EP0471304B1 - Pendulum vehicle - Google Patents
Pendulum vehicle Download PDFInfo
- Publication number
- EP0471304B1 EP0471304B1 EP19910113381 EP91113381A EP0471304B1 EP 0471304 B1 EP0471304 B1 EP 0471304B1 EP 19910113381 EP19910113381 EP 19910113381 EP 91113381 A EP91113381 A EP 91113381A EP 0471304 B1 EP0471304 B1 EP 0471304B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- vehicle
- vehicle body
- point
- uncouple
- pendulum
- 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.)
- Expired - Lifetime
Links
Images
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
- B61F5/00—Constructional details of bogies; Connections between bogies and vehicle underframes; Arrangements or devices for adjusting or allowing self-adjustment of wheel axles or bogies when rounding curves
- B61F5/02—Arrangements permitting limited transverse relative movements between vehicle underframe or bolster and bogie; Connections between underframes and bogies
- B61F5/22—Guiding of the vehicle underframes with respect to the bogies
Definitions
- This invention relates to a pendulum vehicle, and in particular to structures for a railway vehicle having pendulum function.
- the pendulum vehicle is provided with the rollers and the swing bolster, which makes the structure of the vehicle comparatively complicated, resulting in worrisome maintenance work. Further, the structure with dusttight and dipproof functions is required for the rollers, which also brings about worrisome maintenance work.
- a pendulum vehicle comprises: a vehicle body; a plurality of trucks each having a truck frame provided below the vehicle body; and a pair of transversely arranged resilient members provided on the truck frame for supporting the vehicle body; wherein axes of the resilient members tilt so as to approach each other as height rises, and uncouple point, which is defined as a point where the vehicle body does not tilt but moves only horizontally in case that transverse load is applied to the point on the vehicle, is arranged at the position higher than the center of gravity of the vehicle.
- the truck frame supporting wheel axles is supported a vehicle body by means of resilient members such as air springs.
- the axles of the resilient members tilt so as to approach each other as height rises. Therefore, the point where the axles of the resilient members and the axle of the vehicle cross each other is positioned over the truck frame and the uncouple point is also formed over the truck frame.
- the uncouple point is designed so as to be positioned higher than the center of gravity of the vehicle body when transverse load because of centrifugal force is applied to the center of gravity of the vehicle body when passing through curves, the portion of the vehicle body which is lower than the uncouple point moves with displacement larger than the displacement at the uncouple point, causing the vehicle body to tilt inwardly, which permits pendulum function of the vehicle.
- FIG. 1 is a plan view of the pendulum vehicle according to one embodiment of the present invention and Fig.2 is a side view of the vehicle.
- a vehicle body 1 is supported by a pair of two-axle trucks 2 arranged at both ends of the vehicle. Between a pair of rails 3 along a service route on the ground is provided reaction plates constituting a linear motor. On the truck 2 is mounted coils 5 opposing to the reaction plates to get propulsion. Over the rails 3 is arranged a substantially H-shaped truck frame 6. Adjacent to a lateral mid-portion of side beams 7 of the truck frame 6 is installed air springs 9 as a pair of transversely arranged resilient members through supporting members 8, which support the vehicle body 1.
- FIG 3 is a front view of the truck 2 and Fig. 4 shows a cross-section taken along the line IV-IV of Fig. 2.
- Figure 5 shows a cross-section of the portion adjacent to wheels 10a.
- the wheels 10a are fixed to axles 11, which are supported on bearings 12 in cylindrical bearing boxes 13a adjacent to the wheels 10a.
- a shaft 14a projecting upward.
- the shaft 14a is rotatably mounted in a supporting hole 16 which is formed on a mounting member 15.
- To the mounting member 15 is fixed the reaction plate 5.
- the side beam 7 of the truck frame 6 is supported by abrasion plate or resilient member 17a such as springs which is positioned between the beam and the bearing box 13a in the vicinity of the bearing 12.
- Another wheel 10b has the same structure as the wheel 10a and the portions of the wheel 10b corresponding to those of the wheel 10a are described by the same reference number with a subscript b.
- Propulsion which is applied to the coil 5 on the vehicle, is transmitted to the truck frame 6 via a propulsion transmitting means 18, and is further transmitted to the vehicle body 1 via a propulsion transmitting link device 50.
- the propulsion transmitting link device 50 comprises links 19a and 19b, a tracking beam 20, and a center pin 21. When the vehicle body does not move laterally, vertical axis of the center pin 21 substantially corresponds to the center of the truck.
- At both ends of the link 19a are arranged spherical bearings or resilient members.
- One end of the link 19a is rotatably connected to a front side-beam 6a and the other end is to the right side of the tracking beam 20 of the truck frame 6 by means of spherical bearings or resilient members.
- One end of the link 19b is also rotatably connected to a rear side-beam 6b and the other end is to the left side of the tracking beam 20 of the truck frame in the same manner as the link 19a.
- Both links 19a and 19b are arranged so as to be parallel to each other.
- propulsion transmitting link device 50 By virtue of the propulsion transmitting link device 50 of the structure described above, propulsion, braking force or the like is transmitted in the longitudinal direction between the vehicle body 1 and truck frame 6 while permitting relative transverse disposition and rotation between them.
- Figure 6 is a diagrammatic illustration showing the arrangement of the air springs 9 and others.
- the axes 26 of the pair of air springs 9 tilt in the same vertical plane so that the axes approach to each other to cross at intersection 27 as height rises under the condition that the vehicle passes through horizontally liner truck.
- This intersection 27 is the geometrical center of the air spring in the direction of the axis of the air spring.
- the center of gravity of the vehicle body is located in the vicinity of the perpendicular bisector 29 of the line 28 passing through the centers of the pair of air springs 9.
- the uncouple point 30, which corresponds to the center of oscillation of this pendulum vehicle, is on the perpendicular bisector 29.
- the vehicle body 1 moves only horizontally and does not tilt.
- This transverse load comprises centrifugal force and the like, which acts on a vehicle when passing through curves.
- the uncouple point is designed so as to be higher than the center of gravity of the vehicle body 1.
- the height C of the uncouple point 30, that is, the distance between the point 30 and the line 28 is determined by formula 4.
- C ( 1 - Kl Kr ) cot ⁇ 1 + Kl Kr cot2 ⁇ ⁇ B
- the spring constant Kx described above is determined so as to have around 1 Hz of characteristic frequency of the vehicle body, as an example.
- the transverse spring constant Kl of the air spring 9 is selected so as to be comparatively small.
- the axial spring constant Kr is determined in such a manner that the spring constant Kx as described above is to be obtained.
- the air spring 9 described above is realized with the structure in which a pair of substantially flat supporting plates 32 and 33 are provided on upper and lower surfaces of air-filled bag 31 with resiliency by rubber or the like, and auxiliary air chamber 36.
- the structure permits the air spring 9 to have the axial spring constant Kr and the transverse spring constant Kl thereof with the following relation with ease. Kr > Kl
- the transverse load because of the centrifugal force described above acts on the center of gravity of the vehicle body 1. Since the uncouple point is positioned higher than the center of gravity of the vehicle body 1, when transverse load acts on the vehicle when passing through curves, the vehicle body tilts inwardly with respect to the uncouple point 30, which can reduce transverse acceleration felt by passengers by the pendulum function.
- springs 9a may be used in place of the air springs 9a.
- the springs 9a are formed by accumulating a plurality of resilient pieces 34 made of thin rubber or the like and interposing stiff flat plates 35 such as steel plates each between the resilient pieces.
Description
- This invention relates to a pendulum vehicle, and in particular to structures for a railway vehicle having pendulum function.
- An example of a typical prior art is disclosed in Japanese Patent Laid-Open Showa 59-143760. In the prior art, on a truck frame is provided a rotating beam which can rotate about the axis of a center pin. On the rotating beam is mounted a swing bolster by means of rollers arranged at both ends of the beam. Further, on the swing beam is supported a vehicle body by air springs.
- In the prior art described above, the pendulum vehicle is provided with the rollers and the swing bolster, which makes the structure of the vehicle comparatively complicated, resulting in worrisome maintenance work. Further, the structure with dusttight and dipproof functions is required for the rollers, which also brings about worrisome maintenance work.
- It is therefore the object of the present invention to provide a pendulum vehicle in which the structure and the maintenance work are simplified, and comfortable drive is guaranteed.
- A pendulum vehicle according to the present invention comprises: a vehicle body; a plurality of trucks each having a truck frame provided below the vehicle body; and a pair of transversely arranged resilient members provided on the truck frame for supporting the vehicle body; wherein axes of the resilient members tilt so as to approach each other as height rises, and uncouple point, which is defined as a point where the vehicle body does not tilt but moves only horizontally in case that transverse load is applied to the point on the vehicle, is arranged at the position higher than the center of gravity of the vehicle.
- When transverse load is applied to the point higher than the uncouple point, the portion on the vehicle which is higher than the uncouple point will tilt with displacement larger than the displacement at the uncouple point. On the other hand, when the transverse load is applied to the point lower than the uncouple point, the portion on the vehicle which is lower than the uncouple point will tilt with displacement larger than the displacement at the uncouple point.
- In the present invention, on the truck frame supporting wheel axles is supported a vehicle body by means of resilient members such as air springs. The axles of the resilient members tilt so as to approach each other as height rises. Therefore, the point where the axles of the resilient members and the axle of the vehicle cross each other is positioned over the truck frame and the uncouple point is also formed over the truck frame.
- In the present invention, since the uncouple point is designed so as to be positioned higher than the center of gravity of the vehicle body when transverse load because of centrifugal force is applied to the center of gravity of the vehicle body when passing through curves, the portion of the vehicle body which is lower than the uncouple point moves with displacement larger than the displacement at the uncouple point, causing the vehicle body to tilt inwardly, which permits pendulum function of the vehicle.
- The present invention will be more apparent from the ensuring description with reference to the accompanying drawing wherein:
- Figure 1 is a plan view showing one embodiment of the present invention;
- Figure 2 is a side view showing the embodiment of Fig. 1;
- Figure 3 is a front view of the
truck 2; - Figure 4 shows the cross section taken along the line IV-IV of Fig. 2;
- Figure 5 shows the cross section adjacent to the
wheel 10a; - Figure 6 is a diagrammatic illustration showing the configuration of the
air springs 9; - Figures 7A and 7B are drawings to explain spring constants of the
air springs 9; - Figure 8 is a drawing briefly illustrating the structure of the
air springs 9; and - Figure 9 is a drawing briefly showing the structure of the
resilient member 9a according to another embodiment of the present invention. - A preferred embodiment of a pendulum vehicle according to the present invention will now be described with reference to drawings.
- Figure 1 is a plan view of the pendulum vehicle according to one embodiment of the present invention and Fig.2 is a side view of the vehicle. In a railway vehicle in accordance with the present invention, a vehicle body 1 is supported by a pair of two-
axle trucks 2 arranged at both ends of the vehicle. Between a pair ofrails 3 along a service route on the ground is provided reaction plates constituting a linear motor. On thetruck 2 is mountedcoils 5 opposing to the reaction plates to get propulsion. Over therails 3 is arranged a substantially H-shaped truck frame 6. Adjacent to a lateral mid-portion ofside beams 7 of thetruck frame 6 is installedair springs 9 as a pair of transversely arranged resilient members through supportingmembers 8, which support the vehicle body 1. - Figure 3 is a front view of the
truck 2 and Fig. 4 shows a cross-section taken along the line IV-IV of Fig. 2. Figure 5 shows a cross-section of the portion adjacent towheels 10a. Thewheels 10a are fixed toaxles 11, which are supported on bearings 12 incylindrical bearing boxes 13a adjacent to thewheels 10a. At the axial mid-portion of the bearingbody 13a is formed ashaft 14a projecting upward. Theshaft 14a is rotatably mounted in a supportinghole 16 which is formed on amounting member 15. To the mountingmember 15 is fixed thereaction plate 5. Theside beam 7 of thetruck frame 6 is supported by abrasion plate orresilient member 17a such as springs which is positioned between the beam and thebearing box 13a in the vicinity of the bearing 12. Anotherwheel 10b has the same structure as thewheel 10a and the portions of thewheel 10b corresponding to those of thewheel 10a are described by the same reference number with a subscript b. Propulsion, which is applied to thecoil 5 on the vehicle, is transmitted to thetruck frame 6 via apropulsion transmitting means 18, and is further transmitted to the vehicle body 1 via a propulsion transmittinglink device 50. The propulsion transmittinglink device 50 compriseslinks tracking beam 20, and acenter pin 21. When the vehicle body does not move laterally, vertical axis of thecenter pin 21 substantially corresponds to the center of the truck. At both ends of thelink 19a are arranged spherical bearings or resilient members. One end of thelink 19a is rotatably connected to a front side-beam 6a and the other end is to the right side of thetracking beam 20 of thetruck frame 6 by means of spherical bearings or resilient members. One end of thelink 19b is also rotatably connected to a rear side-beam 6b and the other end is to the left side of thetracking beam 20 of the truck frame in the same manner as thelink 19a. Bothlinks center pin 21, which is positioned at the middle of thelinks tracking beam 20, rotatably connects the vehicle body 1 to thetracking beam 20 about thevertical axis 23 of thecenter pin 21. - By virtue of the propulsion transmitting
link device 50 of the structure described above, propulsion, braking force or the like is transmitted in the longitudinal direction between the vehicle body 1 andtruck frame 6 while permitting relative transverse disposition and rotation between them. - Figure 6 is a diagrammatic illustration showing the arrangement of the
air springs 9 and others. Theaxes 26 of the pair ofair springs 9 tilt in the same vertical plane so that the axes approach to each other to cross atintersection 27 as height rises under the condition that the vehicle passes through horizontally liner truck. Thisintersection 27 is the geometrical center of the air spring in the direction of the axis of the air spring. The center of gravity of the vehicle body is located in the vicinity of theperpendicular bisector 29 of theline 28 passing through the centers of the pair ofair springs 9. Theuncouple point 30, which corresponds to the center of oscillation of this pendulum vehicle, is on theperpendicular bisector 29. Even when load P as a transverse load is applied to theuncouple point 30, the vehicle body 1 moves only horizontally and does not tilt. This transverse load comprises centrifugal force and the like, which acts on a vehicle when passing through curves. In the present invention, the uncouple point is designed so as to be higher than the center of gravity of the vehicle body 1. - Referring to Figs. 7A and 7B, where spring constant of the
air spring 9 in the direction of theaxis 26 is defined as Kr and that of thespring 9 in the direction perpendicular to theaxis 26 is defined as Kl, and further, spring constant of theair spring 9 in the direction parallel to theperpendicular bisector 29 is determined as Kx and that of the spring in the direction parallel to theline 28 is Ky, the following formula holds. In the formula, the distance between theline 28 and theintersection 27 is H1; the distance between the centers of the pair of air springs is 2B; and the angle between theaxis 26 and theperpendicular bisector 29 is α. -
- The spring constant Kx described above is determined so as to have around 1 Hz of characteristic frequency of the vehicle body, as an example. The transverse spring constant Kl of the
air spring 9 is selected so as to be comparatively small. Further, the axial spring constant Kr is determined in such a manner that the spring constant Kx as described above is to be obtained. - As shown in Fig. 8, the
air spring 9 described above is realized with the structure in which a pair of substantially flat supportingplates bag 31 with resiliency by rubber or the like, andauxiliary air chamber 36. The structure permits theair spring 9 to have the axial spring constant Kr and the transverse spring constant Kl thereof with the following relation with ease. - The transverse load because of the centrifugal force described above acts on the center of gravity of the vehicle body 1. Since the uncouple point is positioned higher than the center of gravity of the vehicle body 1, when transverse load acts on the vehicle when passing through curves, the vehicle body tilts inwardly with respect to the
uncouple point 30, which can reduce transverse acceleration felt by passengers by the pendulum function. - As another embodiment of the present invention, springs 9a may be used in place of the air springs 9a. The
springs 9a are formed by accumulating a plurality ofresilient pieces 34 made of thin rubber or the like and interposing stiffflat plates 35 such as steel plates each between the resilient pieces. - Other structure may be applied to attain the object instead of the air springs 9 and the resilient members shown in Fig. 9.
- In the present invention as described above, since a pair of transversely arranged resilient members, of which axes tilt so as to approach each other as height rises, support a vehicle body on a truck frame and uncouple point formed by the above structure is designed in such a manner as to be higher than the center of gravity of the vehicle body, pendulum function of the vehicle body is obtained without rollers and a swing bolster disclosed in the prior art. Therefore, the structure and maintenance work are simplified. Further, stationary transverse acceleration felt by passengers when passing through curves can be reduced to achieve comfortable drive, which improves the vehicle speed on a curved track.
Claims (3)
- A pendulum vehicle comprising:
vehicle body (1);
a plurality of trucks (2) each having a truck frame (6) provided below said vehicle body; and
a pair of transversely arranged resilient members (9) provided on said truck frame (6) for supporting said vehicle body (1); wherein axes (26) of the resilient members (9) tilt so as to approach each other as height rises, and an uncouple point (30) of the vehicle is positioned higher than center of gravity (G) of the vehicle body. - A pendulum vehicle as claimed in claim 1, wherein said pair of resilient members (9) include air springs.
- A pendulum vehicle as claimed in claim 1, wherein said pair of resilient members (9) include springs formed by accumulating a plurality of resilient pieces (34) made of thin rubber and interposing stiff flat plates (35) made of steel plates each between the resilient pieces.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP214652/90 | 1990-08-13 | ||
JP2214652A JP2870603B2 (en) | 1990-08-13 | 1990-08-13 | Railway pendulum vehicle |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0471304A1 EP0471304A1 (en) | 1992-02-19 |
EP0471304B1 true EP0471304B1 (en) | 1994-03-02 |
Family
ID=16659314
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19910113381 Expired - Lifetime EP0471304B1 (en) | 1990-08-13 | 1991-08-09 | Pendulum vehicle |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0471304B1 (en) |
JP (1) | JP2870603B2 (en) |
CA (1) | CA2048889A1 (en) |
DE (1) | DE69101290T2 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT406570B (en) * | 1998-01-16 | 2000-06-26 | Siemens Ag Oesterreich | BOG FOR A TILTABLE RAIL VEHICLE |
CN107697091B (en) * | 2017-09-27 | 2019-12-27 | 中车长春轨道客车股份有限公司 | Compact bogie with built-in axle box for metro vehicle |
CN109484424A (en) * | 2018-11-19 | 2019-03-19 | 中车长春轨道客车股份有限公司 | A kind of independent wheel bogie of linear motor driving |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2225242A (en) * | 1938-03-07 | 1940-12-17 | Pacific Railway Equipment Comp | Suspension system for vehicles |
US2910014A (en) * | 1956-03-16 | 1959-10-27 | Pullman Standard Car Mfg Co | Suspension system saddle support |
GB962822A (en) * | 1960-12-22 | 1964-07-01 | Ernst Florian Kreissig | Improvements in or relating to a vehicle and suspension system thereof |
JPS4827510U (en) * | 1971-08-11 | 1973-04-03 | ||
ES424615A1 (en) * | 1974-03-25 | 1976-06-01 | Talgo Patentes | Train having a pendular suspension system |
US4368672A (en) * | 1980-12-29 | 1983-01-18 | The Budd Company | Secondary suspension system for a railway car |
-
1990
- 1990-08-13 JP JP2214652A patent/JP2870603B2/en not_active Expired - Fee Related
-
1991
- 1991-08-09 DE DE1991601290 patent/DE69101290T2/en not_active Expired - Fee Related
- 1991-08-09 CA CA 2048889 patent/CA2048889A1/en not_active Abandoned
- 1991-08-09 EP EP19910113381 patent/EP0471304B1/en not_active Expired - Lifetime
Also Published As
Publication number | Publication date |
---|---|
JP2870603B2 (en) | 1999-03-17 |
EP0471304A1 (en) | 1992-02-19 |
CA2048889A1 (en) | 1992-02-14 |
JPH0495564A (en) | 1992-03-27 |
DE69101290T2 (en) | 1994-06-09 |
DE69101290D1 (en) | 1994-04-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US5415107A (en) | Running gear for drop-frame rail vehicles | |
US3888187A (en) | Dampened axle bearing mounting | |
JP2866718B2 (en) | Hinge bogies for railway vehicles | |
CA1235607A (en) | Steerable truck for railway vehicle | |
WO2001034996A1 (en) | Vehicle suspension system | |
US5001989A (en) | Single axle suspension system for railway car truck | |
US3807313A (en) | Linear motor-driven railway truck | |
US3782294A (en) | Articulated railway truck swinging bolster | |
US4760799A (en) | Lightweight railway vehicle truck | |
EP0471304B1 (en) | Pendulum vehicle | |
US1813140A (en) | Railway motor suspension | |
US3515405A (en) | Axle suspension system for transit vehicles | |
JP3498258B2 (en) | 2-axle bogie for railway vehicles | |
AU716083B2 (en) | Rail vehicle with a driving unit and a wagon | |
JP3919434B2 (en) | Body support mechanism of single-shaft bogie, railcar bogie using the same, and railcar using the bogie | |
US4625653A (en) | High adhesion railway power truck with body spring-supported on the truck structure | |
JPS61211159A (en) | Meandering preventive device for railway rolling stock | |
US3244118A (en) | Rapid transit trucks | |
JPH09301163A (en) | Bolsterless truck for rolling stock | |
JPH04339072A (en) | Pendulum truck for rolling stock | |
JPS59230859A (en) | Truck for railway rolling stock | |
JPS58145565A (en) | Linear-motor propulsive truck | |
WO1991013786A1 (en) | Suspension system | |
JPS59106360A (en) | Driving truck of linear motor | |
JPS5814140Y2 (en) | Bearing support device for railway vehicle bogies |
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 FR GB |
|
17P | Request for examination filed |
Effective date: 19920414 |
|
17Q | First examination report despatched |
Effective date: 19930602 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: KAWASAKI JUKOGYO KABUSHIKI KAISHA |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB |
|
REF | Corresponds to: |
Ref document number: 69101290 Country of ref document: DE Date of ref document: 19940407 |
|
ET | Fr: translation filed | ||
PLBI | Opposition filed |
Free format text: ORIGINAL CODE: 0009260 |
|
26 | Opposition filed |
Opponent name: GEC ALSTHOM SA Effective date: 19941201 |
|
PLBL | Opposition procedure terminated |
Free format text: ORIGINAL CODE: EPIDOS OPPC |
|
PLBM | Termination of opposition procedure: date of legal effect published |
Free format text: ORIGINAL CODE: 0009276 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: OPPOSITION PROCEDURE CLOSED |
|
27C | Opposition proceedings terminated |
Effective date: 19970505 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20060803 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20060808 Year of fee payment: 16 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20060809 Year of fee payment: 16 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20070809 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20080430 |
|
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 NON-PAYMENT OF DUE FEES Effective date: 20080301 |
|
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: 20070831 |
|
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: 20070809 |