US20040144345A1 - Device for controlling charge exchange valves - Google Patents

Device for controlling charge exchange valves Download PDF

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Publication number
US20040144345A1
US20040144345A1 US10/473,528 US47352804A US2004144345A1 US 20040144345 A1 US20040144345 A1 US 20040144345A1 US 47352804 A US47352804 A US 47352804A US 2004144345 A1 US2004144345 A1 US 2004144345A1
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US
United States
Prior art keywords
valve
pressure
pump
recited
valves
Prior art date
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Abandoned
Application number
US10/473,528
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English (en)
Inventor
Udo Diehl
Bernd Rosenau
Simon Kieser
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ROSENAU, BERND, DIEHL, UDO, KIESER, SIMON
Publication of US20040144345A1 publication Critical patent/US20040144345A1/en
Abandoned legal-status Critical Current

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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 present invention is based on a device for controlling gas exchange valves according to the definition of the species in claim 1 .
  • each electrohydraulic valve actuator has an operating piston that acts on a gas-exchange valve, and two hydraulic working chambers that are delimited by the operating piston.
  • the first working chamber which acts on the gas-exchange valve in the closing direction, is constantly filled with a fluid under high pressure
  • the second working chamber which acts on the gas-exchange valve in the opening direction, is alternately able to be filled with, or relieved of, a working medium or fluid under high pressure via a first and a second electrical control valve.
  • a pressure-supply device delivers a fluid under high pressure, which is conveyed via the first electrical control valve to first working chamber, on the one hand, and to the second working chamber, on the other hand.
  • the second working chamber is connected to a return line leading back to the fluid reservoir by way of the second electrical control valve.
  • the pressure-supply device includes a working-pressure accumulator and a controlled variable displacement pump, which conveys fluid from a fluid reservoir to the working-pressure accumulator via a check valve.
  • the second working chamber In the closed state of the gas exchange valve, the second working chamber is separated from the pressure supply device by the closed first control valve, and connected to the return line through the open second control valve, so that the operating piston is displaced into its closed position by the fluid pressure prevailing in the first working chamber.
  • the control valves are switched over, so that the second working chamber is cut off from the return line and connected to the pressure supply device.
  • the operating piston While opening the gas exchange valve, the operating piston is displaced toward the first working chamber since the piston area of the operating piston is larger in the second working chamber than the effective area of the operating piston in the first working chamber, the length of the opening stroke depending on the formation of the electric control signal applied to the first control valve and the opening velocity depending on the fluid pressure controlled by the pressure supply device.
  • control valves switch over again, thereby connecting the second working chamber, which is blocked off from the pressure supply device, to the return line, and the fluid pressure prevailing in the first working chamber guiding the operating piston back into its valve-closed position, so that the gas exchange valve is closed by the operating piston.
  • the device according to the present invention for controlling gas exchange valves having the features of claim 1 , has the advantage that by dividing the pressure accumulator unit into two high-pressure accumulators for separately supplying of fluid to the valve actuators for the at least one intake valve, on the one hand, and for the at least one discharge valve, on the other hand, the fluid pressure in the two high-pressure circuits can be adapted for the intake and the discharge valve depending on the requirement for the degree of freedom allowed in the valve control by the electrohydraulic valve control, such as instant of valve actuation, lift, lift velocity and valve opening duration; and different pressure levels can be implemented.
  • Dividing the pressure-supply device into two separate high-pressure circuits for the intake valves and for the discharge valves as proposed by the present invention also allows the use of a constant displacement pump, which has a simple design, instead of the variable delivery pump, which has generally been used heretofore and has a technically more complicated design, thereby achieving a considerable savings effect in the production cost of the control device.
  • the known constant displacement pump is distinguished in that it generates a delivery or volumetric rate that is a function of only its driving speed, regardless of the delivery pressure.
  • the constant displacement pump may either be operated by an upstream delivery pump, for instance by the oil pump of the internal combustion engine, or it may be configured as a self-priming pump.
  • the switching member is provided for the alternate connecting of the two high-pressure accumulators to the constant displacement pump and is configured as a 4/3 directional solenoid control valve having spring resetting.
  • One of the three valve outlets of the solenoid valve is connected to one of the high-pressure accumulators and one is connected to the other high-pressure accumulator, and the third to the return line, while the valve inlet of the solenoid valve is connected to the pump outlet of the constant displacement pump.
  • FIG. 1 a circuit diagram of a device for controlling gas exchange valves for an internal combustion engine
  • FIG. 2 a detailed circuit diagram of an electrohydraulic valve actuator for actuating a gas-exchange valve in the control device according to FIG. 1.
  • the device for controlling gas-exchange valves shown as a circuit diagram in FIG. 1, controls a total of four intake valves 11 and a total of four discharge valves 12 of an internal combustion engine via an electronic control device 13 .
  • the number of intake valves 11 and discharge valves 12 may vary, however.
  • Each intake valve 11 and discharge valve 12 is arranged in a cylinder head 14 , shown in a cutaway view in FIG. 2, of a combustion cylinder and seals a combustion chamber formed in the combustion cylinder in a gastight manner.
  • each gas exchange valve has a valve seat 16 , which encloses an opening cross section 15 in cylinder head 14 , and a valve element 17 , which has a valve closure element 172 sitting on a valve shaft 171 that is guided so as to be axially displacable and cooperates with valve seat 16 to close and release opening cross section 15 .
  • valve closure element 172 lifts off from valve seat 16 or sets down on valve seat 16 .
  • each gas-exchange valve that is each intake valve 11 and each discharge valve 12 , is assigned an electrohydraulic valve actuator 18 for its actuation.
  • Electrohydraulic valve actuator 18 which is known per se, is illustrated in detail in FIG. 2. It includes a double-acting hydraulic working cylinder 19 and two electrical control valves 20 , 21 , which are preferably configured as 2/2 directional solenoid control valves having spring resetting. Electrical control valves 20 , 21 are controlled by electronic control device 13 .
  • hydraulic working cylinder 19 has a cylinder housing 22 and an operating piston 23 , which is connected to valve shaft 171 of a gas-exchange valve and guided in cylinder housing 22 so as to be axially displacable, the operating piston dividing the interior of cylinder housing 25 into a first working chamber 24 and a second working chamber 25 .
  • First working chamber 24 is connected directly, and second working chamber 25 via first electrical control valve 20 , to an hydraulic inlet 181 of valve actuator 18 .
  • Second working chamber 25 is connected to an hydraulic outlet 182 of valve actuator 18 via second electrical control valve 21 .
  • the mode of action of valve actuators 18 for opening and closing the associated gas-exchange valve is known and described in the introduction in the section “Background Information”.
  • the control device has a pressure-supply device 26 .
  • Pressure-supply device 26 includes a constant displacement pump 27 for generating high pressure, which is supplied from a fluid reservoir 29 by a presupply pump 28 ; a switching member 30 connected to the pump outlet of constant displacement pump 27 ; and two high-pressure accumulators 31 , 32 which, depending on the switching position of switching member 30 , are alternately able to be connected to the pump outlet of constant displacement pump 27 via a check valve 33 and 34 , respectively.
  • First high-pressure accumulator 31 is connected to a first outlet 261 of the pressure-supply device, and the second high-pressure accumulator to a second outlet 262 of pressure-supply device 26 .
  • each high-pressure accumulator 31 , 32 is connected to a pressure-relief valve 35 and 36 , respectively, whose valve outlet is connected to a return line 37 discharging into fluid reservoir 29 .
  • switching member 30 is configured as a 4/3 directional solenoid control valve 41 having spring resetting, which is triggered by electronic control device 13 .
  • a first valve outlet 412 having a check valve 33 interposed, is connected to first high-pressure accumulator 31
  • a second valve outlet 413 having check valve 34 interposed, to second high-pressure accumulator 32
  • a third valve outlet 414 is connected to return line 37 or directly to fluid reservoir 29 via a connecting line 42
  • valve inlet 411 is connected to the pump outlet of constant displacement pump 27 .
  • All electrohydraulic valve actuators 18 activating an intake valve 11 are connected to first output 261 of pressure-supply device 26 by way of their hydraulic input 181 and thus are connected to first high-pressure accumulator 31 .
  • All hydraulic outlets 182 of these valve actuators 18 are connected to return line 37 via a shared connecting line 38 .
  • All electrohydraulic valve actuators 18 for activating discharge valves 12 are connected to second input 262 of pressure-supply device 26 by way of their hydraulic inlets 181 and thus are connected to second high-pressure accumulator 32 .
  • Hydraulic outlets 182 of these valve actuators 18 are in turn connected to return line 37 via a shared connecting line 39 .
  • a check valve 43 and 44 may also be arranged in both connecting lines 38 and 39 , respectively, the check valves opening toward return line 37 .
  • Electrohydraulic valve actuators 18 for all gas-exchange valves i.e., for all intake valves 11 and all discharge valves 12
  • the actuating force that must be generated by valve actuators 18 for discharge valves 12 which is predefined by the combustion-chamber pressure, is considerably higher than the actuating force that valve actuators 18 must generate to actuate intake valves 11 .
  • These different forces are realized by different pressure levels in high-pressure accumulators 31 , 32 .
  • the different pressure levels are realized by an appropriate adjustment of pressure-relief valves 35 , 36 .
  • high-pressure accumulators 31 or high-pressure accumulator 32 are then tensioned by constant displacement pump 37 to the pressure level specified by respective pressure-relief valve 35 and 36 . Since high-pressure accumulator 31 is set to a lower pressure level, the energy required for pressure generation is reduced. If no fluid is drawn off from the two high-pressure circuits via valve actuators 18 , 4/3 directional solenoid control valve 41 is controlled to its intermediate position shown in FIG. 1, in which the fluid circulates without pressure via fluid reservoir 29 .
  • Constant displacement pump 27 may alternatively be configured as a self-priming pump. In this case, presupply pump 28 is omitted, and constant displacement pump 27 draws in fluid directly from fluid reservoir 29 .
  • the present invention is not limited to the described exemplary embodiment.
  • the number of intake valves 11 and discharge valves 12 operated by the control device may vary.
  • a so-called 3-valve operation is possible as well, in which each combustion chamber formed in a combustion cylinder of the internal combustion engine is assigned two intake valves 11 and one discharge valve 12 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US10/473,528 2002-01-29 2002-11-28 Device for controlling charge exchange valves Abandoned US20040144345A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10203275A DE10203275A1 (de) 2002-01-29 2002-01-29 Vorrichtung zur Steuerung von Gaswechselventilen
DE10203275.0 2002-01-29
PCT/DE2002/004365 WO2003064823A1 (fr) 2002-01-29 2002-11-28 Dispositif de commande de soupape de changement des gaz

Publications (1)

Publication Number Publication Date
US20040144345A1 true US20040144345A1 (en) 2004-07-29

Family

ID=7713253

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/473,528 Abandoned US20040144345A1 (en) 2002-01-29 2002-11-28 Device for controlling charge exchange valves

Country Status (6)

Country Link
US (1) US20040144345A1 (fr)
EP (1) EP1481148B1 (fr)
JP (1) JP2005516146A (fr)
KR (1) KR20040077808A (fr)
DE (2) DE10203275A1 (fr)
WO (1) WO2003064823A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11156134B2 (en) * 2017-05-22 2021-10-26 EMPA Eidgenössische Materialprüfungs-und Forschungsanstalt Hydraulic drive for accelerating and braking dynamically moving components

Families Citing this family (5)

* Cited by examiner, † Cited by third party
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
KR20040013033A (ko) * 2004-01-09 2004-02-11 (주)하이드로 메틱스 다수의 실린더와 유압축적기를 구비한 중앙집중식 가스밸브구동용 유압장치
US8602002B2 (en) 2010-08-05 2013-12-10 GM Global Technology Operations LLC System and method for controlling engine knock using electro-hydraulic valve actuation
DE102016213976B4 (de) * 2016-07-29 2018-07-05 Schaeffler Technologies AG & Co. KG Elektrohydraulischer Ventiltrieb eines Verbrennungsmotors
DE102016224772A1 (de) * 2016-12-13 2018-06-14 Bayerische Motoren Werke Aktiengesellschaft Hubkolbenbrennkraftmaschine

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4353286A (en) * 1979-07-17 1982-10-12 Mds Mannesmann Demag Sack Gmbh Hydraulic control system with a pipeline antiburst safety device for a double acting drive cylinder
US4833971A (en) * 1988-03-09 1989-05-30 Kubik Philip A Self-regulated hydraulic control system
US5478045A (en) * 1991-10-11 1995-12-26 Caterpillar Inc. Damped actuator and valve assembly
US5645030A (en) * 1995-08-04 1997-07-08 Daimler-Bauz Ag Motorbrake for a diesel engine
US6067946A (en) * 1996-12-16 2000-05-30 Cummins Engine Company, Inc. Dual-pressure hydraulic valve-actuation system
US6321703B1 (en) * 1998-06-12 2001-11-27 Robert Bosch Gmbh Device for controlling a gas exchange valve for internal combustion engines
US6408807B1 (en) * 2000-08-03 2002-06-25 Aisin Seiki Kabushiki Kaisha Variable valve timing system

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE69218971T2 (de) * 1991-06-24 1997-07-24 Ford Werke Ag Hydraulische Ventilsteuervorrichtung für eine Brennkraftmaschine
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
DE19816817A1 (de) * 1997-11-25 1999-10-21 Bayerische Motoren Werke Ag Hydraulische Betätigungsvorrichtung für ein Gaswechselventil einer Brennkraftmaschine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4353286A (en) * 1979-07-17 1982-10-12 Mds Mannesmann Demag Sack Gmbh Hydraulic control system with a pipeline antiburst safety device for a double acting drive cylinder
US4833971A (en) * 1988-03-09 1989-05-30 Kubik Philip A Self-regulated hydraulic control system
US5478045A (en) * 1991-10-11 1995-12-26 Caterpillar Inc. Damped actuator and valve assembly
US5645030A (en) * 1995-08-04 1997-07-08 Daimler-Bauz Ag Motorbrake for a diesel engine
US6067946A (en) * 1996-12-16 2000-05-30 Cummins Engine Company, Inc. Dual-pressure hydraulic valve-actuation system
US6321703B1 (en) * 1998-06-12 2001-11-27 Robert Bosch Gmbh Device for controlling a gas exchange valve for internal combustion engines
US6408807B1 (en) * 2000-08-03 2002-06-25 Aisin Seiki Kabushiki Kaisha Variable valve timing system

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11156134B2 (en) * 2017-05-22 2021-10-26 EMPA Eidgenössische Materialprüfungs-und Forschungsanstalt Hydraulic drive for accelerating and braking dynamically moving components

Also Published As

Publication number Publication date
DE10203275A1 (de) 2003-08-07
EP1481148B1 (fr) 2005-09-21
WO2003064823A1 (fr) 2003-08-07
EP1481148A1 (fr) 2004-12-01
DE50204351D1 (de) 2005-10-27
KR20040077808A (ko) 2004-09-06
JP2005516146A (ja) 2005-06-02

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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:DIEHL, UDO;ROSENAU, BERND;KIESER, SIMON;REEL/FRAME:015123/0028;SIGNING DATES FROM 20031031 TO 20031105

STCB Information on status: application discontinuation

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