EP0428374B1 - Positive displacement pump systems - Google Patents
Positive displacement pump systems Download PDFInfo
- Publication number
- EP0428374B1 EP0428374B1 EP19900312361 EP90312361A EP0428374B1 EP 0428374 B1 EP0428374 B1 EP 0428374B1 EP 19900312361 EP19900312361 EP 19900312361 EP 90312361 A EP90312361 A EP 90312361A EP 0428374 B1 EP0428374 B1 EP 0428374B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- overspill
- bore
- land
- valve member
- 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
-
- 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
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
-
- 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
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/06—Control
- F04B1/063—Control by using a valve in a system with several pumping chambers wherein the flow-path through the chambers can be changed, e.g. between series and parallel flow
-
- 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
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
- F04B49/24—Bypassing
-
- 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
- F04C2/3447—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 the vanes having the form of rollers, slippers or the like
Definitions
- This invention relates to positive displacement pump systems and is more particularly concerned with such systems in which deliveries from two positive displacement pump sources are available to be fed to a common supply passage.
- a positive displacement pump system having first and second delivery passages for pumped fluid, a main discharge passage connected to receive a flow from the first delivery passage and to receive through a non-return valve a flow from the second delivery passage, a control orifice disposed in the main discharge passage at a location to receive the combined said flows, and a control valve for apportioning the flow from the second delivery passage between the main discharge passage and overspill porting and controlling the by-passing of a proportion of the flow from the first delivery passage through the overspill porting, said control valve comprising a valve member slidably mounted in a bore in a valve body, one end of which bore is in communication with the main discharge passage at a location upstream of said control orifice, a spring which is disposed in a spring chamber in the valve body and which urges the valve member towards said one end of the bore, said spring chamber communicating with the main discharge passage at a location downstream of the control orifice, said valve member having a first metering land between
- the overspill porting comprises an annular overspill port extending about the valve bore, and the edge of the overspill port nearer the first land and the end of the first land nearer said one end of the valve bore are so shaped in relation to each other that on movement of the valve member against the spring loading, the communication between the by-pass port and said one end of the valve bore is, initially at least, less than fully annular as the valve member moves against the spring loading.
- the progressive increase in the area of communication towards fully annular communication in these constructions may be achieved by providing peripheral notches in the said end face of the first and/or the second land or otherwise making the periphery of such end face non-circular. Alternatively notches may be cut in axial end edge of the port.
- the system comprises a positive displacement pump 10 and in this instance of the well-known roller type and has two inlet ports 12, 13 and two outlet ports 14, 15 from which the pumped fluid flows into first and second delivery passages 16, 17 respectively.
- the downstream end of delivery passage 16 is in direct communication with the upstream end of a main discharge passage 18.
- the downstream end of the second delivery passage 17 communicates with the discharge passage 18 through a non-return valve 19.
- a discharge orifice 20 is provided in the discharge passage 18.
- the control valve 11 comprises a spool valve member 22 slidably mounted in a bore 24 in a body part 26.
- One end of the bore 24 opens to the main discharge passage 18 upstream of the orifice 20.
- the other end of the bore forms a chamber 27 housing a spring 28 which urges the valve member into abutment with a wall of the main discharge passage 18.
- the chamber 27 communicates through a duct 25 with the passage 18 at a location downstream of the orifice 20 so that the pressure drop across the orifice opposes the force of the spring 28.
- the valve member has first and second lands 29, 30 of which, in the position shown in Figure 1, the former is disposed between the main discharge passage and an annular overspill port 31 in the bore 24. Port 31 communicates through a passage 32 with a passage 33 leading to the inlet port 12. Land 30 is axially spaced from land 29 and, in the position shown in Figure 1, obstructs an annular by-pass port 34 which is in communication with the second delivery passage 17 at a location upstream of the non-return valve 19.
- the lands 29,30 have in the periphery of their end portions nearer the main discharge passage a number of notches 35, 36 respectively opening to the end face.
- Figure 1 shows the valve in its position in low-speed operation of the pump.
- the pressure in the main discharge passage is low, and the lands 29 and 30 respectively prevent communication between the discharge passage 18 and the by-pass port 34 respectively and the overspill port 31, so that the whole flow from the second outlet port 15 flows through the non-return valve 19 and joins the flow from the first outlet port 14 in the main discharge passage leading to the point of utilisation.
- the pump speed increases, assuming for the moment that the pressure at the downstream side of orifice 20 remains constant, the increase in pressure at the upstream side of the orifice urges the valve member to move against the spring force as shown in Figure 2.
- valve member causes a sharp fall in the pressure in the second delivery passage 17 and a consequent reduction in the power requirement of the pump. Further increases in pump speed move the valve member further rightward permitting increased flow of fluid from the first delivery passage to pass through notches 35 to the overspill port 34.
- the two lands 29, 30 of the valve member have fully planar end faces and notches 37, 38 are instead formed in the axial end faces 31b, 34b of the ports 31, 34 which co-operate with the lands in controlling the opening of the ports.
- the notches 37, 38 operate in conjunction with the ends of the lands 29, 30 in exactly the same way as the notches 35, 36 operate in conjunction with the edges 31a of the ports in the arrangement of Figure 1.
- the orifice 20 operates to maintain a constant flow to the point of utilisation, and if at any stage of operation, the pressure downstream of the orifice 20 falls, the resulting drop in pressure in chamber 27 causes the valve member to move to increase the amount of fluid passed to the overspill port. Conversely if the pressure downstream of orifice 20 rises, the resulting rise in pressure in chamber 27 causes the valve member to move to reduce the amount of fluid passed to the overspill port.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
- Details Of Reciprocating Pumps (AREA)
Description
- This invention relates to positive displacement pump systems and is more particularly concerned with such systems in which deliveries from two positive displacement pump sources are available to be fed to a common supply passage.
- According to this invention there is provided a positive displacement pump system having first and second delivery passages for pumped fluid, a main discharge passage connected to receive a flow from the first delivery passage and to receive through a non-return valve a flow from the second delivery passage, a control orifice disposed in the main discharge passage at a location to receive the combined said flows, and a control valve for apportioning the flow from the second delivery passage between the main discharge passage and overspill porting and controlling the by-passing of a proportion of the flow from the first delivery passage through the overspill porting, said control valve comprising a valve member slidably mounted in a bore in a valve body, one end of which bore is in communication with the main discharge passage at a location upstream of said control orifice, a spring which is disposed in a spring chamber in the valve body and which urges the valve member towards said one end of the bore, said spring chamber communicating with the main discharge passage at a location downstream of the control orifice, said valve member having a first metering land between said one end of the valve bore and the overspill porting, and a second metering land disposed between the spring chamber and the overspill porting, and the valve body having an annular by-pass port variably obstructed by the second land and connected to the second delivery passage at a location upstream of said non-return valve, the by-pass port and the axial end portion of the second land nearer the overspill porting being so shaped in relation to each other that on movement of the valve member against the spring loading, the communication between the by-pass port and the space in the valve bore at the axial side of the second land nearer said one end of the valve bore is initially at least, less than fully annular as the valve member moves against the spring loading.
- According to a preferred feature of the invention, the overspill porting comprises an annular overspill port extending about the valve bore, and the edge of the overspill port nearer the first land and the end of the first land nearer said one end of the valve bore are so shaped in relation to each other that on movement of the valve member against the spring loading, the communication between the by-pass port and said one end of the valve bore is, initially at least, less than fully annular as the valve member moves against the spring loading.
- The progressive increase in the area of communication towards fully annular communication in these constructions may be achieved by providing peripheral notches in the said end face of the first and/or the second land or otherwise making the periphery of such end face non-circular. Alternatively notches may be cut in axial end edge of the port.
- The invention will now be described in more detail with reference by way of example to the accompanying diagrammatic drawings in which:
- Figure 1 shows a positive displacement pump system according to the invention in a low-speed condition,
- Figures 2 and 3 respectively show the control valve of the system of Figure 1 in medium speed and high speed conditions respectively,
- Figure 4 illustrates a modified arrangement of the control valve, and
- Figures 5 and 6 are respectively fragmentary sectional end views on the lines 5-5 and 6-6 of Figure 4.
- Referring first to Figure 1 the system comprises a
positive displacement pump 10 and in this instance of the well-known roller type and has twoinlet ports outlet ports second delivery passages delivery passage 16 is in direct communication with the upstream end of amain discharge passage 18. The downstream end of thesecond delivery passage 17 communicates with thedischarge passage 18 through anon-return valve 19. Adischarge orifice 20 is provided in thedischarge passage 18. - The
control valve 11 comprises aspool valve member 22 slidably mounted in abore 24 in a body part 26. One end of thebore 24 opens to themain discharge passage 18 upstream of theorifice 20. The other end of the bore forms achamber 27 housing aspring 28 which urges the valve member into abutment with a wall of themain discharge passage 18. Thechamber 27 communicates through aduct 25 with thepassage 18 at a location downstream of theorifice 20 so that the pressure drop across the orifice opposes the force of thespring 28. - The valve member has first and
second lands annular overspill port 31 in thebore 24.Port 31 communicates through apassage 32 with apassage 33 leading to theinlet port 12.Land 30 is axially spaced fromland 29 and, in the position shown in Figure 1, obstructs an annular by-pass port 34 which is in communication with thesecond delivery passage 17 at a location upstream of thenon-return valve 19. Thelands notches - Figure 1 shows the valve in its position in low-speed operation of the pump. The pressure in the main discharge passage is low, and the
lands discharge passage 18 and the by-pass port 34 respectively and theoverspill port 31, so that the whole flow from thesecond outlet port 15 flows through thenon-return valve 19 and joins the flow from thefirst outlet port 14 in the main discharge passage leading to the point of utilisation. As the pump speed increases, assuming for the moment that the pressure at the downstream side oforifice 20 remains constant, the increase in pressure at the upstream side of the orifice urges the valve member to move against the spring force as shown in Figure 2. As thenotches 36 in the end portion of the second land pass thecircular edge 34a of theport 34, a flow of fluid through the port to theoverspill port 31 occurs which is less than if there were fully annular communication between the port and the bore, so that the flow to the overspill is not greatly affected by ie is less sensitive to, small movements of the valve member on initial opening. An increasing proportion of the flow from thesecond delivery port 15 is by-passed through theoverspill port 34, as the pump speed increases. As the valve member moves rightward the area of communication increases to the position where the plane of the end face passes theedge 34a of theport 34 and communication is then fully annular. - Up to this point the
non-return valve 19 has remained open but at their maximum opening thenotches 36 are capable of passing to theoverspill port 31 the entire flow from thesecond delivery passage 17 and when the end face ofland 30 moves past theedge 34a, the resulting fall in pressure in the second delivery passage tends to produce a reverse flow through the non-return valve, which causes thevalve 19 to close. The next increase in the pump speed causes a sudden and substantial rightward movement of the valve member, which movesnotches 35 to a point relative to theedge 31a ofoverspill port 31 at which the fresh excess of fluid can pass to the overspill port through thenotches 35, see Figure 3. This rightward movement of the valve member causes a sharp fall in the pressure in thesecond delivery passage 17 and a consequent reduction in the power requirement of the pump. Further increases in pump speed move the valve member further rightward permitting increased flow of fluid from the first delivery passage to pass throughnotches 35 to theoverspill port 34. - Thus, with progressively increasing pump speed, all of the fluid delivered to the second delivery passage is passed at low pressure through the overspill port, and an increasing proportion of the fluid delivered to the first delivery passage is also passed through the overspill port
- In an alternative arrangement illustrated in Figures 4 to 6, the two
lands notches axial end faces ports notches lands notches edges 31a of the ports in the arrangement of Figure 1. - The
orifice 20 operates to maintain a constant flow to the point of utilisation, and if at any stage of operation, the pressure downstream of theorifice 20 falls, the resulting drop in pressure inchamber 27 causes the valve member to move to increase the amount of fluid passed to the overspill port. Conversely if the pressure downstream oforifice 20 rises, the resulting rise in pressure inchamber 27 causes the valve member to move to reduce the amount of fluid passed to the overspill port.
Claims (5)
- A positive displacement pump system having first and second delivery passages for pumped fluid, a main discharge passage connected to receive a flow from the first delivery passage and to receive through a non- return valve a flow from the second delivery passage, a control orifice disposed in the main discharge passage at a location to receive the combined said flows, and a control valve for apportioning the flow from the second delivery passage between the main discharge passage and overspill porting and controlling the by-passing of a proportion of the flow from the first delivery passage through the overspill porting, said control valve comprising a valve member slidably mounted in a bore in a valve body, one end of which bore is in communication with the main discharge passage at a location upstream of said control orifice, a spring which is disposed in a spring chamber in the valve body and which urges the valve member towards said one end of the bore, said spring chamber communicating with the main discharge passage at a location downstream of the control orifice, said valve member having a first metering land between said one end of the valve bore and the overspill porting, and a second metering land disposed between the spring chamber and the overspill porting, and the valve body having an annular by-pass port variably obstructed by the second land and connected to the second delivery passage at a location upstream of said non-return valve, the by-pass port and the axial end portion of the second land nearer the overspill porting being so shaped in relation to each other that on movement of the valve member against the spring loading, the communication between the by-pass port and the space in the valve bore at the axial side of the second land nearer said one end of the valve bore is initially at least, less than fully annular as the valve member moves against the spring loading.
- A pump system as claimed in claim 1, wherein the overspill porting comprises an annular overspill port extending about the valve bore, and the edge of the overspill port nearer the first land and the end of the first land nearer said one end of the valve bore are so shaped in relation to each other that on movement of the valve member against the spring loading, the communication between the by-pass port and said one end of the valve bore is, initially at least, less than fully annular as the valve member moves against the spring loading.
- A pump system as claimed in claim 2, wherein the peripheries of the said end faces of the first and second lands are non-circular.
- A pump system as claimed in claim 3, wherein peripheral notches are formed in the said end face of the first and/or second land.
- A pump system as claimed in claim 2, wherein the notches are formed in the axial end expel of the overspill part and the by-pass part which co-operate with the respective lands.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
GB898925592A GB8925592D0 (en) | 1989-11-13 | 1989-11-13 | Positive displacement pump systems |
GB8925592 | 1989-11-13 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0428374A1 EP0428374A1 (en) | 1991-05-22 |
EP0428374B1 true EP0428374B1 (en) | 1994-07-13 |
Family
ID=10666206
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19900312361 Expired - Lifetime EP0428374B1 (en) | 1989-11-13 | 1990-11-13 | Positive displacement pump systems |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0428374B1 (en) |
DE (1) | DE69010631T2 (en) |
GB (1) | GB8925592D0 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2320955B (en) | 1997-01-03 | 1999-08-04 | Hobourn Automotive Ltd | Flow control valve |
DE69915436T2 (en) | 1998-12-11 | 2004-07-22 | Dana Automotive Ltd., Rochester | Displacement pump systems |
US6641372B2 (en) * | 2000-01-21 | 2003-11-04 | Delphi Technologies, Inc. | Dual discharge hydraulic pump and system therefor |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2074618A (en) * | 1934-08-01 | 1937-03-23 | Clyde A Roeder | Pumping system |
US2192512A (en) * | 1937-01-07 | 1940-03-05 | F E Twiss Co Inc | Pump |
GB681625A (en) * | 1950-05-03 | 1952-10-29 | Hobson Ltd H M | Improvements in hydraulic pumps |
GB1376732A (en) * | 1971-04-16 | 1974-12-11 | Lucas Industries Ltd | Hydraulic pumps |
DE2817173A1 (en) * | 1978-04-20 | 1979-10-25 | Rexroth Gmbh G L | RADIAL PISTON PUMP |
DE3034377A1 (en) * | 1980-09-12 | 1982-04-22 | Krauss-Maffei AG, 8000 München | FLOW CONTROL VALVE |
-
1989
- 1989-11-13 GB GB898925592A patent/GB8925592D0/en active Pending
-
1990
- 1990-11-13 EP EP19900312361 patent/EP0428374B1/en not_active Expired - Lifetime
- 1990-11-13 DE DE1990610631 patent/DE69010631T2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
EP0428374A1 (en) | 1991-05-22 |
DE69010631T2 (en) | 1994-10-27 |
DE69010631D1 (en) | 1994-08-18 |
GB8925592D0 (en) | 1990-01-04 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1008754B1 (en) | Positive displacement pump systems | |
US3807447A (en) | Fluid controlling apparatus | |
US4107923A (en) | Load responsive valve assemblies | |
US3987622A (en) | Load controlled fluid system having parallel work elements | |
US4075842A (en) | Load responsive fluid control system | |
US4400938A (en) | Hydraulic fluid feeding device for power steering device | |
US4222409A (en) | Load responsive fluid control valve | |
US4502845A (en) | Multistage gear pump and control valve arrangement | |
US4011721A (en) | Fluid control system utilizing pressure drop valve | |
US6901754B2 (en) | Power conserving hydraulic pump bypass compensator circuit | |
JP4230575B2 (en) | Valve device and pump for transmission | |
US4028889A (en) | Load responsive fluid control system | |
GB1425602A (en) | Directional control valves | |
GB2032528A (en) | Rotary positive-displacement fluidmachines | |
EP0176219A1 (en) | Flow regulator valve | |
US5222870A (en) | Fluid system having dual output controls | |
US3642019A (en) | Apparatus for controlling the flow from two outlets | |
US4140152A (en) | Load responsive valve assemblies | |
EP0428374B1 (en) | Positive displacement pump systems | |
CA1245100A (en) | Rotary vane pump | |
US3625007A (en) | Hydraulic system including flow stabilization means | |
GB1201389A (en) | Improvements in or relating to rotary pumps | |
US3801228A (en) | Fuel pump control system and method | |
EP0043947B1 (en) | Power steering pump | |
US4340337A (en) | Positive displacement pump systems |
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 IT NL |
|
17P | Request for examination filed |
Effective date: 19911115 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: HOBOURN GROUP LIMITED |
|
17Q | First examination report despatched |
Effective date: 19930901 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: HOBOURN AUTOMOTIVE LIMITED |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
ITF | It: translation for a ep patent filed |
Owner name: BARZANO' E ZANARDO MILANO S.P.A. |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT NL |
|
REF | Corresponds to: |
Ref document number: 69010631 Country of ref document: DE Date of ref document: 19940818 |
|
ET | Fr: translation filed | ||
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 | ||
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
NLS | Nl: assignments of ep-patents |
Owner name: DANA AUTOMOTIVE LIMITED |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TP |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20041018 Year of fee payment: 15 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20041119 Year of fee payment: 15 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED. Effective date: 20051113 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20060601 |
|
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: 20060731 |
|
NLV4 | Nl: lapsed or anulled due to non-payment of the annual fee |
Effective date: 20060601 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20060731 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20071128 Year of fee payment: 18 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20071221 Year of fee payment: 18 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20081113 |
|
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: 20090603 |
|
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: 20081113 |