also be arranged in the wall of the pump chamber facing away from the pump chamber. Combination options are of course also conceivable. If the intermediate capacity is in the pump housing, this is, however, arranged very close to the pump chamber, so that long connection paths for the intermediate capacity are avoided.
  • a preferred embodiment of the pump is characterized in that the pumping chamber is composed of a pumping amber ring and at least one pressure located on the end faces of the pumping chamber ring.
  • plate is formed and / or is limited by the pump housing, wherein in a preferred embodiment there is a hydraulic resistance in one of the pressure plates and the intermediate capacity in the pump housing.
  • the hydraulic resistors can be realized by simple openings with a small cross section, which simultaneously form the first and second connection of the intermediate capacitance. Behind the pressure plate is then the intermediate capacity as a recess, which is covered by the pressure plate and is connected to the openings in the pressure plate.
  • the intermediate capacitance and / or the at least one hydraulic resistance can therefore lie in one of the pressure plates and / or in the pump chamber ring and / or in the pump housing.
  • the hydraulic resistance lies between the wall adjacent to the pump element and the wall (outer wall) of the pump chamber facing away from this wall.
  • the hydraulic resistance can thus be easily produced by a, preferably step-like, breakthrough.
  • the transition from the hydraulic resistance to the intermediate capacity is sealed in such a way that the medium cannot flow between the surfaces of the pressure plate and the pump housing, i.e. the transition is sealed off from other pressure areas is.
  • An embodiment is preferred in which the second connection of the intermediate capacitance opening into the pump chamber wall has a circular cross section.
  • the mouth region of the second connection is circular.
  • this opening area in the pump chamber wall is expanded at least in some areas. Opening cross-sectional expansions can thus be provided, such as those formed by notches in the pump chamber wall.
  • the notches can also influence the volume flow • that flows into the cell to be filled.
  • the notches can also have a constant or a changing cross section.
  • the volume flow entering the cell to be filled can thus be influenced as a function of the rotational position of the pump element.
  • a slowly increasing volume flow can also be provided if notches are used whose cross sections decrease in the opposite direction to the direction of rotation of the rotor. This is particularly advantageous for low degrees of foaming.
  • the pump can have several suction and pressure connections.
  • a multi-stroke pump can therefore be provided, with Intermediate capacities are formed according to the number of pressure connections.
  • An intermediate capacitance is therefore preferably provided for each pressure connection.
  • the pump according to the invention is particularly preferably a vane or roller cell pump in which the conveying elements are formed, among other things, by vanes or rollers.
  • the pump is particularly preferably used in automatic transmissions for supplying the working medium to the speed transmission means or hydraulic control elements, since oil is present in automatic transmissions with very different degrees of foaming.
  • one of the pressure plates is supported relative to the pump housing by means of a spacer, as is described in DE 199 00 927 AI.
  • an embodiment is preferred in which the pressure connection and / or the suction connection have an opening widening, so that the pressure compensation process is controlled both by the intermediate capacity and by the notches.
  • FIG. 1b shows an enlarged detail of the detail designated X in FIG.
  • FIG. 2 shows a cross section of the pump according to FIG. 1 a, the section being along the line II-II in FIG. 1 a,
  • FIG. 3 shows a detail of a “developed” rotor
  • Figure 4 shows various pressure profiles of a pump according to the prior art and the pump according to the invention.
  • the pump 1 is shown with the housing open, as can be seen from the section line Ia-Ia of Figure 2.
  • the pump 1 has a pump housing 2, which can be formed in several parts, in particular in two parts, so that — as in the present exemplary embodiment — a basic housing body 3 and housing cover 4 can be present.
  • the basic housing body 3 has a recess 5 in which a pump insert 6 is arranged.
  • This has a pump chamber 7 and a pump element 8 which is arranged in the pump chamber 7 so as to be driven in rotation.
  • the pump element 8 is driven by a drive shaft 9 which is mounted in the housing 2 and thus penetrates the housing 2 or the housing cover 4.
  • the drive shaft 9 is non-rotatably connected to the pump element 8 at one end. At its other end, not shown here, a drive torque can be introduced into the drive shaft 9.
  • the pump chamber 7 is delimited by a pump chamber ring 10 and by two pressure plates 11 and 12 lying on the end faces of the pump chamber ring. However, the pump chamber 7 can also be delimited by the pump chamber ring 10, one of the pressure plates 11 or 12 and the pump housing 2.
  • a spiral-shaped suction chamber 13 is formed around the pump chamber ring 10 and can be connected to a reservoir for a delivery medium, not shown here.
  • An opening 14 is formed between the pump chamber ring 10 and at least one of the pressure plates 11 or 12, which opens into the pump chamber 7 and thus connects the suction chamber 13 to the pump chamber 7 and thus forms a suction connection 15.
  • pumped medium is introduced into the pump chamber 7 via the suction connection 14, conveyed and expelled from the pump chamber 7 at a pressure connection 16.
  • the pump element 8 has a rotor 17 which can be driven in rotation.
  • Radially extending slots 18 are formed in the rotor, into each of which a radially displaceably guided wing 19 is introduced.
  • the wings 19 form conveyor elements 20 which — viewed in the direction of rotation D — limit conveyor cells 21.
  • the delivery cells 21 are delimited radially on the outside by a sliding surface 22 of the pump chamber ring 10, on which the delivery elements 20 slide or roll along.
  • the conveyor cells 21 are laterally delimited by the pressure plates 11 and 12. Due to the cross-sectional shape of the opening in the pump chamber ring 10, the delivery cells 21 are variable in volume.
  • the delivery cells 21 rotate within the pump chamber 7, so that they alternate. are in connection with the suction connection 15 and the pressure connection 16.
  • a vane pump is present in the present exemplary embodiment.
  • the pump 1 can also be designed as a roller cell pump.
  • roller-like conveying elements 20 are provided, which lie in corresponding recesses in the rotor 17.
  • the pressure connection 16 opens into a pressure chamber 23, which lies in the housing 2, in particular in the basic housing body 3, and here is formed purely for example by a section of the recess 5 and is delimited by the pressure plate 11.
  • the pressure chamber 23 is closed off from the suction chamber 13 by means of a seal 24.
  • the pressure chamber 23 is connected to a consumer connection 25, to which a consumer, not shown here, can be connected, which is to be acted upon by the pumped medium.
  • the consumer can be, for example, an automatic transmission, for which purpose it is provided in particular that the housing 2 is flanged within the automatic transmission, so that the consumers in the automatic transmission are supplied via the consumer connection 25 connected to the pressure chamber.
  • the pump 1 is designed as a double-stroke pump. It therefore has two pressure connections 16 and two suction connections 15.
  • a single-stroke pump with a pressure connection 16 and a suction connection 15 can also be provided.
  • pumps can also be implemented whose pumping have more than two suction and two pressure connections.
  • the pressure connection 16 opens into the pump chamber 7, preferably in a so-called pressure kidney 26, which can be formed in the pressure plate 11 and / or 12.
  • the suction connection 15 can open into a so-called suction kidney, as can be seen in particular from FIG.
  • opening extensions 27 and 28 can be formed, which are preferably implemented as a notch, the cross section of which widens in the direction of rotation of the rotor, as shown in the opening extension 28, or which extends in the direction of rotation of the rotor are tapered in cross-section, as can be seen in the opening widening 27.
  • the pump 1 has at least one hydraulic intermediate capacity 29, which can thus temporarily store and release the pumped medium.
  • the intermediate capacity 29 is acted upon by the medium pressure prevailing at the pressure connection 16, depending on the rotational position of the pump element 8.
  • the temporarily stored pumped medium is delivered to a pumping cell 21, which is neither directly connected to the suction port 16 nor to the pressure port 15.
  • the intermediate capacitance 29 is charged when its first connection 30 and its second connection 31 lie within a conveyor cell 21 which has a direct connection to the pressure connection 16.
  • 1 a shows a rotor position in which the first connection 30 lies within a first delivery cell 21 'and the second connection lies in a second delivery cell 21'', this delivery cell 21''having no direct connection to the suction connection 15 and the pressure connection 16.
  • the two connections 30 and 31 are thus - seen in the circumferential direction of the rotor 17 - at a distance from one another.
  • the first connection 30 of the intermediate capacitance 29 is connected directly to the pressure connection 16, as can be seen from FIGS. 1a and 1b.
  • the second connection 31 of the intermediate capacitance 29 opens into the wall W of the pump chamber, specifically in the region of the wall W which is swept by the delivery cells 21, 21 ', 21' ', that is to say faces the rotor 17.
  • the second connection 31 opens out on the surface of the pressure plate 12 facing the rotor 17.
  • the second connection 31 of the intermediate capacitance 29 could also open out on the sliding surface 22. Of course, this also applies to the first connection 30 of the intermediate capacitance 29.
  • the intermediate capacitance 29 lies in the housing 2, in particular in the housing cover 4, the pump 1 and the first and second connection 30, 31 are formed in the pressure plate 12. So that the pumped medium cannot get between the contact surfaces between the pressure plate 12 and the housing cover 4, sealing means 32 are provided which, as shown in FIG. 2, can be formed in the housing 2, in particular the housing cover 4, or else in the pressure plate 12.
  • the connections 30 and 31 are realized in the pressure plate 12 as openings, which preferably have a circular cross section. An embodiment is preferred in which the openings 33 and 34 are designed as step openings. Hydraulic resistors 35 and 36 are formed within the first and / or second connections, that is, within the openings 33 and 34, respectively, which are thus in series with the intermediate capacitance 29.
  • the intermediate capacitance 29 can also lie in the wall W 'of the pump chamber 7 according to one exemplary embodiment, this wall W' forming the outer wall of the pump chamber 7.
  • the intermediate capacitance 29 could thus also lie in the pressure plate 11 and / or 12 and / or in the pump chamber 10. As shown, it can of course also be located in one of the housing parts 3 and / or 4.
  • the hydraulic resistors 35 and 36 lie between the wall W and the outer wall W ′′ of the pump chamber 7.
  • the intermediate capacitance 29 can also comprise a plurality of interconnected partial capacitances 37, 38, the first partial capacitance 37 being connected to the first connection 30 and the second partial capacitance 38 being connected to the second connection 31.
  • the two partial capacitances 37 and 38 are connected to one another, a hydraulic resistor 39 preferably being interposed. This results in a series connection of hydraulic resistance 34, partial capacity 37, hydraulic resistance 39, partial capacity 38 and hydraulic resistance 35.
  • the capacity of the intermediate capacity 29 is dimensioned such that it has approximately twice the volume of a delivery cell 21.
  • the volume of the intermediate capacity is to be divided accordingly if partial capacities 37, 38 are provided.
  • the volumes of the partial capacities 37, 38 can be the same or different. A parallel connection of partial capacities with the same or different volumes would also be conceivable.
  • the intermediate capacitance 29 is formed in the pump housing 2.
  • the pressure plate 12 it would also be conceivable to produce both the connections 30 and 31, the hydraulic resistors 35, 36 and 39 and intermediate capacitance 29 in the pressure plate 12. It would also be conceivable to provide the intermediate capacitance and / or the hydraulic resistances in the pump chamber ring 10.
  • the mouth regions of the first and second connections 30, 31 can be circular.
  • the second connection 31 in its mouth region 40 can also be expanded.
  • a notch K can be provided, which extends from the opening area 40 against the direction of rotation of the rotor 17.
  • the notches can have a constant cross-section; however, it is also possible for the mouth region 40 to art is that it widens or narrows in or against the direction of rotation of the rotor.
  • FIG. 4 shows various pressures over the angle of rotation of the pump element for a known pump without intermediate capacity 29 and for the pump 1 according to the invention with intermediate capacity 29.
  • the assignment of the graphs results from the following legend:
  • the following consideration applies to a delivery cell that has been filled up to a rotation angle ⁇ l of the rotor 17 via the suction connection 15. From the angle of rotation ⁇ l, the feed cell 21 is charged by the intermediate capacity 29. The delivery cell pressure 45 thus begins to rise slightly. The pressure 44 in the intermediate capacity 29 drops because it discharges into the delivery cell 21.
  • the intermediate capacity 29 relaxes in the direction of the cell to be filled, as from Angle of rotation ⁇ l to ⁇ 3 is shown in Figure 4. If the pump element continues to rotate during this period, the intermediate capacity 29 ensures an earlier pressure increase in the delivery cell 21. From the angle ⁇ 3, the operating pressure now charges both the cell to be filled and the intermediate capacity 29. Since the operating pressure has to charge a larger volume, which, as just mentioned, results from the intermediate capacity 29 and the cell to be filled, the pressure in the delivery cell 21 increases more gently.
  • FIG. 2 also shows that the pressure plate 12 is supported at a distance from the bottom B of the recess 5 by a spacer 46.
  • the spacer 46 can be realized in one piece with the housing part 4 or the pressure plate 12. However, it can also be provided as a separate insert.
  • a mechanical gap compensation is implemented with the distance means 46, in which the area of the pressure plate 12 bends within the distance means 46 in the direction of the rotor 17 and thus reduces the leakage gap.
  • the sealing effect of the sealant 32 is not affected.
  • DE 199 00 927 AI describes the pressure plate support by means of spacers and the gap compensation in detail.

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

Abstract

L'invention concerne une pompe comprenant une chambre dans laquelle est monté un élément de pompe pouvant être entraîné en rotation ; au moins un raccord d'aspiration débouchant dans la chambre et au moins un raccord de refoulement ; et des cellules de refoulement rotatives, à volume variable qui sont raccordées, en fonction de la position de rotation de l'élément de pompe, au raccord d'aspiration ou au raccord de refoulement. Une capacité intermédiaire hydraulique peut être soumise à la pression d'un fluide de refoulement, régnant dans le raccord d'aspiration, par l'intermédiaire de son premier raccord, à la pression d'un fluide de refoulement, régnant dans le raccord de refoulement, par l'intermédiaire de son deuxième raccord, en fonction de la position de rotation de l'élément de pompe, ou est raccordée à une cellule de refoulement qui ne communique pas directement avec le raccord de refoulement.
EP01945237A 2000-06-08 2001-06-01 Pompe Expired - Lifetime EP1292773B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10027990 2000-06-08
DE10027990A DE10027990A1 (de) 2000-06-08 2000-06-08 Pumpe
PCT/EP2001/006282 WO2001094791A1 (fr) 2000-06-08 2001-06-01 Pompe

Publications (2)

Publication Number Publication Date
EP1292773A1 true EP1292773A1 (fr) 2003-03-19
EP1292773B1 EP1292773B1 (fr) 2008-02-13

Family

ID=7644873

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01945237A Expired - Lifetime EP1292773B1 (fr) 2000-06-08 2001-06-01 Pompe

Country Status (6)

Country Link
US (1) US6817847B2 (fr)
EP (1) EP1292773B1 (fr)
JP (2) JP5250171B2 (fr)
DE (3) DE10027990A1 (fr)
ES (1) ES2299492T3 (fr)
WO (1) WO2001094791A1 (fr)

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DE102018133680A1 (de) 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit
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DE102019132729A1 (de) 2019-12-02 2021-07-01 Schwäbische Hüttenwerke Automotive GmbH Sickendichtung
DE102020116748A1 (de) 2020-06-25 2022-02-17 Schwäbische Hüttenwerke Automotive GmbH Pumpe mit axial wirksamer Federdichtung
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DE102022203867A1 (de) 2022-04-20 2023-10-26 Hanon Systems Efp Deutschland Gmbh Gerotorpumpe
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ES2299492T3 (es) 2008-06-01
US6817847B2 (en) 2004-11-16
DE10192363D2 (de) 2003-05-08
WO2001094791A1 (fr) 2001-12-13
JP2003536022A (ja) 2003-12-02
EP1292773B1 (fr) 2008-02-13
DE50113597D1 (de) 2008-03-27
JP2013050112A (ja) 2013-03-14
JP5250171B2 (ja) 2013-07-31
DE10027990A1 (de) 2001-12-20
US20040091381A1 (en) 2004-05-13

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