US20040069255A1 - Method for operating an electrohydraulic valve control system of an internal combustion engine, computer program, and control, and regulating unit for operating an internal combustion engine - Google Patents
Method for operating an electrohydraulic valve control system of an internal combustion engine, computer program, and control, and regulating unit for operating an internal combustion engine Download PDFInfo
- Publication number
- US20040069255A1 US20040069255A1 US10/398,577 US39857703A US2004069255A1 US 20040069255 A1 US20040069255 A1 US 20040069255A1 US 39857703 A US39857703 A US 39857703A US 2004069255 A1 US2004069255 A1 US 2004069255A1
- Authority
- US
- United States
- Prior art keywords
- pressure
- hydraulic accumulator
- low
- actuator
- working chamber
- 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.)
- Abandoned
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 20
- 238000000034 method Methods 0.000 title claims description 27
- 230000001105 regulatory effect Effects 0.000 title claims description 16
- 238000004590 computer program Methods 0.000 title claims description 8
- 239000012530 fluid Substances 0.000 claims description 18
- 230000033228 biological regulation Effects 0.000 claims description 3
- 229910000859 α-Fe Inorganic materials 0.000 claims description 3
- 230000007935 neutral effect Effects 0.000 description 14
- 230000004048 modification Effects 0.000 description 6
- 238000012986 modification Methods 0.000 description 6
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 230000006641 stabilisation Effects 0.000 description 2
- 238000011105 stabilization Methods 0.000 description 2
- 230000001960 triggered effect Effects 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 1
- 230000006399 behavior Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000009499 grossing Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000035484 reaction time Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
Definitions
- the invention relates first of all to a method for operating an electrohydraulic valve control of an internal combustion engine, with at least one actuator that acts on a gas exchange valve and has at least one working chamber, which in order to switch the actuator from a first position into a second position, is connected to a high-pressure hydraulic accumulator and shut off from a low-pressure return, and in order to switch the actuator from the second position back into the first position, is connected to the low-pressure return and shut off from the high-pressure hydraulic accumulator.
- Electrohydraulic valve controls of internal combustion engines permit gas exchange valves to be triggered independent of the position of the crankshaft or camshaft. Among other things, they permit fuel savings and improvements to the emissions characteristics of an internal combustion engine to be achieved.
- the shaft of the gas exchange valve is connected to a hydraulic actuator.
- This actuator has two working chambers of different sizes on the two sides with the piston end faces.
- the small end face is continuously acted on by high pressure from a high-pressure hydraulic accumulator, which is in turn supplied by a hydraulic pump.
- the large end face of the piston is alternatively connected either likewise to the high-pressure hydraulic accumulator or to a low-pressure return. Depending on which of these it is connected to, a force resultant is produced, which opens or closes the gas exchange valve.
- the object of the current invention is to modify a method of the type mentioned at the beginning so that the pressure in the high-pressure hydraulic accumulator can be kept constant in a simple manner.
- the measures taken according to the invention permit the high-pressure hydraulic accumulator to be connected directly to the low-pressure return, without requiring additional components, e.g. a pressure control valve.
- an operating state is expressly permitted in which the working chamber is connected to the high-pressure hydraulic accumulator and the low-pressure return of the electrohydraulic valve control at the same time. If it turns out, e.g. as determined by a sensor, that it is necessary to drain hydraulic fluid from the high-pressure hydraulic accumulator in order to be able to keep the pressure in it constant, then this can occur in a simple manner according to the invention in that the fluid flows through the working chamber to the low-pressure return.
- the on-off valves usually used for this have a short reaction time and a highly dynamic switching behavior, then it is also possible to smooth out momentary fluctuations of the pressure in the high-pressure hydraulic accumulator. Therefore on the one hand, the method according to the invention permits the elimination of a pressure control valve. On the other hand, the high-pressure hydraulic accumulator can be smaller. This reduces costs in the manufacture of the electrohydraulic valve control and in addition, the electrohydraulic valve control takes up less space.
- the working chamber of an actuator in order to stabilize or reduce the pressure in the high-pressure hydraulic accumulator, is connected to the high-pressure hydraulic accumulator and the low-pressure return simultaneously and its associated gas exchange valve is closed at the time.
- This modification of the method according to the invention is particularly suitable if an exertion of the full high pressure is used to trigger the actuator and open the gas exchange valve. In the closed neutral position of the gas exchange valve, therefore, the working chamber of the actuator usually contains a pressure, which is lower than the full high pressure of the high-pressure hydraulic accumulator.
- the working chamber of the actuator contains a pressure, which is lower than the full pressure in the high-pressure hydraulic accumulator.
- the closed neutral position of the gas exchange valve is consequently not influenced by this simultaneous connection of the working chamber to both the high-pressure hydraulic accumulator and the low-pressure return.
- the working chamber of an actuator is connected to the high-pressure hydraulic accumulator and the low-pressure return simultaneously and its associated gas exchange valve cannot open at the time due to a high internal pressure in the cylinder. This effectively prevents an undesired opening of the gas exchange valve in an actuator that reacts “sensitively” to pressure fluctuations in the working chamber.
- a triggering of the actuator which was intended anyway, is used to drain hydraulic fluid from the high-pressure hydraulic accumulator.
- This is made possible by shifting the time at which the working chamber is connected to the low-pressure return or to the high-pressure hydraulic accumulator. Consequently, there is an overlap of the times in which the working chamber is connected to the low-pressure return and to the high-pressure hydraulic accumulator. This makes it possible to integrate the stabilization or reduction of the pressure in the high-pressure hydraulic accumulator into the normal operation of an actuator.
- the working chamber of an actuator is temporarily connected to the high-pressure hydraulic accumulator and the low-pressure return at the same time when the internal combustion engine is operated at a low speed.
- This modification takes into account the fact that at a low engine speed, a lower pressure in the high-pressure hydraulic accumulator is generally advantageous. Since such a deliberate pressure reduction in the high-pressure hydraulic accumulator was not previously possible, the triggering strategy of the actuator instead had to be changed at low engine speeds. This is no longer necessary with the modified method according to the invention.
- Another modification includes the proposal that the pressure stabilization or pressure reduction by means of a simultaneous connection of the working chamber of an actuator to the low-pressure return and the high-pressure hydraulic accumulator be combined with a control or regulation of the delivery quantity by means of a hydraulic pump. While the above-mentioned connection of the working chamber can be used to exert very rapid and highly dynamic influence on the pressure in the high-pressure hydraulic accumulator, the control or regulation of the delivery quantity by means of the hydraulic pump permits a long-term, quantitatively substantial adaptation of the pressure in the high-pressure hydraulic accumulator.
- the method according to the invention is particularly preferable if the actuator has two working chambers that are separated from each other by pressure surfaces on a piston, which are of different sizes and work in opposition to each other, and the one working chamber is continuously acted on by high pressure while the other working chamber can be connected to the high-pressure hydraulic accumulator and the low-pressure return. Actuators of this kind can achieve very short switching times, thus making it easier to execute the method according to the invention.
- the hydraulic fluid can also flow out of the working chamber into a low-pressure hydraulic accumulator. This reduces the pressure difference when the hydraulic fluid flows out, which counteracts cavitation.
- the invention also relates to a computer program, which is suitable for executing the method according to one of the preceding claims when it is run on a computer. It is particularly preferable if the computer program is stored in a memory, in particular a flash memory or a ferrite RAM.
- the invention also relates to a control and regulating unit for operating an internal combustion engine, which is connected at least to a first control valve and a second control valve of an electrohydraulic valve control, which can connect a working chamber of an actuator of a gas exchange device to a high-pressure hydraulic accumulator and/or to a low-pressure return.
- control and regulating unit be suitable for executing the above-mentioned method. It is particularly preferable if it is provided with a computer program of the type mentioned above.
- FIG. 1 schematically depicts an electrohydraulic valve control of an internal combustion engine
- FIG. 2 is a graph, which depicts the pressure curve over time in a high-pressure hydraulic accumulator from FIG. 1;
- FIG. 3 is a graph, which depicts the pressure in the high-pressure hydraulic accumulator from FIG. 1 over a speed of the internal combustion engine.
- an electrohydraulic valve control is labeled as a whole with the reference numeral 10 .
- it includes a reservoir for hydraulic fluid, which is labeled here with the reference numeral 12 and which can be the oil pan of the internal combustion engine.
- a controllable high-pressure hydraulic pump 14 feeds the hydraulic fluid from the hydraulic reservoir 12 into a high-pressure hydraulic accumulator 16 .
- a hydraulic line 18 leads from the high-pressure hydraulic accumulator 16 to a solenoid valve 22 via a pressure control valve 20 .
- the hydraulic line 18 leads from the solenoid valve 22 to an actuator 24 .
- This actuator is a hydraulic cylinder with a double-acting piston 26 .
- the piston 26 is guided in a housing 28 .
- a first working chamber 30 is formed between this piston and the housing 28 .
- This working chamber 30 is connected to the solenoid valve 22 .
- a second working chamber 32 is formed between this piston and the housing 28 .
- This working chamber 32 is connected via a branch line 33 to the section of the hydraulic line 18 situated between the high-pressure hydraulic accumulator 16 and the solenoid valve 22 .
- the end face 34 of the piston 26 at the top in FIG. 1 is larger than the end face 36 of the piston 26 at the bottom in FIG. 1, which end face 36 defines the second working chamber 32 .
- the piston 26 is thus a so-called “differential piston”.
- the piston 26 is connected to a gas exchange valve 38 , which has a valve rod 40 and a valve element 42 .
- the valve element 42 can open or close an opening (no reference numeral) of a combustion chamber 44 .
- the combustion chamber 44 is contained in an engine block 46 of an internal combustion engine (no reference numeral).
- a hydraulic line 48 leads via a second solenoid valve 50 to a low-pressure hydraulic accumulator 52 .
- This accumulator is in turn connected via a pressure control valve 54 to a low-pressure return 56 , which finally leads back to the hydraulic reservoir 12 .
- another hydraulic line 58 leads via a pressure control valve 60 back to the high-pressure hydraulic accumulator 16 .
- the two solenoid valves 22 and 50 are actuated by magnetic actuators 62 and 64 and are each pressed onto their neutral position by a compression spring 66 and 68 .
- the first solenoid valve 22 is closed in its neutral position 70 , in which the current to the magnetic actuator 62 is switched off, whereas it is open in the actuated switched position 72 .
- the second solenoid valve 50 is open in its neutral switched position 74 and is closed in the actuated switched position in which the magnetic actuator 64 is supplied with current.
- This actuated switched position is labeled with the reference numeral 76 .
- the electrohydraulic valve control 10 also has a control and regulating unit 78 . On the output side, this unit is connected to the magnetic actuators 62 and 64 . It can also control the hydraulic pump 14 . On the input side, the control and regulating unit 78 is connected to a pressure sensor 80 , which detects the pressure in the high-pressure hydraulic accumulator 16 . The control and regulating unit 78 is also connected to a speed sensor for the crankshaft of the engine. This speed sensor is labeled with the reference numeral 82 .
- the electrohydraulic valve control 10 operates as follows (the method described hereinafter is stored as a computer program on a ferrite RAM (not shown) in the control and regulating unit 78 ): In order to open the gas exchange valve 38 , the piston 26 must be moved downward in FIG. 1. This is achieved in that starting from the neutral position 74 , the second solenoid valve 50 is supplied with current and is thus closed. This consequently breaks the connection between the first working chamber 30 and the low-pressure hydraulic accumulator 52 .
- control and regulating unit 78 supplies current to the magnetic actuator 62 of the first solenoid valve 22 so that this solenoid valve 22 moves from its closed neutral position 70 into the open switched position 72 .
- This connects the first working chamber 30 to the high-pressure hydraulic accumulator 16 . Consequently, the hydraulic pressure prevailing in the high-pressure hydraulic accumulator 16 is also established in the first working chamber 30 .
- control and regulating unit 78 initially switches off the current to the first solenoid valve 22 so that the compression spring 66 presses it from the open switched position 72 into the closed switched position 70 . This consequently breaks the connection again between the high-pressure hydraulic accumulator 16 and the first working chamber 30 .
- control and regulating unit 78 switches off the current to the second solenoid valve 50 so that the compression spring 68 moves it from the closed switched position 76 into the open neutral position 74 .
- the first working chamber 30 is then reconnected with the low-pressure hydraulic accumulator 52 . Consequently, the pressure in the first working chamber 30 decreases until a force resultant is produced, which moves the piston 26 back upward. This closes the gas exchange valve 38 .
- the control and regulating unit 78 switches the first solenoid valve 22 into its open switched position 72 while the second solenoid valve 50 remains in its open neutral position 74 . It is assumed here that the engine is in an operating state in which the gas exchange valve 38 , which is connected to the actuator 24 , should remain closed.
- the direct connection between the high-pressure hydraulic accumulator 16 and the low-pressure hydraulic accumulator 52 is preferably produced when a high pressure prevailing in the combustion chamber 44 presses the valve element 42 into its closed position.
- the control and regulating unit 78 terminates the flow of hydraulic fluid out of the high-pressure hydraulic accumulator 16 into the low-pressure hydraulic accumulator 52 in a simple manner by switching the current to the first solenoid valve 22 off again so that it returns to its closed neutral position 70 . The pressure prevailing in the low-pressure hydraulic accumulator 52 is then reestablished in the first working chamber 30 .
- the electrohydraulic valve control 10 can also be operated in a different manner in order to stabilize or reduce the pressure in the high-pressure hydraulic accumulator 16 :
- connection of the high-pressure hydraulic accumulator 16 to the low-pressure hydraulic accumulator 52 can be coupled to a triggering of the actuator 24 .
- the actuator 24 is triggered so that the gas exchange valve 38 opens, for example just before the magnetic actuator 64 of the second solenoid valve 50 is supplied with current, which causes it to move from its open neutral position 74 into the closed switched position 76 , the solenoid valve 22 can already have been moved from its closed neutral position 70 into the actuated and open switched position 72 .
- This also produces a temporary direct connection from the high-pressure hydraulic accumulator 16 , to the low-pressure hydraulic accumulator 52 , and on to the low-pressure return 56 , through which hydraulic fluid flows out of the high-pressure hydraulic accumulator 16 , consequently allowing the pressure in this accumulator to be kept constant or to be reduced.
- Such a temporary actuation of the valves and such a temporary connection of the high-pressure hydraulic accumulator 16 to the low-pressure return 56 permit the pressure in the high-pressure hydraulic accumulator 16 to be kept constant, as can be inferred from FIG. 2.
- the quantity of the fluid to be drained is controlled by the duration of the direct connection.
- the pressure without a corresponding actuation of the solenoid valves 22 and 50 is depicted with a dashed line and the pressure curve that can be produced with a corresponding actuation of the solenoid valves 22 and 50 is depicted with a solid line.
- the engine speed sensor 82 detects this and sends a corresponding signal to the control and regulating unit 78 .
- This unit can then trigger the solenoid valves 22 and 50 so that the pressure is reduced in the high-pressure hydraulic accumulator 16 .
- the operating pressure usually 200 bar is reduced to approximately 50 bar.
- FIG. 3 depicts the relationship between the speed n of the engine and the pressure P in the high-pressure hydraulic accumulator 16 .
- the pressure adjustment in the high-pressure hydraulic accumulator 16 can be assisted if need by through an appropriate triggering of the high-pressure hydraulic pump 14 .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10138881.0 | 2001-08-08 | ||
DE10138881A DE10138881A1 (de) | 2001-08-08 | 2001-08-08 | Verfahren zum Betreiben einer elektrohydraulischen Ventilsteuerung einer Brennkraftmaschine, Computerprogramm sowie Steuer- und Regelgerät zum Betreiben einer Brennkraftmaschine |
PCT/DE2002/001957 WO2003016682A1 (de) | 2001-08-08 | 2002-05-28 | Verfahren zum betreiben einer elektrohydraulischen ventilsteuerung einer brennkraftmaschine, computerprogramm sowie steuer- und regelgerät zum betreiben einer brennkraftmaschine |
Publications (1)
Publication Number | Publication Date |
---|---|
US20040069255A1 true US20040069255A1 (en) | 2004-04-15 |
Family
ID=7694759
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/398,577 Abandoned US20040069255A1 (en) | 2001-08-08 | 2002-05-28 | Method for operating an electrohydraulic valve control system of an internal combustion engine, computer program, and control, and regulating unit for operating an internal combustion engine |
Country Status (6)
Country | Link |
---|---|
US (1) | US20040069255A1 (de) |
EP (1) | EP1430201B1 (de) |
JP (1) | JP4047807B2 (de) |
KR (1) | KR100852805B1 (de) |
DE (2) | DE10138881A1 (de) |
WO (1) | WO2003016682A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080109151A1 (en) * | 2002-12-24 | 2008-05-08 | Rolf Jaros | Method and Control Device for Triggering Solenoid Valves Assigned to Gas-Exchange Valves |
WO2019069000A1 (fr) * | 2017-10-02 | 2019-04-11 | Vianney Rabhi | Actionneur hydraulique de soupape a regeneration |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1287069C (zh) * | 2003-11-27 | 2006-11-29 | 宁波华液机器制造有限公司 | 一种压差式变气门控制系统 |
DE102004030306A1 (de) * | 2004-06-23 | 2006-01-12 | Robert Bosch Gmbh | Verfahren zur Erfassung mindestens einer Ventilhubposition bei einer Brennkraftmaschine mit variabler Ventilsteuerung |
DE102009046943A1 (de) * | 2009-11-20 | 2011-05-26 | Robert Bosch Gmbh | Elektrohydraulischer Aktor |
JP5589634B2 (ja) * | 2010-07-20 | 2014-09-17 | いすゞ自動車株式会社 | カムレスエンジン弁開閉制御装置 |
JP5891475B2 (ja) * | 2011-03-24 | 2016-03-23 | 三菱重工業株式会社 | 油圧アクチュエータシステム |
DE102013207863A1 (de) * | 2013-04-30 | 2014-10-30 | Mahle International Gmbh | Vorrichtung zur Steuerung eines Gaswechselventils einer Brennkraftmaschine |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5123397A (en) * | 1988-07-29 | 1992-06-23 | North American Philips Corporation | Vehicle management computer |
US5572961A (en) * | 1995-04-05 | 1996-11-12 | Ford Motor Company | Balancing valve motion in an electrohydraulic camless valvetrain |
US5806300A (en) * | 1995-12-22 | 1998-09-15 | United Technologies Corporation | Electronic control for a variable delivery, positive displacement fuel pump |
US6067946A (en) * | 1996-12-16 | 2000-05-30 | Cummins Engine Company, Inc. | Dual-pressure hydraulic valve-actuation system |
US6321702B1 (en) * | 1998-06-12 | 2001-11-27 | Robert Bosch Gmbh | Process for controlling a gas exchange valve for internal combustion engines |
US6321703B1 (en) * | 1998-06-12 | 2001-11-27 | Robert Bosch Gmbh | Device for controlling a gas exchange valve for internal combustion engines |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4407585C2 (de) * | 1994-03-08 | 1996-09-19 | Mtu Friedrichshafen Gmbh | Variable Ventilsteuerung |
-
2001
- 2001-08-08 DE DE10138881A patent/DE10138881A1/de not_active Ceased
-
2002
- 2002-05-28 KR KR1020037004929A patent/KR100852805B1/ko not_active IP Right Cessation
- 2002-05-28 DE DE50204345T patent/DE50204345D1/de not_active Expired - Lifetime
- 2002-05-28 US US10/398,577 patent/US20040069255A1/en not_active Abandoned
- 2002-05-28 WO PCT/DE2002/001957 patent/WO2003016682A1/de active IP Right Grant
- 2002-05-28 EP EP02747175A patent/EP1430201B1/de not_active Expired - Lifetime
- 2002-05-28 JP JP2003520955A patent/JP4047807B2/ja not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5123397A (en) * | 1988-07-29 | 1992-06-23 | North American Philips Corporation | Vehicle management computer |
US5572961A (en) * | 1995-04-05 | 1996-11-12 | Ford Motor Company | Balancing valve motion in an electrohydraulic camless valvetrain |
US5806300A (en) * | 1995-12-22 | 1998-09-15 | United Technologies Corporation | Electronic control for a variable delivery, positive displacement fuel pump |
US6067946A (en) * | 1996-12-16 | 2000-05-30 | Cummins Engine Company, Inc. | Dual-pressure hydraulic valve-actuation system |
US6321702B1 (en) * | 1998-06-12 | 2001-11-27 | Robert Bosch Gmbh | Process for controlling a gas exchange valve for internal combustion engines |
US6321703B1 (en) * | 1998-06-12 | 2001-11-27 | Robert Bosch Gmbh | Device for controlling a gas exchange valve for internal combustion engines |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080109151A1 (en) * | 2002-12-24 | 2008-05-08 | Rolf Jaros | Method and Control Device for Triggering Solenoid Valves Assigned to Gas-Exchange Valves |
US7472017B2 (en) * | 2002-12-24 | 2008-12-30 | Robert Bosch Gmbh | Method and control device for triggering solenoid valves assigned to gas-exchange valves |
WO2019069000A1 (fr) * | 2017-10-02 | 2019-04-11 | Vianney Rabhi | Actionneur hydraulique de soupape a regeneration |
KR20200057741A (ko) * | 2017-10-02 | 2020-05-26 | 비아니 라비 | 재생 밸브용 유압 액추에이터 |
KR102652495B1 (ko) | 2017-10-02 | 2024-03-28 | 비아니 라비 | 재생 밸브용 유압 액추에이터 |
Also Published As
Publication number | Publication date |
---|---|
DE50204345D1 (de) | 2005-10-27 |
KR20040019008A (ko) | 2004-03-04 |
JP2004538416A (ja) | 2004-12-24 |
JP4047807B2 (ja) | 2008-02-13 |
EP1430201A1 (de) | 2004-06-23 |
DE10138881A1 (de) | 2003-02-27 |
KR100852805B1 (ko) | 2008-08-18 |
EP1430201B1 (de) | 2005-09-21 |
WO2003016682A1 (de) | 2003-02-27 |
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Legal Events
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AS | Assignment |
Owner name: ROBERT BOSCH GMBH, GERMANY Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:SCHLEMBACH, HANS;GAESSLER, HERMANN;DIEHL, UDO;AND OTHERS;REEL/FRAME:014663/0629;SIGNING DATES FROM 20030505 TO 20030528 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |