US20050217622A1 - Valve mechanism with a variable valve opening diameter - Google Patents

Valve mechanism with a variable valve opening diameter Download PDF

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Publication number
US20050217622A1
US20050217622A1 US10/399,656 US39965603A US2005217622A1 US 20050217622 A1 US20050217622 A1 US 20050217622A1 US 39965603 A US39965603 A US 39965603A US 2005217622 A1 US2005217622 A1 US 2005217622A1
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US
United States
Prior art keywords
valve
mechanism according
seal
valve mechanism
regulating
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
Application number
US10/399,656
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English (en)
Inventor
Uwe Hammer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Individual
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Filing date
Publication date
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Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HAMMER, UWE
Publication of US20050217622A1 publication Critical patent/US20050217622A1/en
Abandoned legal-status Critical Current

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    • 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
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/20—Shapes or constructions of valve members, not provided for in preceding subgroups of this group
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/28—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of coaxial valves; characterised by the provision of valves co-operating with both intake and exhaust ports
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • 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

Definitions

  • the invention relates to a valve mechanism with a variable valve opening cross section with the features mentioned in the preamble to claim 1 .
  • an electrohydraulic valve control offers the possibility of a variable or completely variable valve control so that it is possible to optimize the gas exchange and consequently to increase the motor efficiency of the internal combustion engine.
  • the electrohydraulic valve control includes a hydraulically actuatable control valve, whose control valve piston actuates a valve body of the inlet and outlet valves and moves it toward a valve seat (valve seat ring) (closing of the valve) or moves it away from the seat (opening of the valve).
  • the control valve can be actuated by controlling the pressure of a hydraulic medium.
  • the pressure control in this connection is executed by means of solenoid valves incorporated into the hydraulic circuit.
  • EP 0 455 761 B1 is a hydraulic valve control device for an internal combustion engine.
  • the fundamental technical principal of this embodiment lies in moving an engine valve by means of a controlled pressure of a hydraulic fluid.
  • This embodiment includes the provision that an electronic control unit triggers a solenoid valve, which in turn controls the movement of a reservoir piston that changes of the stroke of the engine valve.
  • EP 0 512 698 A1 describes an adjustable valve system for an internal combustion engine. This embodiment is an example of a mechanical valve control by means of the cams of a rotating camshaft.
  • U.S. Pat. No. 4,777,915 is an electromagnetic valve control system for an internal combustion engine.
  • a similar embodiment of an electromagnetic valve control is known from EP 0 471 614 A1.
  • the valve is moved back and forth into different positions through the use of electromagnetic force.
  • the electromagnets are disposed inside a housing part of the cylinder head, in two different regions. The alternating activation of the electromagnets moves the valve alternatively into two end positions that respectively correspond to the open position and the closed position of the valve. In these end positions of the valve, the opening to allow the passage of the air-fuel mixture into the combustion chamber is open the widest it can go or is completely closed.
  • EP 0 551 271 B1 Another embodiment is known from EP 0 551 271 B1.
  • This embodiment is a valve mechanism with a disk valve, which is disposed in a passageway of an internal combustion engine.
  • the fundamental principle of this embodiment lies in dividing the valve disk in two, where the first half of the valve disk executes only part of the stroke of the other half of the valve disk.
  • a particular disadvantage of these embodiments for valve control is the high cost of manufacturing and assembling the valve mechanism due to its complex design. This has a negative effect on the costs of manufacture and assembling. Furthermore, these embodiments require extremely high speeds and powerful forces for valve control, resulting in an inevitable increase in susceptibility to malfunction of the valve control due to a considerable wear on the parts of the valve mechanism.
  • valve mechanism with the characterizing features of the main claim, has the advantage over the prior art of achieving a variable valve opening cross section through the use of simple means.
  • a seal valve is disposed coaxial to the gas exchange valve, is acted on by the force of a coupling spring, and can be slid back and forth in an axial direction by the valve control unit, wherein the position of the seal valve in relation to the gas exchange valve in the axial direction can be adjusted by means of an adjusting unit, which is essentially comprised of a regulating valve and a working cylinder that contains a regulating piston that can be slid by means of a working medium, produces a valve mechanism that has a simple design and functions in a reliable, durable fashion.
  • variable valve opening cross section can be produced, wherein each individual valve can be separately regulated. It is also possible to regulate all of the outlet and inlet valves together or separately by cylinder.
  • the variable valve opening cross section can advantageously be produced with the valve mechanism according to the invention, without producing high speeds and without powerful forces so that this valve mechanism has an extremely low susceptibility to malfunction. Due to its simple design, the valve mechanism according to the invention can be inexpensively manufactured and assembled.
  • the invention advantageously achieves a variable valve control that makes it possible to optimize the gas exchange and consequently to increase the motor efficiency of the internal combustion engine.
  • valve control unit is a camshaft
  • the gas exchange valve has a rotationally symmetrical basic design and is comprised of a valve shaft, the lower end of which has a valve disk supported on it.
  • valve disk has a conical circumference surface, which constitutes the sealing seat of the gas exchange valve.
  • a preferred embodiment of the invention provides that in the closed position of the valve mechanism, the sealing seat of the gas exchange valve respectively rests directly against a sealing seat of the seal valve and against a valve seat ring of the cylinder head.
  • the seal valve is comprised of a bushing-shaped supporting body, which is disposed so that it can slide axially back and forth inside a guide of the cylinder head.
  • FIG. 1 shows a section through a cylinder head, with the valve mechanism according to the invention
  • FIG. 2 shows a perspective view of a seal valve of the valve mechanism according to the invention
  • FIG. 3 shows a connection diagram of a hydraulic adjusting unit of the regulating slide valve of the valve mechanism according to the invention
  • FIG. 4 is a sectional depiction of a regulating valve of a hydraulic adjusting unit of the regulating slide valve of the valve mechanism according to the invention.
  • valve mechanism according to the invention In the four Figs., the individual parts of the valve mechanism according to the invention are depicted schematically and are only shown with the components that are essential to the invention. The same parts of the valve mechanism according to the invention are given the same reference numerals in the Figs. and as a rule, are only described once.
  • FIG. 1 shows the valve mechanism according to the invention in its position in the cylinder head 18 of an internal combustion engine.
  • the valve mechanism has a gas exchange valve 12 , which is acted on by the force of a valve spring 16 .
  • the gas exchange valve 12 can be slid back and forth inside a guide, wherein the sliding motion is produced by a valve control unit.
  • a camshaft (not shown) is provided as the valve control unit.
  • the gas exchange valve 12 has a rotationally symmetrical basic design and is comprised of a valve shaft 14 , the lower end of which has a valve disk 20 supported on it.
  • FIG. 1 shows the valve mechanism in the closed position of the gas exchange valve 12 . In this position, the sealing seat 28 of the gas exchange valve 12 respectively rests directly against a sealing seat 30 of the seal valve 10 and against a valve seat ring 22 of the cylinder head 18 .
  • gas exchange valves 12 are generally known in and of themselves, so there is no need to discuss them in detail in the context of the current specification.
  • the invention provides that a seal valve 10 is disposed coaxial to the gas exchange valve 12 .
  • the seal valve 10 is acted on by the force of a coupling spring 24 and can be slid axially back and forth.
  • the camshaft that controls the sliding motion of the gas exchange valve 12 also produces the sliding motion of the seal valve 10 .
  • FIG. 2 shows a perspective view of the seal valve 10 .
  • the seal valve 10 is essentially comprised of a supporting body 40 and a sealing body 38 .
  • the supporting body 40 of the seal valve 10 is bushing-shaped and is contained so that it can slide axially back and forth inside a guide of the cylinder head 18 .
  • the seal valve 10 is provided with a cylindrical sealing body 38 whose outer surface constitutes the sealing seat 30 .
  • the sealing seat 38 is connected to the supporting body 40 by means of connecting rods 42 .
  • a stop disk 26 is fastened to the supporting body 40 in the vicinity of its top end. In order to facilitate assembly, this stop disk 26 is comprised of two parts. The two parts of the stop disk 26 are encompassed by a clamping ring 36 , which holds them together.
  • connection between the sealing body 38 and the supporting body 40 is designed so that sufficient space remains for the air or air-fuel mixture flowing through. Both for the inlet and for the outlet of air or of the air-fuel mixture, this advantageously provides for a through opening inside the seal valve 10 large enough to permit an unhindered flow of this medium.
  • FIG. 3 shows a connection diagram for a hydraulic adjusting unit with a regulating valve 44 , which can be used to regulate the position of the seal valve 10 in relation to the gas exchange valve 12 by means of a regulating piston 46 , which is disposed in a sliding fashion inside a working cylinder 52 .
  • the regulating valve 44 which is embodied in the form of an intrinsically known 3-way valve, has three separate working chambers, which permit the hydraulic fluid to flow into the working chamber 52 and permit the hydraulic fluid to flow back out of the working chamber 52 or completely shut off the flow of the hydraulic fluid. To this end, the sliding of the regulating valve 44 can bring the working chambers of the regulating valve 44 into three different switched positions A, B, C.
  • FIG. 4 shows a sectional view of the design of a regulating valve 44 of the hydraulic adjusting unit.
  • the regulating valve 44 is comprised of a housing 56 with three connections.
  • the connections respectively, are a pressure connection 60 , a return line 54 , and a cylinder connection 58 .
  • Pressure generated by an oil pump 50 supplies the hydraulic fluid to the regulating valve 44 via the pressure connection 60 .
  • the return line 54 permits the hydraulic fluid to flow from the regulating valve 44 to the oil tank 48 (not shown here).
  • the cylinder connection 58 communicates with the working cylinder 52 of the adjusting unit and is used to supply the hydraulic fluid to the working cylinder 52 and to drain hydraulic fluid from the working cylinder 52 .
  • the cylinder connection 58 is disposed on the one side of the regulating valve 44 , approximately in its middle.
  • the pressure connection 60 and the return line 56 are disposed on opposite sides of the regulating valve 44 , close to its respective upstream and downstream ends.
  • An adjusting pin 90 is supported so that it can be slid axially in the housing 88 of the regulating valve 44 .
  • the adjusting pin 90 is connected at one of its ends to a stroke drive unit 84 , which generates an axial sliding motion of the adjusting pin 90 .
  • the adjusting pin 90 is continuously acted on by the force of a spring 78 , which presses a stop connected to the adjusting pin 90 against a support 86 of the housing 88 of the regulating valve 44 .
  • At the opposite end of the adjusting pin 90 it is supported so that it can slide in a bore of a sealing seat support 72 of the housing 88 of the regulating valve 44 .
  • a first driver disk 64 and a second driver disk 66 are fastened to the adjusting pin 90 spaced apart from each other.
  • the first driver disk 64 serves to support a first seal valve 68 and the second driver disk 66 serves to support a second seal valve 70 , wherein both of the seal valves 68 , 70 are supported so that they can slide axially on the adjusting pin 90 and a compression spring 80 is disposed between the two seal valves 68 , 70 , whose force presses the seal valves 68 , 70 into contact with their respective associated driver disks 64 , 66 .
  • the first seal valve 68 has a conical outer surface, which corresponds to a sealing seat 74 of the housing 88 of the regulating valve 44 .
  • the second seal valve 70 also has a conical outer surface, which corresponds to a sealing seat 76 of the sealing seat support 72 of the regulating valve 44 .
  • valve mechanism shown in FIGS. 1 and 2 functions in the following manner:
  • the valve control unit which is a camshaft (not shown) in a preferred embodiment of the invention, can either open or close the gas exchange valve 12 .
  • the camshaft pushes down the valve shaft 14 of the gas exchange valve 12 and thus controls the course of movement of the gas exchange valve 12 .
  • all known methods can be used, which are based on the technical principles of a bucket tappet, a tilting lever, a drag lever, and the like.
  • the camshaft 44 works against the restoring force of the valve spring 16 , which is supported against the cylinder head 18 and against the valve disk 20 that moves along with the gas exchange valve 12 .
  • the rotation of the camshaft 44 pushes the gas exchange valve 12 downward, and the sealing seat 28 of the gas exchange valve 12 lifts up from the valve seat ring 22 .
  • the coupling spring 24 which is subjected to a certain degree of initial stress, causes the seal valve 10 to move along with it.
  • the coupling spring 24 is supported against the valve disk 20 and the stop disk 26 , which is connected to the seal valve 10 .
  • the sealing seat 28 of the seal valve 10 is pressed against the sealing seat 28 of the gas exchange valve 12 . Since an annular gap seal is provided between the sealing body 38 and the valve seat ring 22 , only a very slight air quantity (leakage) can travel into the combustion chamber 32 .
  • the gas exchange valve 12 and therefore also the seal valve 10 follow the course of the cam until the stop disk 26 comes into contact with the regulating slide valve 34 .
  • the regulating slide valve 34 In its starting position, the regulating slide valve 34 can be adjusted in relation to the gas exchange valve 12 in the axial direction of the valve shaft 14 .
  • the regulating slide valve 34 here can only be adjusted by means of a corresponding adjusting unit, a preferred embodiment of which, in the form of a hydraulic adjusting unit, is shown in detail in FIGS. 3 and 4 . Otherwise, the position of the regulating slide valve 34 inside the valve mechanism remains fixed, even when external forces act on it. There is also the possibility of embodying the adjusting unit in an electric or pneumatic form.
  • the seal valve 10 can execute no further movement in the opening direction of the gas exchange valve 12 . Since the camshaft moves the gas exchange valve 12 further, the sealing seat 28 of the gas exchange valve 12 lifts up from the sealing seat 30 of the seal valve 10 , which allows air to travel into the combustion chamber 32 .
  • the coupling spring 24 is compressed in the process of this.
  • valve spring 16 pushes the gas exchange valve 12 in the closing direction.
  • the sealing seat 28 of the gas exchange valve 12 comes to rest against the sealing seat 30 of the seal valve 10 .
  • the seal valve 10 is carried along with the gas exchange valve until the sealing seat 28 of the gas exchange valve 12 comes to rest against the valve seat ring 22 and the gas exchange valve 12 is closed.
  • the gas exchange valve 12 and consequently also the seal valve 10 follow the course of the cam on the camshaft 44 .
  • the stop disk 26 that is connected to the seal valve 10 comes into contact with the regulating slide valve 34 (state shown in FIG. 1 ).
  • the seal valve 10 can no longer follow the course of the cam on the camshaft 44 .
  • the gas exchange valve 12 lifts up from the seal valve 10 and air can travel into the combustion chamber.
  • Axial shifting of the position of the regulating slide valve 34 by means of an adjusting unit can be used to set when the sealing seat 28 of the gas exchange valve 12 lifts up from the sealing seat 30 of the seal valve 10 .
  • This advantageously makes it possible to regulate the opening cross section of the gas exchange valve 12 and consequently also the quantity of the air traveling into the combustion chamber 32 .
  • the hydraulic adjusting unit of the seal valve 10 which is shown in the form of a connection diagram in FIG. 3 , functions as follows:
  • the regulating piston 46 is connected to the regulating slide valve 34 and, like it, can slide in the axial direction of the valve shaft 14 of the gas exchange valve 12 .
  • the sliding is executed with the aid of a hydraulic fluid, which travels under a particular pressure into the working cylinder 52 of the adjusting unit in which the regulating piston 46 is contained in a sliding fashion.
  • FIG. 3 shows the regulating valve 44 of the adjusting unit in the first switched position A.
  • hydraulic fluid can travel out of the working cylinder 52 via the return line 56 into the oil tank 48 .
  • the prestressing force of the coupling spring 24 acts on the regulating slide valve 34 and presses it downward as long as the regulating valve 44 , is in the first switched position A.
  • a preferred embodiment of the invention provides that the regulating valve 44 can be electrically triggered.
  • the regulating valve 44 is designed so that it is always in the first switched position A without a being supplied with current. This results in the fact that when the regulating valve 44 is without current, the regulating piston 46 is pressed downward and consequently sets the opening cross section of the gas exchange valve 12 to the minimal possible value.
  • the regulating valve 44 of the adjusting unit of the seal valve 10 shown in FIG. 4 functions as follows:
  • the hydraulic fluid travels via the pressure connection 60 into the housing 88 of the regulating valve 44 .
  • the prestressing force of the spring 78 presses the stop 82 connected to the adjusting pin 90 against the support 86 of the housing 88 .
  • the first driver disk 64 lifts the first seal valve 68 , which is movably supported on the adjusting pin 90 , up from the sealing seat 74 of the housing 88 .
  • the spring 88 presses the second seal valve 70 against the sealing seat 76 of the sealing seat support 72 of the regulating valve 44 .
  • the fluid can travel from the working cylinder 52 of the adjusting unit, through the cylinder connection 62 , and into the return line 56 . At the same time, the connection between the pressure connection 60 and the cylinder connection 62 is closed. This corresponds to the first switched position A according to FIG. 3 .
  • the stroke drive unit 84 whose design is known per se to one skilled in the art and is therefore not shown in detail, can exert a force on the adjusting pin 90 in the axial direction.
  • the exertion of a particular force of the stroke drive unit 84 on the adjusting pin 90 causes the adjusting pin 90 to move in the axial direction.
  • the force of the stroke drive unit 84 that must be exerted in order to bring about this movement depends respectively on the prestressing forces of the spring 78 and the compression spring 80 against which the stroke drive unit 84 must work.
  • the switched position B of the regulating valve 44 ( FIG. 3 ) is achieved by selecting the drive force of the stroke drive unit 84 so that the adjusting pin 90 moves until the compression spring 80 presses the first seal valve 68 against the first sealing seat 74 . In this case, the second driver disk 66 has not yet lifted the second seal valve 70 up from the sealing seat 76 of the sealing seat support 72 . In this switched position B of the regulating valve 44 , the two connections are closed so that no hydraulic fluid can flow.
  • the invention advantageously makes it possible to regulate the opening cross sections of the gas exchange valves 12 of an internal combustion engine either individually or in groups through the use of one adjusting unit.
  • the embodiment according to the invention is particularly inexpensive.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
US10/399,656 2001-08-21 2002-07-12 Valve mechanism with a variable valve opening diameter Abandoned US20050217622A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE101-40-919.2 2001-08-21
DE10140919A DE10140919A1 (de) 2001-08-21 2001-08-21 Ventilmechanismus mit einem variablen Ventilöffnungsquerschnitt
PCT/DE2002/002550 WO2003018965A1 (de) 2001-08-21 2002-07-12 Ventilmechanismus mit einem variablen ventilöffnungsquerschnitt

Publications (1)

Publication Number Publication Date
US20050217622A1 true US20050217622A1 (en) 2005-10-06

Family

ID=7696105

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/399,656 Abandoned US20050217622A1 (en) 2001-08-21 2002-07-12 Valve mechanism with a variable valve opening diameter

Country Status (6)

Country Link
US (1) US20050217622A1 (de)
EP (1) EP1421260A1 (de)
JP (1) JP2005500460A (de)
KR (1) KR20040030160A (de)
DE (1) DE10140919A1 (de)
WO (1) WO2003018965A1 (de)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3640589A (en) * 1969-12-30 1972-02-08 Nippon Denso Co Automatic antiskid braking system
US3881459A (en) * 1974-02-28 1975-05-06 Werner Gaetcke Inlet valve for internal combustion engine and method for supplying fuel thereto
US4901683A (en) * 1988-05-12 1990-02-20 Huff Reggie D Vented valve for internal combustion engines
US6766778B2 (en) * 2001-08-21 2004-07-27 Robert Bosch Gmbh Valve mechanism with a variable valve opening cross-section

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2636519A1 (de) * 1976-08-13 1978-02-16 Daimler Benz Ag Brennkraftmaschine mit einem durch ein einlass- und zusatzventil steuernden einlassquerschnitt
RO74461A2 (ro) * 1978-09-26 1983-02-01 Intreprinderea De Autoturisme,Ro Dispozitiv pentru modificarea fazelor de distributie la motoarele cu ardere interna
DE3150533A1 (de) * 1981-12-21 1983-07-07 Salzgitter Maschinen Und Anlagen Ag, 3320 Salzgitter Vorrichtung zur regelung eines hydrostatischen antriebs
US4777915A (en) 1986-12-22 1988-10-18 General Motors Corporation Variable lift electromagnetic valve actuator system
DE3939065A1 (de) 1989-11-25 1991-05-29 Bosch Gmbh Robert Hydraulische ventilsteuervorrichtung fuer brennkraftmaschinen
FR2665926B1 (fr) 1990-08-17 1994-07-01 Renault Dispositif d'actionnement pour soupape notamment dans un moteur a combustion interne.
GB2248471A (en) 1990-10-04 1992-04-08 Ford Motor Co I.c.engine poppet valve guide and variable throttle
US5159906A (en) 1991-05-03 1992-11-03 Ford Motor Company Adjustable valve system for an internal combustion engine
IT1290225B1 (it) * 1997-01-31 1998-10-22 Voith Riva Hydro S P A Valvola idraulica e relativo impianto elettro-idraulico per il comando degli organi di regolazione di turbine idrauliche

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3640589A (en) * 1969-12-30 1972-02-08 Nippon Denso Co Automatic antiskid braking system
US3881459A (en) * 1974-02-28 1975-05-06 Werner Gaetcke Inlet valve for internal combustion engine and method for supplying fuel thereto
US4901683A (en) * 1988-05-12 1990-02-20 Huff Reggie D Vented valve for internal combustion engines
US6766778B2 (en) * 2001-08-21 2004-07-27 Robert Bosch Gmbh Valve mechanism with a variable valve opening cross-section

Also Published As

Publication number Publication date
KR20040030160A (ko) 2004-04-08
EP1421260A1 (de) 2004-05-26
WO2003018965A1 (de) 2003-03-06
JP2005500460A (ja) 2005-01-06
DE10140919A1 (de) 2003-03-20

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AS Assignment

Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HAMMER, UWE;REEL/FRAME:014563/0009

Effective date: 20030527

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION