EP1415070A1 - Dispositif de commande de soupapes de commutation des gaz - Google Patents

Dispositif de commande de soupapes de commutation des gaz

Info

Publication number
EP1415070A1
EP1415070A1 EP02745076A EP02745076A EP1415070A1 EP 1415070 A1 EP1415070 A1 EP 1415070A1 EP 02745076 A EP02745076 A EP 02745076A EP 02745076 A EP02745076 A EP 02745076A EP 1415070 A1 EP1415070 A1 EP 1415070A1
Authority
EP
European Patent Office
Prior art keywords
valve
valves
gas exchange
control
switching
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
Application number
EP02745076A
Other languages
German (de)
English (en)
Other versions
EP1415070B1 (fr
Inventor
Udo Diehl
Bernd Rosenau
Uwe Hammer
Volker Beuche
Peter Lang
Stefan Reimer
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
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1415070A1 publication Critical patent/EP1415070A1/fr
Application granted granted Critical
Publication of EP1415070B1 publication Critical patent/EP1415070B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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

Definitions

  • the invention relates to a device for controlling gas exchange valves in combustion cylinders of an internal combustion engine according to the preamble of claim 1.
  • each valve actuator the actuating piston of which is connected in one piece to the valve tappet of the associated gas exchange valve, is constantly connected to a high-pressure source with its first working chamber and, on the one hand, to a supply line to the one with its second working chamber High-pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a second control valve alternately releasing or closing a relief line.
  • the electrical control valves are designed as 2/2 solenoid valves with spring return. With de-energized control valves, the first work area is still under high pressure, while the second work space is separated from the high pressure source and connected to the relief line. The gas exchange valve is closed.
  • Both control valves are energized to open the gas exchange valve. Due to the switching control valves, the second working space of the valve actuator is blocked on the one hand by the second control valve with respect to the relief line and on the other hand connected to the supply line to the high pressure source by the first control valve.
  • the gas exchange valve opens, the size of the opening stroke depending on the formation of the electrical control signal applied to the first electrical control valve and the opening speed on the pressure applied by the high pressure source.
  • the first control valve is then switched off so that it shuts off the supply line to the second working area of the valve actuator. In this way, all valve opening positions of the gas exchange valve can be set by means of an electrical control device for generating control signals.
  • two electrical control valves are required, which act accordingly on the assigned valve actuator with hydraulic pressure.
  • the device according to the invention for controlling gas exchange valves with the features of claim 1 has the advantage that through the use of a control valve pair composed of an extreme and a second electrical control valve for the alternate actuation of the whole two valve actuators, two electrical control valves per pair of valve actuators can be saved. Since the electrical control valves, which are primarily designed as 2/2 solenoid valves, have to realize extremely short switching times, in practice approx. 0.3 ms with an opening cross section of 3 mm 2 , such control valves are very expensive, so that the number of control valves is reduced in the control device brings significant cost savings. The smaller number of electrical control valves also reduces the number of output stages and the amount of electrical wiring required to control the control valves, which leads to further cost savings.
  • the switching of the control valves is carried out by means of two switching valves designed as 3/2-way valves, three of which are controlled valve connections, the first of which is connected to the first or second electrical control valve and the two which can be connected alternately to the first valve connection further valve connections are connected to the second work spaces of the two valve actuators.
  • Simple switching valves that can 'be driven electrically or hydraulically, are bulk buying very cheap, especially if no quick
  • a permanent hydraulic pressure at the control input of the hydraulically controlled changeover valves which is increased by means of a reciprocating piston to change the changeover valves into their working position.
  • the reciprocating piston is for this purpose driven by a rotating with respect to the speed of the crankshaft halved speed cam for reciprocating movement in a standing with the respective control input in communication pressure chamber.
  • Fig. 1 is a circuit diagram of a device for controlling four in different
  • FIG. 2 shows a schematic representation of a gas exchange valve in a combustion cylinder of the internal combustion engine
  • FIG. 3 shows a diagram of the valve lift of various valves in the device according to FIG. 1 as a function of the crank angle.
  • the device shown in FIG. 1 for the control of gas exchange valves in combustion cylinders of an internal combustion engine serves to control a total of four gas exchange valves 10 (FIG. 2), one of which is arranged in a combustion cylinder of a four-cylinder, four-stroke internal combustion engine.
  • the gas exchange valves 10 can be the intake valves or the exhaust valves of the combustion cylinders.
  • the combustion cylinders, not shown here, are symbolic with 03/012263
  • valve actuators 11 for the gas exchange valves 10 of the respective combustion cylinder in FIG. 1.
  • the device has a total of four hydraulic valve actuators 11, each of which is assigned to a gas exchange valve 10 in the combustion cylinders I-IV.
  • Each valve actuator 11 has a working cylinder 12 in which an actuating piston 13 is guided so as to be axially displaceable.
  • the actuating piston 13 divides the working cylinder 12 into two hydraulic working spaces 121 and 122 defined by it and is firmly connected to the valve tappet 14 of the gas exchange valve 10.
  • a valve actuator 11 in connection with a gas exchange valve 10 is shown schematically in an enlarged representation in FIG. 2.
  • the valve tappet 14 carries at its end remote from the actuating piston 13 a plate-shaped valve sealing surface 15 which cooperates with a valve seat surface 17 formed on the housing 16 of the combustion cylinder of the internal combustion engine to control an opening cross section.
  • Working cylinder 12 has a total of three hydraulic connections, of which two hydraulic connections 122a and 122b open in the second working space 122 and one hydraulic connection 121a in the first working space 121.
  • the device also has a pressure supply device 22, which consists of a fluid reservoir 18, a prefeed pump 29, a high pressure pump 19, a check valve 20 and a memory 21 for pulsation damping and energy storage.
  • the output 221 of the tapped between the check valve 20 and the memory 21 Pressure supply device 22 is connected to all via a line 23. Hydraulic connections 121a of the four valve actuators 11 connected, so that the first working spaces 121 of the. Valve actuator 11 is constantly acted upon by the hydraulic pressure present at the outlet 221 of the pressure supply device 22.
  • the second working spaces 122 of the working cylinders 12 can be connected on the one hand via first electrical control valves 24 and 26 to the outlet 221 of the pressure supply device 22 and on the other hand via second electrical control valves 25 and 27 to a relief line 28, which in turn opens into the fluid reservoir 18.
  • All control valves 24 - 27 are designed as 2/2-way solenoid valves with spring return. In each case a first control valve 24 or 26 and a second
  • Control valve 25 and 27 form a pair of control valves with which two valve actuators 11 are alternately actuated.
  • the two valve actuators 11 controlled by the control valve pairs 24, 25 and 26, 27 are each associated with gas exchange valves 10 in those combustion cylinders whose ignition times are offset from one another by a crank angle of 360 °.
  • control valve pair 24, 25 controls the two valve actuators 11 of the gas exchange valves 10 in the first and third combustion cylinders I and III and the control valve pair 26, 27 controls the valve actuators 11 for the gas exchange valves 10 in the second and fourth combustion cylinders II and IV, whereby ' the control each of the two valve actuators 11 takes place alternately and the switching of the control valve pair 24, 25 or 26, 27 from one valve actuator 11 to the other valve actuator 11 during the closed state of the two of the Valve actuators 11 operated gas exchange valves 10 is performed.
  • the changeover of the two control valves 24 and 25 or 26 and 27 of each control valve pair • takes place synchronously.
  • changeover valves 30-33 are used, which in the exemplary embodiment in FIG. 1 are designed as hydraulically controlled 3/2-way valves with spring return.
  • Each changeover valve 30-33 has two switching positions and three controlled valve connections 34-36, of which the first valve connection 34 is connected to the respectively associated control valves 24 and 25 or 26 and 27 and the other two can be connected to the first valve connection 34
  • Valve connections 35 and 36 are connected to the second working spaces 122 of the valve actuator 11.
  • the second valve connection 25 with the second working chamber 122 of the valve actuator 11 is for the first
  • Combustion cylinder I and the second valve connection 36 are connected to the second working chamber 122 of the valve actuator 11 for the third "combustion cylinder III.
  • the first valve connection 34 of the changeover valve 31 is connected to the second control valve 25, the second valve connection 35 to the second working chamber 122 of the valve actuator 11 for the first combustion cylinder I and the third valve connection 36 are connected to the working space 122 of the valve actuator 11 for the third combustion cylinder III.
  • the switching valves 30-33 are controlled hydraulically against the spring force of a return spring, for which purpose the control inputs of the switching valves 30 and 31 are connected via a check valve 37 and the control inputs ' of the switching valves 32 and 33 via a check valve 38 are connected to the outlet of the pre-feed pump 29.
  • the changeover valves 30-33 are designed so that they cannot be moved out of their rest position shown in FIG. 1 by the hydraulic pressure present at the outlet of the prefeed pump 29.
  • the hydraulic pressure at the control inputs is controlled by means of a lifting piston 40 and 41
  • Changeover valves 30 - 34 enlarged.
  • Each reciprocating piston 40 or 41 delimits a fluid-filled pressure chamber 42 or 43 which is connected to the outlet of the prefeed pump 29 and is driven by a cam 44 or 45 for the stroke movement.
  • the pressure chamber 42 is connected to the control inputs of the changeover valves 30 and 31 and the pressure chamber 43 to the control inputs of the changeover valves 32, 33.
  • the two cams 44, 45 rotate at half the speed of the crankshaft, with each cam revolution the hydraulic pressure applied to the control inputs increasing from the pressure level at the outlet of the pre-feed pump 29 to a maximum pressure required for switching the changeover valves 30-33 and back to the original pressure level is reduced.
  • the pistons 41, 42 are reset by the restoring force of the return springs of the changeover valves and by the permanent pressure of the pre-feed pump 29.
  • the pre-feed pump 29 also compensates for leakage losses.
  • 3 shows the valve lift as a function of the crank angle for the various valves.
  • Diagrams a, b, f and g each show the valve lift of the gas exchange valves 10 forming intake valves in the first, third, second and fourth combustion cylinders I, III, II and IV, diagram c the valve lift of the changeover valves 30 31, diagram h the valve lift of the changeover valves 32 and 33, diagram d the valve lift of the control valve 24, diagram e the valve lift of the control valve 25, diagram i the valve lift of the control valve 26 and diagram k the valve lift of the control valve 27.
  • each gas exchange valve 10 is controlled by the associated valve actuator 11 in such a way that to close the gas exchange valve 10, the second working chamber 122 of the valve actuator 11 is connected to the relief line 28 via the second electrical control valve 25 or 27 and via the first electrical control valve 24 or 26 is blocked by the outlet 221 of the pressure supply device 22. Due to the system pressure prevailing in the first working chamber 121 of the valve actuator 11, the actuating piston 13 in FIG. 2 is shifted upward until the valve sealing surface 15 of the gas exchange valve 10 rests on the valve seat surface 17 on the housing 16 of the combustion cylinder of the internal combustion engine. The actuating piston 13 takes the Position shown in Fig. 1 within the working cylinder 12 of the valve actuator 11.
  • All control valves 24-27 are de-energized and assume their basic or rest position.
  • the second electrical control valve 25 or 27 is transferred into its blocking position, in which the second working space 122 is blocked off from the relief line 28, and the first electrical control valve 24 or 26 is transferred into its working position, so that the second working space 122 is connected to the outlet 221 of the pressure supply device 22 and the system pressure is now also present in the second working space 122 of the valve actuator 11. Since the piston area of the actuating piston 13, which delimits the first working chamber 121, is smaller than the area of the actuating piston 13, which delimits the second working chamber 122, one is created
  • Displacement force which moves the actuating piston 13 to the right in FIG. 1 or downwards in FIG. 2, which causes the
  • Gas exchange valve 10 is opened. The. The size of the opening stroke of the gas exchange valve 10 depends on the opening duration and opening speed of the first control valve 24 or 26.
  • the energization of the first control valve 24 or 26 is released and the first control valve 24 or 26 falls back into its blocking position.
  • the pressure in the second working space 122 is maintained, so that the gas exchange valve 10 maintains the opening stroke that has been occupied.
  • the second control valve 25 or 27 is then de-energized.
  • Diagram d shows the activation of the first control valve 24, diagram e the Activation of the second control valve 25.
  • Diagram i shows the activation of the first control valve 26 and diagram k the activation of the second control valve 27.
  • the first control valves 24 and 26 are blocked when de-energized while the second control valves 25, 27 are open when de-energized.
  • the changeover valves 30, 31 are in the rest or basic position A shown in FIG. 1, as shown by diagram c in FIG. 3.
  • the valve lift of the gas exchange valve 10 in the cylinder I as a function of the crank angle is shown in diagram a.
  • Gas change valve 10 the two changeover valves 30, 31 are reversed in their working position B.
  • the second working chamber 122 of the valve actuator 11 is connected to the two control valves 24, 25 for actuating the gas exchange valve 10 in the third combustion cylinder III.
  • the valve control process for the gas exchange valve 10 in the combustion cylinder III then proceeds in the same way as described above for the combustion cylinder I.
  • Diagram b shows the stroke of the gas exchange valve 10 in the combustion cylinder III as a function of the crank angle, while the changeover valves 30, 31 are in position B (diagram c).
  • the closing times of the gas exchange valves 10 in the combustion cylinders I and III which approximately corresponds to the ignition times in the combustion cylinders I and III, are offset by a crank angle of 360 °.
  • a maximum opening angle of the gas exchange valves 10 of about 240 ° stands for the changeover of the two changeover valves' 30, are closed in the crank angular range in both -the gas exchange valves 10 in the cylinder I and III 31, sufficient time is available.
  • This switching range is denoted by S in diagram c and covers approximately 60 ° crank angle.
  • the changeover valves 30, 31 and 32, 33 are each in a crank angle range of about 300 ° in position A and position B.
  • the corresponding switch is by the
  • Cams 44, 45 causes that rotate at half the crankshaft speed.
  • the changeover valves cannot be operated hydraulically but electrically, with the de-energized changeover valve in position A and the energized changeover valve in position B or vice versa. It is also possible, in the case of the hydraulically controlled changeover valves 30-33 described, instead of the

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

L'invention concerne un dispositif de commande de soupapes de commutation des gaz dans un moteur à combustion interne, présentant respectivement des régleurs hydrauliques (11) associés à une soupape de commutation, avec un piston de réglage (13) agissant sur la soupape de commutation, et deux espaces de travail hydrauliques (121, 122) délimités par le piston de réglage (13). La première chambre de travail (121) sollicitant la soupape de commutation (10) dans le sens de la fermeture, est remplie en permanence d'un fluide sous pression, et la seconde chambre de travail (122) sollicitant la soupape de commutation (10) dans le sens de l'ouverture, sont alternativement remplies de fluide sous pression et libérées, via une première et une seconde soupapes de commande électriques (24, 25 ou 26, 27). En vue de réduire le coût de fabrication, l'invention est caractérisée en ce que les deux régleurs de soupape (11) sont actionnés chacun, alternativement, par la même première et la même seconde soupape de commande (24 ou 26, 25 ou 27), et en ce que l'inversion des soupapes de commande (24, 25 ou 26, 27) s'effectue pendant la fermeture des deux soupapes de commutation des gaz (10) actionnées par lesdits régleurs de soupape (11).
EP02745076A 2001-07-24 2002-05-23 Dispositif de commande de soupapes de commutation des gaz Expired - Lifetime EP1415070B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10136020 2001-07-24
DE10136020A DE10136020A1 (de) 2001-07-24 2001-07-24 Vorrichtung zur Steuerung von Gaswechselventilen
PCT/DE2002/001868 WO2003012263A1 (fr) 2001-07-24 2002-05-23 Dispositif de commande de soupapes de commutation des gaz

Publications (2)

Publication Number Publication Date
EP1415070A1 true EP1415070A1 (fr) 2004-05-06
EP1415070B1 EP1415070B1 (fr) 2006-12-20

Family

ID=7692908

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02745076A Expired - Lifetime EP1415070B1 (fr) 2001-07-24 2002-05-23 Dispositif de commande de soupapes de commutation des gaz

Country Status (7)

Country Link
US (1) US6889639B2 (fr)
EP (1) EP1415070B1 (fr)
JP (1) JP2005508469A (fr)
KR (1) KR20040019331A (fr)
BR (1) BR0205797A (fr)
DE (2) DE10136020A1 (fr)
WO (1) WO2003012263A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007138057A1 (fr) * 2006-05-26 2007-12-06 Robert Bosch Gmbh Procédé de commande de l'échange gazeux d'un moteur à combustion interne
DE102006042912A1 (de) * 2006-09-13 2008-03-27 Volkswagen Ag Brennkraftmaschine mit gemischten Nockenwellen
DE102009046943A1 (de) * 2009-11-20 2011-05-26 Robert Bosch Gmbh Elektrohydraulischer Aktor
DE112015001762T5 (de) * 2014-05-12 2017-03-09 Borgwarner Inc. Kurbelwellengesteuerte Ventilbetätigung
CN106536875A (zh) * 2014-07-16 2017-03-22 博格华纳公司 使用连接杆的曲轴驱动阀致动
CN110689980A (zh) * 2019-11-01 2020-01-14 中核核电运行管理有限公司 钴同位素棒束水下应急抓取工具气控装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009695A (en) * 1972-11-14 1977-03-01 Ule Louis A Programmed valve system for internal combustion engine
JPS59170414A (ja) * 1983-03-18 1984-09-26 Nissan Motor Co Ltd 油圧式弁駆動装置
US5231959A (en) * 1992-12-16 1993-08-03 Moog Controls, Inc. Intake or exhaust valve actuator
US5497736A (en) * 1995-01-06 1996-03-12 Ford Motor Company Electric actuator for rotary valve control of electrohydraulic valvetrain
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
JP3622446B2 (ja) * 1997-09-30 2005-02-23 日産自動車株式会社 ディーゼルエンジンの燃焼制御装置
DE19826047A1 (de) 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO03012263A1 *

Also Published As

Publication number Publication date
WO2003012263A1 (fr) 2003-02-13
DE50209020D1 (de) 2007-02-01
US20040035379A1 (en) 2004-02-26
BR0205797A (pt) 2003-07-22
EP1415070B1 (fr) 2006-12-20
DE10136020A1 (de) 2003-02-13
US6889639B2 (en) 2005-05-10
JP2005508469A (ja) 2005-03-31
KR20040019331A (ko) 2004-03-05

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