EP0383167A1 - Moteur à pistons axiaux - Google Patents

Moteur à pistons axiaux Download PDF

Info

Publication number
EP0383167A1
EP0383167A1 EP90102354A EP90102354A EP0383167A1 EP 0383167 A1 EP0383167 A1 EP 0383167A1 EP 90102354 A EP90102354 A EP 90102354A EP 90102354 A EP90102354 A EP 90102354A EP 0383167 A1 EP0383167 A1 EP 0383167A1
Authority
EP
European Patent Office
Prior art keywords
cylinder drum
piston
axial
drive shaft
additional device
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
EP90102354A
Other languages
German (de)
English (en)
Other versions
EP0383167B1 (fr
Inventor
Franz Dipl.-Ing. Forster (Fh)
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.)
Linde GmbH
Original Assignee
Linde GmbH
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 Linde GmbH filed Critical Linde GmbH
Publication of EP0383167A1 publication Critical patent/EP0383167A1/fr
Application granted granted Critical
Publication of EP0383167B1 publication Critical patent/EP0383167B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F01B3/0041—Arrangements for pressing the cylinder barrel against the valve plate, e.g. fluid pressure

Definitions

  • the invention relates to an axial piston machine with a rotating cylinder drum, which has a plurality of cylinder bores arranged concentrically to the axis of rotation with pistons longitudinally displaceable therein and bears against a control surface fixed to the housing, the pistons engaging with an active surface which can be positioned obliquely to the axis of rotation and the cylinder bores with connecting openings Control channels of the control surface are provided, wherein the cylinder drum is also mounted to be longitudinally movable and an additional device for controlling the pressing force of the cylinder drum on the control surface is provided, which is in operative connection with the cylinder drum.
  • the pump has the highest possible absorbency in order to minimize the filling losses caused by suction-side flow losses and the resulting reduction in the delivery volume.
  • the flow losses depend on the flow rate of the pumped medium in the suction channel of the pump and on its design. It is therefore necessary that the intake duct has the largest possible cross section in order to keep the flow velocity and thus the pipe friction and the flow losses low.
  • Axial piston machines now have a special feature that also leads to filling losses. This consists in the design-related gap between the control surface fixed to the housing, which contains the mouths of the suction channel designed as kidney-shaped control channels, and the rotating cylinder drum resting against them.
  • the gap is necessary so that a hydrostatic lubricating film can form between the webs of the control surface and those of the cylinder drum, which reduces the friction and enables the machine to run smoothly and smoothly.
  • the gap causes external leakage currents and internal leakage currents that flow directly from the high-pressure to the low-pressure side of the control surface. The resulting loss of current reduces the volumetric efficiency of the machine and thus the actual delivery volume.
  • the gap between the rotating cylinder drum and the control surface must be kept as small as possible. This is achieved on the one hand in that the cylinder drum is pressed against the control surface by a compression spring, and on the other hand in that a connection is made between the cylinder bores and the control channels through openings, the diameter of which is smaller than the diameter of the cylinder bores.
  • the latter measure presses the cylinder drum against the control surface as a result of the liquid pressure in the cylinder bores, the contact pressure being proportional to the load on the machine.
  • the leakage currents and filling losses of the axial piston machine are kept at a low level.
  • the narrowed connection openings between the cylinder bores and the control channels represent a constriction of the suction channel, which leads to a certain flow rate in this area for a certain desired delivery volume and thus to flow losses and, according to the flow rate, to a limitation of the absorbency of such a machine compared to a machine without this constructive measure.
  • the geometrical conditions on the suction side are thus essentially determined from the balance of forces and moments between hydrostatic relief of the rotating cylinder drum and limitation of the relief gap.
  • the present invention has for its object to avoid the disadvantages mentioned and to increase the absorbency of an axial piston machine in an economical manner.
  • the achievement of the object is that the additional device is arranged in an annular cavity of the cylinder drum. This allows an additional device without requiring additional space and with simple means be created that controls the pressing force of the cylinder drum to the control surface, for example, increasing. An additional axial force is thus generated in the direction of the control surface.
  • the additional pressure achieved in this way can be used in accordance with the balance of forces and moments to enlarge the kidney-shaped control channels in the control surface and the connection openings to the cylinder bores. Under certain circumstances, even the diameter of the connection openings can correspond to the diameter of the cylinder bores. In any case, this is associated with a significant improvement in the absorbency of the axial piston machine and an increase in the possible suction speed, which is particularly advantageous in machines that work in an open circuit.
  • An increase in the suction speed means that the machine can be absorbent in a speed range that enables operation via a directly connected drive machine, so that a previously required reduction gear can be dispensed with. This leads to an increase in the efficiency of such
  • the present invention can also be used for machines which operate in a closed circuit. Both the control channels can be enlarged and the webs between them can be widened. The additional hydrostatic relief of the cylinder drum caused by a web widening is then compensated for by the axial force generated by the additional device.
  • the additional device contains at least one piston surface which can be subjected to operating pressure depending on the flow rate.
  • the pressure force of the cylinder drum on the control surface is controlled by the medium under operating pressure, which acts on the piston surface.
  • the medium is removed from the high pressure control channels.
  • the arrangement of the additional device can be used both in machines whose cylinder drum is mounted so as to be longitudinally movable on a drive shaft which passes centrally through them, and in machines which do not have a continuous shaft.
  • the additional device presses the cylinder drum against the control surface and the cylinder drum is centrally penetrated by a drive shaft
  • the piston surface is formed between a hollow cylindrical inner surface of the cylinder drum and two annular pistons arranged coaxially to the axis of rotation and mutually longitudinally displaceable , of which the first annular piston has an axial support on the cylinder drum and is longitudinally movable with respect to the drive shaft and the second annular piston has an axial support on the drive shaft and is longitudinally movable with respect to the cylinder drum.
  • the additional device has an effective direction directed away from the control surface.
  • the cylinder block which is pressed against the control surface by a compression spring and as a result of the pressure in the cylinder bores and the narrowing of the connecting openings, is thus relieved of pressure, which reduces the friction in the gap.
  • the resulting axial force corresponds to the spring force
  • the pressing effect of the compression spring is completely eliminated and only the force resulting from the pressure in the cylinder bores acts on the cylinder block and, in contrast, the hydrostatic relief force in the gap. If the relief pressure remains below a certain value, the full spring force acts on the cylinder drum, as a result of which higher speeds can be reached in this case without the cylinder drum tipping over.
  • the auxiliary device then expediently consists essentially of an annular piston arranged coaxially to the axis of rotation between a cylindrical outer surface of the drive shaft and a hollow cylindrical inner surface of the cylinder drum, which is longitudinally movable both with respect to the cylinder drum and with respect to the drive shaft and with a cylindrical outer surface in connection with a hollow cylindrical inner surface the cylinder drum forms at least one annular space, the annular piston having a first end position in the unpressurized state of the axial piston machine, in which a compression spring arranged between a hollow cylindrical inner surface of the annular piston and the cylindrical outer surface of the drive shaft has the greatest possible axial extent and the annular piston has a stop on the drive shaft abuts, and at a certain load on the axial piston machine, a second end position of the annular piston is provided, in which the compression spring r has the smallest possible axial extent, and the ring piston rests against a stop of the cylinder drum.
  • At least one connecting channel arranged in the cylinder drum is provided between the annular space and at least one of the control channels in the control surface. This can easily be introduced during the manufacture of the cylinder drum. The drive shaft itself then remains free of holes and grooves.
  • axial piston machines with a device for adjusting the delivery volume and reversing the flow direction, for example a swash plate type axial piston pump which can be pivoted on both sides
  • a device for adjusting the delivery volume and reversing the flow direction for example a swash plate type axial piston pump which can be pivoted on both sides
  • at least one annular space and at least one connecting channel are assigned to each flow direction.
  • the additional device can be used regardless of the direction of flow, so that the flow losses are reduced in both cases on the suction side and on the pressure side.
  • a plurality of connecting channels are spaced apart concentrically to the axis of rotation on a first pitch circle with approximately the same angular amount and for the second direction of flow a plurality of connecting channels are concentric to the axis of rotation on a second pitch circle with approximately the same angular amount are spaced from each other.
  • high pressure is applied to the annulus approximately uniformly.
  • an axial piston machine according to the invention in this example an axial piston machine in a swashplate construction, are shown with no representation of the housing and the effective surface of the piston and any adjustment devices.
  • a swash plate pump has a drive shaft 3 which is supported by two bearings 1 and 2 and which is penetrated centrally by a cylinder drum 4 and connected to it in a rotationally fixed manner.
  • the cylinder drum 4 is longitudinally movable relative to the drive shaft 1 within certain limits, which is achieved, for example, by spline teeth.
  • the axial section BB shown runs along the section line BB of an associated control surface 5 shown on the right side of FIG. 1. This in turn represents a section AA along the section line AA of the axial section BB shown on the left side of FIG. 1. This also applies to the remaining figures 2 to 4.
  • the end face of the cylinder drum 4 bears against the control surface 5 fixed to the housing and has a plurality of cylinder bores 6 in which pistons 7 are mounted so as to be longitudinally movable.
  • the cylinder bores 6 are arranged concentrically to the axis of rotation I of the swash plate pump.
  • the pistons 7 are connected to an active surface, not shown in the figure, which can be positioned at an angle to the axis of rotation.
  • the cylinder bores 6 are connected to control channels 9 and 10 of the control surface 5 by means of connection openings 8 in certain rotational positions of the cylinder drum 4.
  • the connecting openings 8 are smaller in cross section than the cylinder bores 6.
  • a compression spring 11 is provided, which in this example is inside the cylinder drum 4 in an annular cavity 12 between a cylindrical outer surface 13 Drive shaft 3 and a hollow cylindrical inner surface 14 of the cylinder drum 4 is arranged coaxially to the axis of rotation I.
  • the compression spring 11 is supported with its right end in the axial section via a first annular piston 15 and a locking ring 16 on the cylinder drum 4.
  • the annular piston 15 can also, as shown modified in the lower half of the axial section, be made in several parts, namely from two parts 151 and 152, of which the latter forms a radially inwardly directed contact collar 15a.
  • the annular piston 15 is opposite both the inner wall 14 of the cylinder drum 4 and the drive shaft 3 longitudinally movable, the longitudinal mobility with respect to the inner wall 14 of the cylinder drum 4 being restricted by the securing ring 16, and thereby touches with its cylindrical outer surface the hollow cylindrical inner surface 14 of the cylinder drum 4.
  • the annular cavity 12, in which the compression spring 11 is arranged, is located between the cylindrical outer surface 13 of the drive shaft 3 and the hollow cylindrical inner surface of the annular piston 15.
  • the cavity 12 is closed at one axial end by the contact collar 15a and at its opposite axial end by a second annular piston 17, which forms the abutment for the compression spring 11.
  • the annular piston 17 is also longitudinally movable both with respect to the hollow cylindrical inner surface 14 of the cylinder drum 4 and with respect to the drive shaft 3, the longitudinal mobility with respect to the drive shaft 3 being restricted by a collar 3a of the drive shaft 3. The compression spring 11 is thus clamped between the cylinder drum 4 and the drive shaft 3.
  • the second annular piston 17 has a radially outwardly directed collar 17a, the cylindrical outer surface of which rests on the hollow cylindrical inner surface 14 of the cylinder drum 4.
  • the first annular piston 15 forms, together with the second annular piston 17 and the hollow cylindrical inner surface 14 of the cylinder drum 4, an annular space 18 which can be connected to at least one of the control channels 9 via an essentially helical channel 19 and connecting channels 20 in the cylinder drum 4.
  • the control channels 9 are under load-dependent high pressure when the pump is running.
  • the connecting channels 20 are arranged concentrically to the axis of rotation on a common pitch circle.
  • the number of connection channels 20 is in principle arbitrary.
  • the number and the angular spacing are expediently chosen such that when the cylinder drum 4 rotates, at least one connecting channel 20 is always connected to a control channel 9.
  • a connection to the suction channel 10 of the control surface 5 is not provided in this figure, since the swash plate pump should only have one flow direction here.
  • the high-pressure pumped medium passes from the control channels 9 via the connecting channels 20 and the channel 19 into the annular space 18, where the aim is to move the annular pistons 15 and 17 away from one another.
  • an additional contact pressure is generated depending on the load, which presses the cylinder drum 4 against the control surface 5.
  • the additional device required for this consists only of the annular pistons 15 and 17, the channel 19 and the connecting channels 20.
  • Figure 2 differs from Figure 1 in that the swash plate pump is designed for operation with different flow directions, that is to say that the swash plate can be swiveled in two directions from the zero position and back again.
  • the additional device can also be effective on both sides, two annular spaces 181 and 182 are provided.
  • the annular space 181 is connected to connecting channels 20a and the annular space 182 to connecting channels 20b.
  • the connecting channels 20a are spaced apart from one another on a first inner pitch circle with approximately the same angular amount and are subjected to high pressure in a first flow direction.
  • the connecting channels 20b are spaced apart on a second outer pitch circle with approximately the same angular amount. If the direction of flow changes, the connecting channels 20b are under high pressure. Regardless of the direction of flow
  • One of the annular spaces 181 or 182 is therefore always subjected to high pressure depending on the load, so that the additional device is effective and presses the cylinder drum 4 against the control surface 5.
  • the variant according to FIG. 3 shows a swash plate pump with only one flow direction, in which, as a result of the design of the control channels 9 and 10 in the control surface 5, only three connecting channels 20 arranged at a distance of 120 ° on a pitch circle are necessary in order to apply the annular space 18 evenly to achieve with high pressure.
  • FIG. 4 shows a swash plate pump with two possible flow directions in which the additional device relieves the cylinder drum during operation.
  • a single step-shaped annular piston 251 is provided, which interacts with a stop part 252.
  • the annular piston 251 is longitudinally movable both with respect to the cylinder drum 4 and with respect to the drive shaft 3.
  • the compression spring 11 presses the annular piston 251 and the stop part 252 apart into a first end position, in which the annular piston 251 on the collar 3a of the drive shaft 3 abuts, the stop member 252 abuts the retaining ring 16 on the cylinder drum 4 and the compression spring 11 has the largest possible axial extent.
  • the gradation of the annular piston 251 enables the formation of two annular spaces 181 and 182, which can be acted upon by high pressure depending on the direction of flow of the medium.
  • the compression spring 11 is compressed with the aid of the annular piston 251 and separated from the collar 3a until the annular piston 251 bears against the stop part 252 in a second end position.
  • the compression spring 11 has the smallest possible axial extent in this position and cannot be compressed any further will. Although it is tense, it still does not act on the cylinder drum 4 in the sense of increasing the contact pressure on the control surface 5. Between the two end positions, the pressure-dependent pressure increase in one of the two annular spaces 181 or 182 continuously reduces or increases the pressure force of the compression spring 11.
EP90102354A 1989-02-17 1990-02-07 Moteur à pistons axiaux Expired - Lifetime EP0383167B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3904782A DE3904782A1 (de) 1989-02-17 1989-02-17 Axialkolbenmaschine
DE3904782 1989-02-17

Publications (2)

Publication Number Publication Date
EP0383167A1 true EP0383167A1 (fr) 1990-08-22
EP0383167B1 EP0383167B1 (fr) 1993-06-16

Family

ID=6374286

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90102354A Expired - Lifetime EP0383167B1 (fr) 1989-02-17 1990-02-07 Moteur à pistons axiaux

Country Status (5)

Country Link
US (1) US5079993A (fr)
EP (1) EP0383167B1 (fr)
JP (1) JP2960456B2 (fr)
DE (2) DE3904782A1 (fr)
ES (1) ES2043132T3 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4341845C2 (de) * 1993-12-08 1995-09-07 Danfoss As Hydraulischer Axialkolben-Motor
DE19855899B4 (de) * 1998-12-03 2010-09-16 Linde Material Handling Gmbh Axialkolbenmaschine
IT1308195B1 (it) * 1999-02-23 2001-12-10 Franco Castelmani Utensile per la troncatura di arbusti.
DE102011118622B4 (de) * 2011-11-16 2017-06-29 Mahle International Gmbh Axialkolbenmaschine mit Auslasssteuerung
DE102012110485A1 (de) 2012-11-02 2014-05-08 Linde Material Handling Gmbh Hydrostatische Axialkolbenmaschine
DE102020203450A1 (de) 2020-03-18 2021-09-23 Robert Bosch Gesellschaft mit beschränkter Haftung Axialkolbenmaschine mit gesteuerter Zylinderanpressung und mittels Regler verstellter Steuerblende
DE102020203445A1 (de) 2020-03-18 2021-09-23 Robert Bosch Gesellschaft mit beschränkter Haftung Axialkolbenmaschine mit gesteuerter Zylinderanpressung und Steuerdruckübergabe an der Steuerfläche

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU37131A1 (fr) *
CH334059A (de) * 1952-11-05 1958-11-15 Sundstrand Machine Tool Co Pumpe
WO1987001760A1 (fr) * 1985-09-23 1987-03-26 Sundstrand Corporation Ensemble a deplacement hydraulique et son procede de montage
WO1989006750A1 (fr) * 1988-01-16 1989-07-27 Michael Meyerle Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3110267A (en) * 1958-06-30 1963-11-12 Linde Eismaschinen Ag Axial piston pumps and motors with rotary cylinder blocks
US3292553A (en) * 1963-12-30 1966-12-20 Sunstrand Corp Piston return mechanism
US4475443A (en) * 1981-05-22 1984-10-09 Linde Aktiengesellschaft Axial piston machine with suction line impurity trap
JPS60500954A (ja) * 1983-04-04 1985-06-27 ヒユ−ズ・エアクラフト・カンパニ− Ｍｏｃｖｄ成長エピタキシヤル半導体層用のテトラメチルスズド−パント源
JPS6149175A (ja) * 1984-08-16 1986-03-11 Kayaba Ind Co Ltd 可変容量型油圧ポンプまたはモ−タの制御装置
DE3714888C2 (de) * 1987-05-05 1994-10-06 Linde Ag Einstellbare Axialkolbenmaschine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU37131A1 (fr) *
CH334059A (de) * 1952-11-05 1958-11-15 Sundstrand Machine Tool Co Pumpe
WO1987001760A1 (fr) * 1985-09-23 1987-03-26 Sundstrand Corporation Ensemble a deplacement hydraulique et son procede de montage
WO1989006750A1 (fr) * 1988-01-16 1989-07-27 Michael Meyerle Moteur hydrostatique a pistons axiaux, notamment pour boites de vitesses a derivation de puissance de vehicules a moteur

Also Published As

Publication number Publication date
ES2043132T3 (es) 1993-12-16
EP0383167B1 (fr) 1993-06-16
US5079993A (en) 1992-01-14
DE3904782A1 (de) 1990-08-23
JPH02264161A (ja) 1990-10-26
JP2960456B2 (ja) 1999-10-06
DE59001736D1 (de) 1993-07-22

Similar Documents

Publication Publication Date Title
DE3590198C2 (de) Ventilplatte für eine hydrostatische Axialkolbeneinheit
EP0162238B1 (fr) Machine à pistons axiaux, en particulier pompe du type à plateau incliné
EP0220175B1 (fr) Pompe hydraulique a pistons axiaux et a plateau oblique
DE3628479A1 (de) Mit einem druckmittel arbeitende, insbesondere hydraulische vorrichtung
EP0401408B1 (fr) Machine à pistons radiaux
DE4134219A1 (de) Zahnradpumpe mit veraenderbarem foerdervolumen
DE1804529A1 (de) Fluessigkeitsmotor oder Pumpe
EP0383167B1 (fr) Moteur à pistons axiaux
DE3209640A1 (de) Hydraulikpumpe
DE60036977T2 (de) Kraftübertragungsmechanismus
DE3441966A1 (de) Steuerung fuer einen hydrostatischen kolbenmotor
EP0509077B1 (fr) Pompe a pistons, notamment pompe a pistons radiaux
DE10044784A1 (de) Verstellvorrichtung für eine Axialkolbenmaschine in Schrägachsenbauweise
DE4340061A1 (de) Axialkolbenmaschine in Schrägscheibenbauart
DE19855899B4 (de) Axialkolbenmaschine
DE2134026A1 (de) Axialkolbenmaschine
DE2038086C3 (de) Axialkolbenmaschine
DE3041856C2 (de) Steuereinrichtung für ein hydrostatisches Getriebe
EP1700034B1 (fr) Machine a pistons axiaux pour realiser un acheminement independant dans plusieurs circuits hydrauliques
EP1671032B1 (fr) Machine a piston hydrostatique munie de deux circuits hydrauliques
DE102021200205A1 (de) Axialkolbenmaschine mit hoher Antriebdrehzahl
DE2163442B2 (de) Einrichtung zum verhindern des abhebens der umlaufenden zylindertrommel vom steuerspiegel einer axialkolbenmaschine
DE3725156C2 (fr)
EP0929743B1 (fr) Pompe a piston radial
EP0329208B1 (fr) Machine de nettoyage à haute pression entraînée hydrauliquement

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE ES FR GB

17P Request for examination filed

Effective date: 19900824

17Q First examination report despatched

Effective date: 19920110

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19930623

REF Corresponds to:

Ref document number: 59001736

Country of ref document: DE

Date of ref document: 19930722

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2043132

Country of ref document: ES

Kind code of ref document: T3

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000202

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20000210

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 20000222

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010207

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20010208

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20010207

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011031

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20020916

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20090428

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20100207

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59001736

Country of ref document: DE

Representative=s name: PATENTSHIP PATENTANWALTSGESELLSCHAFT MBH, DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59001736

Country of ref document: DE

Representative=s name: PATENTSHIP PATENTANWALTSGESELLSCHAFT MBH, DE