EP1046003A1 - Control valve for a hydraulic motor - Google Patents
Control valve for a hydraulic motorInfo
- Publication number
- EP1046003A1 EP1046003A1 EP99900440A EP99900440A EP1046003A1 EP 1046003 A1 EP1046003 A1 EP 1046003A1 EP 99900440 A EP99900440 A EP 99900440A EP 99900440 A EP99900440 A EP 99900440A EP 1046003 A1 EP1046003 A1 EP 1046003A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- annular
- return
- throttle
- control valve
- neutral position
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
- F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
Definitions
- the invention concerns a control valve for a hydraulic motor with a slide extending in a housing bore, the slide having on both sides of a neutral position working areas, each allocated to a working direction, in which working areas an inflow throttle and approximately at the same time also a return throttle open after passing through a deadband.
- a control valve of this kind is known from DE 38 02 672 C2.
- the housing bore has a central annular pump groove connected with a pump connection, having on either side an annular motor groove connected with a motor connection and on the outside of this an annular tank groove connected with a tank connection.
- the slide has two annular distributor grooves, each arranged in the area of an annular motor groove, from which distributor grooves originate inflow pockets extending in the direction of the annular pump grooves for forming the inflow throttles and return pockets extending in the direction of the annular tank grooves for forming the return throttles.
- a deadband occurs - based on the neutral position, in which the inflow pressure increases from a standby value to the required working pressure, and immediately after the deadband a control area occurs, in which both inflow throttle and return throttle are active.
- This is particularly important, when the motor, at least in one working direction, is loadable by an external force, for example by a crane boom, a lifting platform, a stacker truck etc., in connection with which the return throttle must prevent a too fast lowering.
- the known control valve cannot be used, when in the return path a pressure-relief valve is provided, which opens on occurrence of the overpressure and must drain off pressure fluid for as long as it takes to relieve the overpressure.
- the reason is that in the neutral position of the control valve the return throttle is closed, so that the overpressure fluid cannot flow off.
- pressure-relief valves are required. When, however, the return throttle is not completely closed, meaning that in the neutral position an opening remains, this leads to a reduction of the working area.
- the task of the invention is to provide a control valve of the kind mentioned in the introduction, which permits a good control and the use of a pressure-relief valve at the same time.
- this task is solved in that the return throttle is open in the neutral position and closes on passing through the deadband.
- the return throttle has a new characteristic.
- a displacement of the control valve from the neutral position initially causes a closing and subse- quently an opening movement.
- pressure fluid drained off by the pressure-relief valve can be lead off to the tank.
- the return throttle is fully active over the whole control area following the deadband.
- the return throttle reaches the closed position at a distance from the end of the deadband. Across this distance the return throttle is therefore closed, so that the pressure increase on passing through the deadband is disturbed as little as possible. It is also favourable that on moving out of the neutral position the return throttle first closes and then opens again, before the inflow throttle starts opening. As it is difficult to reach the tolerances of a simultaneous opening of return throttle and inflow throttle, the order mentioned is recommended, as the pressure increase does not stop until the inflow throttle is open. In many cases, however, it is also favourable to let the inflow throttle open before the return throttle.
- the housing bore has a central annular pump groove connected with the pump connection, having on either side an annular motor groove, each connected with a motor connection and on the outside of these an annular tank groove, each connected with a tank connection, that the slide has two annular distributor grooves, each arranged in the area of an annular motor groove, from which distributor grooves originate inflow pockets extending in the direction of the annular pump grooves to form the inflow throttles and return pockets extending in the direction of the annular tank grooves to form the return throttles, and that the slide has additional pockets with a limited axial length, which in the neutral position bypass the present connection between annular motor groove and annular tank groove.
- the normal return pocket is thus supplemented by an additional pocket.
- the desired characteristic thus occurs from the combined effect of both pockets.
- the additional pocket axially overlaps both a return pocket and a load pressure sensing opening and is displaced in relation to both in the circumferential direction.
- both pockets and the load pressure sensing opening only need small dimensions, they can be arranged on the slide surface without difficulty.
- Fig. 1 the opening characteristic of a return throttle and an inflow throttle with a control valve ac- cording to the invention
- Fig. 2 a section through a constructive embodiment of such a control valve.
- Fig. 1 shows the opening cross section F in mm 2 across the adjustment distance s in mm of the slide of a control valve.
- the first quadrant Ql refers to a return throttle
- the second quadrant Q2 refers to an inflow throttle.
- the latter is closed over a deadband c and then opens as shown by the curve Z.
- the curve for the return throttle comprises two sections Rl and R2.
- the section Rl shows that the return throttle opens almost simultaneously with the inflow throttle, or rather, at a distance b from the neutral position, that is, temporally shortly before the inflow throttle.
- the return throttle is open in the neutral position and closes after passing through a section a of the deadband, so that an adjustment distance section b-a remains, in which the return throttle is completely closed.
- Fig. 2 shows a valve housing 1 with a housing bore 2, in which a slide 3 is axially adjustable. A displacement from the neutral position, for example to the right, as sug- gested by the arrow s, leads to the diagram in Fig. 1.
- the control valve made this way is connected in series with a compensation valve 4, which maintains a constant pressure drop at the inflow throttle of the control valve. In stead of this flow control, the control valve can also be part of a pressure control or have another desired function.
- the housing bore 2 has a central annular pump groove 5 connected with a pump connection P.
- annular motor grooves 6 and 7 connected with motor connec- tions A and B, respectively.
- annular tank grooves 8 and 9 connected with a tank connection T.
- the slide 3 is provided with two annular distributor grooves 10 and 11, which are arranged in the area of the annular motor grooves 6 and 7. From these originate inflow pockets 12 and 13 directed towards each other, which form inflow throttles 14 and 15 together with the annular pump groove 5.
- return pockets 16 and 17 are extending, which form return throttles 18 and 19 together with the annular tank grooves 8 and 9.
- Additional pockets 20 and 21 also belong to the return throttles, which pockets in the neutral position each bypass a connection 22 and 23 between the annular motor groove 6 and the annular tank groove 8 or the annular motor groove 7 and the annular tank groove 9, respectively.
- the additional pockets 20 and 21 can be provided once or multiple times. Most often, they are distributed evenly on the circumference.
- Fig. 2 also shows the dead zone c, which the slide 3 must pass when leaving the neutral position, before the inflow pocket 12 or 13 reaches the annular pump groove 5.
- the distance b is the distance to be passed by the slide 3 when leaving the neutral position, before the return pocket 16 or 17 reaches the annular tank groove 8 or 9.
- the additional pockets 20, 21 can pass a distance a before getting inactive.
- load pressure sensing openings 24, 25, 26 and 27 are arranged on the slide surface, which, like the return pockets 16 and 17 and the additional pockets 20 an 21, only have a limited extension in the circumferential direction, so that the two pockets and one load pressure sensing opening can be arranged in axial overlapping.
- the pressure-relief valve arranged in the return side motor path can be an independent spring loaded non-return valve, but can also be an additional function of another valve, for example a load retaining valve.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Safety Valves (AREA)
Abstract
A control valve for a hydraulic motor with a slide (3) extending in a housing bore (2), the slide having on both sides of a neutral position working areas, each allocated to a working direction, in which working areas an inflow throttle (14, 15) and approximately at the same time also a return throttle (18, 19) open after passing through a deadband (c). The return throttle (18, 19) is open in the neutral position and closes on passing through the deadband (c). Thus, a pressure-relief valve can drain off pressure fluid to the tank in the neutral position under maintenance of the good control properties.
Description
Control valve for a hydraulic motor
The invention concerns a control valve for a hydraulic motor with a slide extending in a housing bore, the slide having on both sides of a neutral position working areas, each allocated to a working direction, in which working areas an inflow throttle and approximately at the same time also a return throttle open after passing through a deadband.
A control valve of this kind is known from DE 38 02 672 C2. The housing bore has a central annular pump groove connected with a pump connection, having on either side an annular motor groove connected with a motor connection and on the outside of this an annular tank groove connected with a tank connection. The slide has two annular distributor grooves, each arranged in the area of an annular motor groove, from which distributor grooves originate inflow pockets extending in the direction of the annular pump grooves for forming the inflow throttles and return pockets extending in the direction of the annular tank grooves for forming the return throttles. As the inflow throttles and return throttles belonging together close and open synchronously, a deadband occurs - based on the neutral position, in which the inflow pressure increases from a standby value to the required working pressure, and immediately after the deadband a control area occurs, in which both inflow throttle and return throttle are active. This is particularly important, when the motor, at least in one working direction, is loadable by an external force, for example by a crane boom, a lifting platform, a stacker truck etc., in connection with which the return throttle must prevent a too fast lowering.
However, the known control valve cannot be used, when in the return path a pressure-relief valve is provided, which
opens on occurrence of the overpressure and must drain off pressure fluid for as long as it takes to relieve the overpressure. The reason is that in the neutral position of the control valve the return throttle is closed, so that the overpressure fluid cannot flow off. Exactly with the motors being of interest here, which can be loaded by an external force, however, pressure-relief valves are required. When, however, the return throttle is not completely closed, meaning that in the neutral position an opening remains, this leads to a reduction of the working area.
The task of the invention is to provide a control valve of the kind mentioned in the introduction, which permits a good control and the use of a pressure-relief valve at the same time.
According to the invention, this task is solved in that the return throttle is open in the neutral position and closes on passing through the deadband.
In this embodiment the return throttle has a new characteristic. A displacement of the control valve from the neutral position initially causes a closing and subse- quently an opening movement. Thus, in the neutral position, pressure fluid drained off by the pressure-relief valve can be lead off to the tank. In spite of this, the return throttle is fully active over the whole control area following the deadband.
It is expedient that the return throttle reaches the closed position at a distance from the end of the deadband. Across this distance the return throttle is therefore closed, so that the pressure increase on passing through the deadband is disturbed as little as possible.
It is also favourable that on moving out of the neutral position the return throttle first closes and then opens again, before the inflow throttle starts opening. As it is difficult to reach the tolerances of a simultaneous opening of return throttle and inflow throttle, the order mentioned is recommended, as the pressure increase does not stop until the inflow throttle is open. In many cases, however, it is also favourable to let the inflow throttle open before the return throttle.
With regard to construction, it has turned out to be advantageous that the housing bore has a central annular pump groove connected with the pump connection, having on either side an annular motor groove, each connected with a motor connection and on the outside of these an annular tank groove, each connected with a tank connection, that the slide has two annular distributor grooves, each arranged in the area of an annular motor groove, from which distributor grooves originate inflow pockets extending in the direction of the annular pump grooves to form the inflow throttles and return pockets extending in the direction of the annular tank grooves to form the return throttles, and that the slide has additional pockets with a limited axial length, which in the neutral position bypass the present connection between annular motor groove and annular tank groove. The normal return pocket is thus supplemented by an additional pocket. The desired characteristic thus occurs from the combined effect of both pockets.
Additionally it is advantageous that the additional pocket axially overlaps both a return pocket and a load pressure sensing opening and is displaced in relation to both in the circumferential direction. As both pockets and the load pressure sensing opening only need small dimensions,
they can be arranged on the slide surface without difficulty.
In the following the invention is described on the basis of preferred embodiments on the basis of the drawings, showing:
Fig. 1 the opening characteristic of a return throttle and an inflow throttle with a control valve ac- cording to the invention
Fig. 2 a section through a constructive embodiment of such a control valve.
Fig. 1 shows the opening cross section F in mm2 across the adjustment distance s in mm of the slide of a control valve. The first quadrant Ql refers to a return throttle, the second quadrant Q2 refers to an inflow throttle. The latter is closed over a deadband c and then opens as shown by the curve Z. The curve for the return throttle, however, comprises two sections Rl and R2. The section Rl shows that the return throttle opens almost simultaneously with the inflow throttle, or rather, at a distance b from the neutral position, that is, temporally shortly before the inflow throttle. According to the section R2 the return throttle is open in the neutral position and closes after passing through a section a of the deadband, so that an adjustment distance section b-a remains, in which the return throttle is completely closed.
In the neutral position pressure fluid drained off by a pressure relief valve can therefore be lead off to the tank. The normal operation, which starts at the end of the deadband c, remains unchanged, as the return throttle is completely closed at the end of the deadband.
Fig. 2 shows a valve housing 1 with a housing bore 2, in which a slide 3 is axially adjustable. A displacement from the neutral position, for example to the right, as sug- gested by the arrow s, leads to the diagram in Fig. 1. The control valve made this way is connected in series with a compensation valve 4, which maintains a constant pressure drop at the inflow throttle of the control valve. In stead of this flow control, the control valve can also be part of a pressure control or have another desired function.
The housing bore 2 has a central annular pump groove 5 connected with a pump connection P. On both sides are annular motor grooves 6 and 7 connected with motor connec- tions A and B, respectively. Further outwards are arranged annular tank grooves 8 and 9 connected with a tank connection T. The slide 3 is provided with two annular distributor grooves 10 and 11, which are arranged in the area of the annular motor grooves 6 and 7. From these originate inflow pockets 12 and 13 directed towards each other, which form inflow throttles 14 and 15 together with the annular pump groove 5. In the direction of the annular tank groove return pockets 16 and 17 are extending, which form return throttles 18 and 19 together with the annular tank grooves 8 and 9. Additional pockets 20 and 21 also belong to the return throttles, which pockets in the neutral position each bypass a connection 22 and 23 between the annular motor groove 6 and the annular tank groove 8 or the annular motor groove 7 and the annular tank groove 9, respectively. The additional pockets 20 and 21 can be provided once or multiple times. Most often, they are distributed evenly on the circumference.
Fig. 2 also shows the dead zone c, which the slide 3 must pass when leaving the neutral position, before the inflow pocket 12 or 13 reaches the annular pump groove 5. The
distance b is the distance to be passed by the slide 3 when leaving the neutral position, before the return pocket 16 or 17 reaches the annular tank groove 8 or 9.
The additional pockets 20, 21 can pass a distance a before getting inactive. For example, the values a, b and c can be as follows: a = 1.2 mm, b = 1.4 mm, c = 1.5 mm.
Further, load pressure sensing openings 24, 25, 26 and 27 are arranged on the slide surface, which, like the return pockets 16 and 17 and the additional pockets 20 an 21, only have a limited extension in the circumferential direction, so that the two pockets and one load pressure sensing opening can be arranged in axial overlapping.
The pressure-relief valve arranged in the return side motor path can be an independent spring loaded non-return valve, but can also be an additional function of another valve, for example a load retaining valve.
Claims
1. Control valve for a hydraulic motor with a slide extending in a housing bore, the slide having on both sides of a neutral position working areas, each allocated to a working direction, in which working areas an inflow throttle and approximately at the same time also a return throttle open after passing through a deadband, characterised in that that the return throt- tie (18, 19) is open in the neutral position and closes on passing through the deadband (c) .
2. Control valve according to claim 1, characterised in that the return throttle (18, 19) reaches the end po- sition at a distance from the end of the deadband.
3. Control valve according to claim 1 or 2, characterised in that on moving out of the neutral position the return throttle (18, 19) first closes and then opens again, before the inflow throttle (14, 15) starts opening.
4. Control valve according to one of the claims 1 to 3, characterised in that the housing bore (2) has a cen- tral annular pump groove (5) connected with the pump connection (P) , having on either side an annular motor groove (6, 7), each connected with a motor connection (A, B) , and on the outside of this an annular tank groove (8, 9), each connected with a tank connection, that the slide (3) has two annular distributor grooves (10, 11), each arranged in the area of an annular motor groove (6, 7), from which distributor grooves originate inflow pockets (12, 13) extending in the direction of the annular pump groove (5) to form the in- flow throttles (14, 15) and return pockets /16, 17) extending in the direction of the annular tank grooves
(8, 9) to form the return throttles (18, 19), and that the slide (3) has additional pockets (20, 21) with a limited axial length, which in the neutral position bypass the present connection (22, 23) between annular motor groove (6, 7) and annular tank groove (8, 9) .
5. Control valve according to claim 4, characterised in that the additional pocket (20, 21) axially overlaps both a return pocket (16, 17) and a load pressure sensing opening (24, 16) and is displaced in relation to both in the circumferential direction.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19800720A DE19800720C2 (en) | 1998-01-12 | 1998-01-12 | Control valve for a hydraulic motor |
| DE19800720 | 1998-01-12 | ||
| PCT/DK1999/000010 WO1999035424A1 (en) | 1998-01-12 | 1999-01-08 | Control valve for a hydraulic motor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1046003A1 true EP1046003A1 (en) | 2000-10-25 |
| EP1046003B1 EP1046003B1 (en) | 2004-04-21 |
Family
ID=7854324
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99900440A Expired - Lifetime EP1046003B1 (en) | 1998-01-12 | 1999-01-08 | Control valve for a hydraulic motor |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP1046003B1 (en) |
| AU (1) | AU1960399A (en) |
| DE (2) | DE19800720C2 (en) |
| WO (1) | WO1999035424A1 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10107532A1 (en) * | 2001-02-17 | 2002-08-29 | Mannesmann Rexroth Ag | Directional control valve for load-independent control of a hydraulic consumer with regard to direction and speed |
| CN102398866B (en) * | 2011-10-26 | 2013-12-25 | 徐州重型机械有限公司 | Crane luffing control valve and crane luffing hydraulic system |
| CN104235098B (en) * | 2013-12-23 | 2016-08-17 | 江苏恒立液压科技有限公司 | Fluid pressure valve device |
| EP2891806A1 (en) | 2014-01-03 | 2015-07-08 | Danfoss Power Solutions Aps | A hydraulic valve arrangement |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2601999C3 (en) * | 1976-01-21 | 1980-02-21 | Danfoss A/S, Nordborg (Daenemark) | Arrangement for influencing the amount of work of a servo motor |
| SE439183B (en) * | 1979-03-23 | 1985-06-03 | Nordhydraulic Ab | HYDRAULIC DIRECTION VALVE |
| DE3802672C2 (en) * | 1988-01-29 | 1993-12-16 | Danfoss As | Hydraulic control valve with pressure sensing device |
| DE4413216C2 (en) * | 1994-04-15 | 2003-02-06 | Bosch Gmbh Robert | Hydraulic directional valve |
-
1998
- 1998-01-12 DE DE19800720A patent/DE19800720C2/en not_active Expired - Fee Related
-
1999
- 1999-01-08 AU AU19603/99A patent/AU1960399A/en not_active Abandoned
- 1999-01-08 WO PCT/DK1999/000010 patent/WO1999035424A1/en active IP Right Grant
- 1999-01-08 EP EP99900440A patent/EP1046003B1/en not_active Expired - Lifetime
- 1999-01-08 DE DE69916573T patent/DE69916573T2/en not_active Expired - Lifetime
Non-Patent Citations (1)
| Title |
|---|
| See references of WO9935424A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| AU1960399A (en) | 1999-07-26 |
| DE69916573T2 (en) | 2004-08-19 |
| DE19800720A1 (en) | 1999-07-15 |
| DE19800720C2 (en) | 2001-10-31 |
| WO1999035424A1 (en) | 1999-07-15 |
| EP1046003B1 (en) | 2004-04-21 |
| DE69916573D1 (en) | 2004-05-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US5287794A (en) | Hydraulic motor with inlet fluid supplemented by fluid from contracting chamber | |
| US4624445A (en) | Lockout valve | |
| US5857330A (en) | Travelling control circuit for a hydraulically driven type of travelling apparatus | |
| EP1407086B1 (en) | Hydraulic control system | |
| US20100300552A1 (en) | Hydraulic valve device | |
| US6971407B2 (en) | Hydraulic valve arrangement | |
| US4204459A (en) | Combination check and flow control valve for hydraulic systems | |
| US4259986A (en) | Control apparatus for a hydraulic power consumer | |
| US20110132476A1 (en) | Hydraulic valve device | |
| US4338856A (en) | Dual pilot counterbalance valve | |
| WO1999035407A1 (en) | Control arrangement for a hydraulic motor | |
| EP1046003B1 (en) | Control valve for a hydraulic motor | |
| US6256986B1 (en) | Hydrostatic drive system | |
| EP0088406A2 (en) | Control valve for double-acting piston and cylinder assembly | |
| US5778929A (en) | Directional control valve assembly having a pressure compensation valve | |
| US3455322A (en) | Pressure compensated diverter valve | |
| EP0836678B1 (en) | Hydraulic valve to maintain control in fluid-loss condition | |
| CZ103096A3 (en) | Hydraulic rack device | |
| US3464444A (en) | Pilot controllable valve mechanism | |
| US4338962A (en) | Control and relief valves | |
| US3358711A (en) | Valve | |
| GB2210678A (en) | Control system for a hydraulic lift | |
| US6223773B1 (en) | Check valve assembly | |
| DE2810375A1 (en) | CONTROL DEVICE FOR HYDRAULIC POWER TRANSFER | |
| USRE29292E (en) | Control valve means for fluid motors |
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 |
|
| 17P | Request for examination filed |
Effective date: 20000602 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE IT SE |
|
| RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: SAUER-DANFOSS (NORDEBORG) A/S |
|
| RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: SAUER-DANFOSS HOLDING A/S |
|
| 17Q | First examination report despatched |
Effective date: 20030422 |
|
| GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
| GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE IT SE |
|
| REF | Corresponds to: |
Ref document number: 69916573 Country of ref document: DE Date of ref document: 20040527 Kind code of ref document: P |
|
| REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
| RAP2 | Party data changed (patent owner data changed or rights of a patent transferred) |
Owner name: SAUER-DANFOSS HOLDING APS |
|
| 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 |
Effective date: 20050124 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20091218 Year of fee payment: 12 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20100116 Year of fee payment: 12 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20091231 Year of fee payment: 12 |
|
| REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 69916573 Country of ref document: DE Effective date: 20110802 |
|
| 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 Effective date: 20110108 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110109 |
|
| 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: 20110802 |