WO2001094751A1 - Axialkolbenmaschine - Google Patents
Axialkolbenmaschine Download PDFInfo
- Publication number
- WO2001094751A1 WO2001094751A1 PCT/EP2001/002255 EP0102255W WO0194751A1 WO 2001094751 A1 WO2001094751 A1 WO 2001094751A1 EP 0102255 W EP0102255 W EP 0102255W WO 0194751 A1 WO0194751 A1 WO 0194751A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- axial piston
- tooth
- piston machine
- machine according
- coupling
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0032—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F01B3/0044—Component parts, details, e.g. valves, sealings, lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B3/00—Reciprocating-piston machines or engines with cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F01B3/0082—Details
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2014—Details or component parts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/2092—Means for connecting rotating cylinder barrels and rotating inclined swash plates
Definitions
- the invention relates to an axial piston machine according to the preamble of claim 1.
- the interior of the housing as an intermediate collecting container for leakage fluid.
- the leakage fluid in the interior of the housing can be used to lubricate moving parts of the axial piston machine. It is also advantageous if the leakage fluid is present as a film between the contact surfaces of parts that are not moved relative to one another, as a result of which contact corrosion and abrasion resulting from vibrations are avoided or at least reduced. It is also advantageous if the hydraulic fluid can reach the desired lubrication points as freely as possible.
- a barrier in the interior of the housing which prevents the desired supply of the fluid to the lubrication point.
- a barrier forms a multi-tooth coupling between two parts of the axial piston machine in the housing interior.
- the purpose of a multi-tooth coupling is to rigidly connect two parts together, e.g. B. against a relative rotation to each other.
- Such a multi-tooth clutch can be provided in the axial piston machine of the type specified at the beginning between a drive shaft and a cylinder drum mounted thereon.
- a multi-tooth clutch Since a multi-tooth clutch is to transmit considerable clutch forces, one is endeavors to shape the abutting surfaces of the multi-tooth coupling not only in the area of the flanks of the teeth and the tooth gaps so that they lie largely close to each other. As a result, the multi-tooth clutch forms a liquid barrier which prevents or at least reduces the access of the hydraulic fluid to both sides of the multi-tooth clutch.
- the multi-tooth coupling forms a barrier which prevents the fluid from flowing from one side to the other side of the multi-tooth coupling.
- This is particularly problematic in the known embodiment because the fluid is prevented from flowing into an annular space between the drive shaft and the cylinder drum.
- a roller bearing arranged in the area of a control disk for the rotary mounting of the drive shaft on the relevant housing wall is hereby separated from the hydraulic fluid by intensive flow, lubrication and cooling.
- the toothing is weakened when the bores for the pressure pins extend right through the teeth or a tooth is left out in the area of a pressure pin.
- DE 198 28 429 AI describes an axial piston machine with a retraction device with pressure pins similar to the retraction device described above.
- three pressure pins distributed around the circumference are each slidably mounted in a first through-channel, which is arranged in the foot region of a missing tooth of the cylinder drum.
- the missing teeth form second through-channels for the fluid.
- the stability or strength of the toothed ring coupling is impaired due to the lack of teeth.
- the invention has for its object to design an axial piston machine of the type mentioned in such a way that, while ensuring a stable design, the multi-tooth coupling enables flow passage and / or mechanical implementation from one side to the other side of the multi-tooth coupling.
- the at least one lead-through channel according to the invention is arranged in a tooth tip surface and / or in an opposite tooth space base surface, it is located in an area which is insensitive to weakening and the flanks of the teeth or tooth spaces are unaffected.
- the inventive one Design therefore neither to a substantial weakening of the cross section of the teeth nor to a reduction in the surface pressure.
- the stability and service life of the multi-tooth coupling is thus retained despite the presence of one or more through-channels arranged distributed around the circumference.
- a plurality of feed-through channels preferably distributed uniformly over the circumference of the toothing. It is also possible to arrange the lead-through channel only in one of the opposing tooth tip surface and tooth space base surface or opposite one another in both surfaces. The latter leads to a common passage channel with an enlarged cross section.
- the cross-sectional shape of the at least one feed-through channel can be different and can be adapted to structural conditions.
- a rounded or semicircular or U-shaped cross-sectional shape is advantageous in order to avoid a notch effect.
- the cross-sectional shape can also be angular or hollow-wedge-shaped, which is advantageous for reasons of production technology and reasons mentioned below.
- the at least one feed-through channel according to the invention can, however, also serve to receive a pin as part of the axial piston machine, e.g. B. a prescribed pressure pin, which extends between two arranged on both sides of the multi-tooth coupling and axially movable components, for. B. between a compression spring and a support ring for a retraction device.
- the pressure pin passes through the feed-through channel and can e.g. B. be slidably guided therein with little movement.
- the feed-through channel does not serve to create a flow connection between both sides of the multi-tooth coupling, but rather serves to create a mechanical one that extends through the through-channel To enable connection, and also without significantly affecting the stability of the toothing.
- the pin can be slidably guided in the lead-through channel with little movement so that there is no fluid feedthrough.
- the at least one feed-through channel is designed with a sufficiently larger cross section than the pin, then the configuration according to the invention can form a passage both for the mechanical connection and for the fluid.
- the feed-through channel is open to the tooth tip surface or tooth space base surface.
- the advantage of this embodiment is that the at least one bushing can be produced as a groove simply and inexpensively, for. B. by machining with a shaping tool, a broaching tool, a roller hammer tool or a milling tool, especially when the profile is included in the milling cutter geometry.
- FIG. 1 shows an axial piston machine according to the invention in axial section
- Fig. 2 shows the partial section II-II in Fig. 1 with several modified configurations
- FIG. 4 shows an axial piston machine according to the invention in axial section in a further modified embodiment
- Fig. 5 shows the partial section VV in Fig. 4;
- Fig. 6 is a section corresponding to the partial section V-V in modified configurations
- the axial piston machine 1 shown by way of example has a closed housing 2 with a cup-shaped housing part 3, the housing interior 4 of which is releasably closed by a so-called connecting part 5, which is screwed in the sense of a cover on the free edge of the housing part 3 by means of screws 6 which are indicated.
- a drive shaft 7 is rotatably mounted, which passes through the bottom wall 3a of the cup-shaped housing 3 in a bearing hole 8 and is directly or indirectly supported by roller bearings 9, 11 on the bottom wall 3a of the cup-shaped housing 3 and on the connecting part 5.
- a control disk 13 On the inside of the connection part 5, a control disk 13 is arranged with control channels 14 running approximately parallel to the axis of rotation 7a of the drive shaft 7, each of which is connected to a feed line 15 and a discharge line 16 in the connection part 5.
- a plurality of piston bores 21 extending approximately axially parallel are arranged in the cylinder drum 17, which are connected at their ends facing the control channels 14 by tapered feed and discharge channels 22 to the control channels 14 and on the side facing away from the control disk 13 from the Open cylinder barrel 17.
- pistons 23 are mounted so as to be axially displaceable, the ends of the working chambers 24 in the piston bores 21 with their ends facing the control disk 13 and with their head ends facing away from the control disk 13 projecting out of the cylinder drum 17 and by means of support joints 25, in particular ball joints, are axially supported on a swash plate 26 in an oblique transverse plane.
- the swash plate 26 is formed by a so-called swash plate, which is rigid in an axial piston machine 1 with a constant throughput volume and is pivotable in an axial piston machine 1 with a variable throughput volume about a pivot axis 27 extending at right angles to the axis of rotation 7a and by itself
- Known and not shown adjusting device is adjustable and lockable in the respectively set position.
- Hollow cylinder-section-shaped bearing surfaces 31a on the swivel plate and a swivel bearing can serve this purpose.
- the swash plate On its side facing the cylinder drum 17, the swash plate has an inclined surface 26a, on which the pistons 23 are supported by sliding shoes 29, which are pivotally connected to the head ends of the pistons 23 by the supporting joints 25.
- the swash plate 26 is mounted on the bottom wall 3a, for which purpose a bearing ring 31 can be provided which is supported on the bottom wall 3a and has a bearing hole in which the associated roller bearing 9 is mounted.
- An axial through hole is arranged in the swash plate 26, through which the drive shaft 7 extends with play.
- the drive shaft 7 and the cylinder drum 17 rotate together about the axis of rotation 7a, the pistons being in due to the inclined plane on the swash plate 26, here on the inclined surface 26a the piston bores 21 are moved back and forth.
- the axial piston machine 1 can work in pump mode or in motor mode.
- the sliding shoes 29 are assigned a retraction device 33 which holds the sliding shoes 29 in contact with the inclined surface 26a and, in the present exemplary embodiment, is formed by a retraction disc 33 which has 35 flanges 29a with perforated edges the sliding shoes 29 engage in a manner known per se.
- the retraction plate 33 is axially supported with a spherical-zone-shaped concave bearing surface 37 on a corresponding spherical-zone-shaped convex bearing surface 38 on a support ring 39 which is axially displaceably mounted on the drive shaft 7 with a bearing hole 41 and is supported with a force in the direction of the cylinder drum 17, which is greater than the lifting forces.
- the support ring 39 is preferably connected in a rotationally fixed manner to the drive shaft 7 by a second multi-tooth coupling 19a, the teeth 43a being provided jointly for both multi-tooth clutches and can be correspondingly long.
- the multi-tooth coupling 19 consists of a plurality of teeth 43a, 44a and tooth gaps 43b, 44b which are arranged on the lateral surface of the drive shaft 7 or on the inner lateral surface of the cylinder drum 13 and follow one another regularly in the circumferential direction whose main shape and size are each designed so that the teeth Fill in tooth gaps essentially.
- the teeth are each loaded in the circumferential direction during rotary driving in the functional mode, effective compressive forces being transmitted in the circumferential direction, which generate a specific surface pressure on the tooth flanks 43c, 44c delimiting the teeth 43a, 44a.
- the surfaces extending between the flanks 43c, 44c are designated with top surfaces 43d, 44d and tooth space base surfaces 43e, 44e.
- the multi-tooth coupling 19 forms a barrier wall or barrier due to the relatively tight contact, which prevents flow of the fluid between the interior sections 4a, 4b arranged on both sides of the multi-tooth coupling 19.
- the toothing preferably has a lead-through channel 45 in the center in at least one tooth tip surface 43d, 44d and / or in at least one tooth space base surface 43e, 44e of the drive shaft 7 and / or the cylinder drum 17 which thus connects the two interior sections 4a, 4b with one another so that a flow can take place.
- the feed-through channel also serves to connect the other interior section 4b to the leakage drain.
- the at least one feed-through channel 45 has, because of its opening to the associated head or base surface 43d, 44d, 43e, 44e, a groove which can be produced in one work step with the tooth profile, e.g. B. by a broaching, impact or roller hammer tool.
- a groove which can be produced in one work step with the tooth profile, e.g. B. by a broaching, impact or roller hammer tool.
- Feed-through channel 45 can be rounded (FIGS. 2 and 5) or curved in the form of a circular arc (FIG. 7) or angular
- Figs. 3 and 6 for. B. be square or triangular.
- the feed-through channels 45 in the tooth tip surfaces 43d, 44d and / or in the tooth gap base surfaces 43e, 44e of the drive shaft 7 and / or the cylinder drum 17 can follow one another directly in the circumferential direction or if one or more Zannkopf surfaces 43d, 44d and / or tooth gap base surfaces 43e, are omitted, 44e may be arranged.
- the above-mentioned and still to be described exemplary embodiments can be used either in combination or individually.
- the spring 42 is arranged on the side of the multi-tooth clutch 19 facing the control disk 13 in an annular space arranged between the cylinder drum 17 and the drive shaft 7 and preferably formed by a helical spring which, with its end facing the control disk 13, presses against an inner shoulder surface 47 on the cylinder drum 17 and prestresses it against the control disk 13.
- the end of the spring 42 facing away from the control disk 13 pretensions the retraction device 33 with a plurality of axial pressure pins 48 arranged opposite one another, each of which extends through a feed-through channel 45 to the support ring 39.
- a pressure ring 49 can be arranged between the pressure pins 48 and the spring 42.
- the length of the pressure pins 48 is larger than the axial length of the multi-tooth coupling 19, so that they protrude into the annular space 46.
- the feed-through channels 45 form axial guides for the pressure pins 48. If the cross-sectional shape and size of the feed-through channels 45 are adapted to the cross-sectional shape and size of the pressure pins 48 with a slight amount of movement, the feed-through channels 45 only perform a guide function for the pressure pins 48 In such a case, another flow passage can ensure that the fluid passes from one housing interior section 4a to the other 4b, here in the annular space 46 and to the roller bearing 11, in order to lubricate this area and possibly also to cool it and / or to rinse.
- An adapted cross-sectional shape results, for. B. if two z. B. semicircular feed-through channels 45 are arranged opposite each other, in which a common round or square pressure pin 48 surrounds with little movement, as shown in FIG. 7 on the right.
- the feed-through channels 45 in such a way that they both form a guide function for the pressure pins 48 and also form at least one passage for the fluid.
- This can be achieved in that the number of feed-through channels 45 is greater than the number of pressure pins 48 and thus at least one feed-through channel 45 can serve as a free passage.
- this can also be achieved in that the cross-sectional shape of the feed-through channels 45 and that of the pressure pins 48 are different.
- a square shape for the feed-through channels 45 and a round shape for the pressure pins 48 are appropriate.
- opposing, e.g. B. in cross section angular feed-through channels 45 a common pressure pin 48 different, for. B. round cross-sectional shape, as shown in Fig. 7 left.
- the feed-through channels 45 can have a guiding function on the Apply pressure pins 48 by guiding them linearly and leaving free passage cross sections 45a through which a fluid flow can take place.
- All the exemplary embodiments according to the invention have in common that a weakening of the tooth flanks 43c and 44c is avoided. Since there are no teeth 43a, 44a, an effective connection between the drive shaft 7 and the cylinder drum 17 is created despite the feed-through channels 45.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Reciprocating Pumps (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10028336A DE10028336C1 (de) | 2000-06-08 | 2000-06-08 | Axialkolbenmaschine |
DE50111740T DE50111740D1 (de) | 2000-06-08 | 2001-02-28 | Axialkolbenmaschine |
EP01915304A EP1287232B1 (de) | 2000-06-08 | 2001-02-28 | Axialkolbenmaschine |
PCT/EP2001/002255 WO2001094751A1 (de) | 2000-06-08 | 2001-02-28 | Axialkolbenmaschine |
US10/220,325 US6796774B2 (en) | 2000-06-08 | 2001-02-28 | Axial piston engine |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10028336A DE10028336C1 (de) | 2000-06-08 | 2000-06-08 | Axialkolbenmaschine |
DE10028336.5 | 2000-06-08 | ||
PCT/EP2001/002255 WO2001094751A1 (de) | 2000-06-08 | 2001-02-28 | Axialkolbenmaschine |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2001094751A1 true WO2001094751A1 (de) | 2001-12-13 |
Family
ID=26006018
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2001/002255 WO2001094751A1 (de) | 2000-06-08 | 2001-02-28 | Axialkolbenmaschine |
Country Status (4)
Country | Link |
---|---|
US (1) | US6796774B2 (de) |
EP (1) | EP1287232B1 (de) |
DE (1) | DE10028336C1 (de) |
WO (1) | WO2001094751A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4111901B2 (ja) * | 2003-09-26 | 2008-07-02 | 株式会社日本自動車部品総合研究所 | 流体機械 |
US9752570B2 (en) | 2014-02-13 | 2017-09-05 | S-RAM Dynamics | Variable displacement compressor and expander |
EP3020966B1 (de) * | 2014-11-11 | 2020-01-22 | Danfoss A/S | Axialkolbenmaschine |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2776628A (en) * | 1952-07-10 | 1957-01-08 | Vickers Inc | Power transmission |
US3139038A (en) * | 1961-07-17 | 1964-06-30 | Applied Power Ind Inc | Engine |
DE3222210A1 (de) | 1982-06-12 | 1983-12-15 | Linde Ag, 6200 Wiesbaden | Schraegscheiben-axialkolbenmaschine |
US5784949A (en) * | 1997-06-25 | 1998-07-28 | Sauer Inc. | Retaining system for slipper holddown pins |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1405856A1 (de) * | 1960-05-27 | 1969-01-02 | Daimler Benz Ag | Drehfeste Verbindung zwischen drehmomentuebertragenden Teilen von Kraftfahrzeuggetrieben,z.B. Verbindung von Zahnraedern mit ihren Wellen |
US3675539A (en) * | 1970-08-07 | 1972-07-11 | Parker Hannifin Corp | Hydraulic motor |
US3698287A (en) * | 1970-12-09 | 1972-10-17 | Cessna Aircraft Co | Axial piston device |
DE4206087C2 (de) * | 1992-02-27 | 1994-01-27 | Linde Ag | Hydromechanischer Radantrieb |
-
2000
- 2000-06-08 DE DE10028336A patent/DE10028336C1/de not_active Expired - Fee Related
-
2001
- 2001-02-28 US US10/220,325 patent/US6796774B2/en not_active Expired - Fee Related
- 2001-02-28 WO PCT/EP2001/002255 patent/WO2001094751A1/de active IP Right Grant
- 2001-02-28 EP EP01915304A patent/EP1287232B1/de not_active Expired - Lifetime
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2776628A (en) * | 1952-07-10 | 1957-01-08 | Vickers Inc | Power transmission |
US3139038A (en) * | 1961-07-17 | 1964-06-30 | Applied Power Ind Inc | Engine |
DE3222210A1 (de) | 1982-06-12 | 1983-12-15 | Linde Ag, 6200 Wiesbaden | Schraegscheiben-axialkolbenmaschine |
US5784949A (en) * | 1997-06-25 | 1998-07-28 | Sauer Inc. | Retaining system for slipper holddown pins |
DE19828429A1 (de) | 1997-06-25 | 1999-02-04 | Sauer Inc | Vorrichtung zum radialen Sichern von Gleitstückniederhaltestiften in einer hydraulischen Einheit |
Also Published As
Publication number | Publication date |
---|---|
US20030010195A1 (en) | 2003-01-16 |
US6796774B2 (en) | 2004-09-28 |
EP1287232B1 (de) | 2006-12-27 |
EP1287232A1 (de) | 2003-03-05 |
DE10028336C1 (de) | 2002-04-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE2759764C2 (de) | Axialkolbenkompressor | |
EP1078165B1 (de) | Spiralkompressor | |
EP0162238B1 (de) | Axialkolbenmaschine, insbesondere -pumpe der Schrägscheiben- bauart | |
EP0102915B1 (de) | Hydraulischer Radialkolbenmotor | |
WO2007118624A1 (de) | Hydrostatische kolbenmaschine mit drehbarer steuerscheibe | |
DE102008013991A1 (de) | Pumpe oder Motor | |
DE3333812C2 (de) | Schwenktrommel-Axialkolbenmaschine | |
DE19755386C2 (de) | Hydrostatische Maschine mit einer drehbar gelagerten Zylindertrommel und einer einstellbaren Schwenkscheibe | |
DE882932C (de) | Raeumlich arbeitendes Hubkolbengetriebe | |
DE2124644B2 (de) | Axialkolbenmaschine mit umlaufender Zylindertrommel | |
DE3206152A1 (de) | Kreuzkopf einer kolbenmaschine | |
DE10028336C1 (de) | Axialkolbenmaschine | |
EP1588051A1 (de) | Kolbenmaschine, welle und wälzlager für eine kolbenmaschine | |
DE102006044294B3 (de) | Radialkolbenpumpe | |
DE4232191C1 (de) | Vorrichtung zum Verstellen der Exzentrizität eines exzentrischen Radiallagers | |
DE19527649A1 (de) | Axialkolbenmaschine | |
DE3733083A1 (de) | Verstellbare axialkolbenmaschine in schraegscheibenbauweise | |
DE1653613C3 (de) | Mitnahmevorrichtung für die Pleuelstangen einer Schrägscheiben-Axialkolbenmaschine | |
EP0341390A2 (de) | Kolbeneinrichtung für eine Kolbeneinheit | |
DE4237463C2 (de) | Ausgleichsgetriebe | |
DE1176954B (de) | Stufenlos regelbare hydrostatische Kraft-uebertragung | |
DE2812906C2 (de) | Hydrostatische Servolenkung für Fahrzeuge | |
DE10017780A1 (de) | Kolbenmaschine | |
DE2254751B2 (de) | Radialkolbenmaschine | |
DE2134944C3 (de) | Kolbenmaschine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AK | Designated states |
Kind code of ref document: A1 Designated state(s): US |
|
AL | Designated countries for regional patents |
Kind code of ref document: A1 Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LU MC NL PT SE TR |
|
DFPE | Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101) | ||
121 | Ep: the epo has been informed by wipo that ep was designated in this application | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2001915304 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 10220325 Country of ref document: US |
|
WWP | Wipo information: published in national office |
Ref document number: 2001915304 Country of ref document: EP |
|
WWG | Wipo information: grant in national office |
Ref document number: 2001915304 Country of ref document: EP |