EP1415070B1 - Vorrichtung zur steuerung von gaswechselventilen - Google Patents

Vorrichtung zur steuerung von gaswechselventilen Download PDF

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Publication number
EP1415070B1
EP1415070B1 EP02745076A EP02745076A EP1415070B1 EP 1415070 B1 EP1415070 B1 EP 1415070B1 EP 02745076 A EP02745076 A EP 02745076A EP 02745076 A EP02745076 A EP 02745076A EP 1415070 B1 EP1415070 B1 EP 1415070B1
Authority
EP
European Patent Office
Prior art keywords
valve
valves
control
gas exchange
case
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.)
Expired - Lifetime
Application number
EP02745076A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1415070A1 (de
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
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1415070A1 publication Critical patent/EP1415070A1/de
Application granted granted Critical
Publication of EP1415070B1 publication Critical patent/EP1415070B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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

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 In a known device of this type (DE 198 26 047 A1) is each valve actuator, the actuator piston is integrally connected to the valve stem of the associated gas exchange valve, with its first working space constantly connected to a high pressure source and its second working space on the one hand to a supply to the High pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a discharge line alternately releasing or closing second control valve.
  • the electrical control valves are designed as 2/2-way solenoid valves with spring return. With de-energized control valves, the first working space is still under high pressure, while the second working space is disconnected from the high pressure source and connected to the relief line. The gas exchange valve is closed. To open the gas exchange valve both control valves are energized.
  • the second working space of the valve actuator is on the one hand blocked by the second control valve with respect to the discharge line and on the other hand connected by the first control valve with the supply line to the high pressure source.
  • the gas exchange valve opens, wherein the size of the opening stroke depends on the formation of the voltage applied to the first electric control valve electrical control signal and the opening speed of the pressure supplied by the high pressure source.
  • the first control valve is then de-energized, so that it shuts off the supply line to the second working space of the valve actuator. In this way, all valve opening positions of the gas exchange valve can be adjusted by means of an electrical control unit for generating control signals.
  • two electrical control valves are required in each case, which act on the associated valve actuator according to hydraulic pressure.
  • the inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by the use of a composed of a first and a second electrical control valve control valve pair for the alternating control of total two valve actuators two electrical control valves per valve pair can be saved. Since the electrical control valves designed primarily as 2/2-way solenoid valves must realize extremely short switching times, in practice about 0.3 ms with an opening cross-section of 3 mm 2 , such control valves are very expensive, so that the reduction of the number of control valves in the control device brings a significant cost savings. Due to the smaller number of electrical control valves, the number of power amplifiers and the amount of electrical wiring for the control of the control valves is reduced, which leads to a further cost savings.
  • the switching of the control valves by means of two trained as 3/2-way valves switching valves is made, of which three controlled valve connections of the first with the first and second electrical control valve is connected and the two alternately alsschaltbaren on the first valve port further valve connections are connected to the second working spaces of the two valve actuators.
  • Simple change-over valves which can be controlled electrically or hydraulically, are very inexpensive as mass-produced articles, especially when no fast switching times are required.
  • the common closed state of two gas exchange valves in combustion cylinders with a 360 ° crank angle offset their ignition extends over a crank angle range of about 60 °, is a sufficiently large period of time for the reversal of the changeover valves available.
  • the switching valves are, especially if they are hydraulically controlled, compared to the 2/2-way solenoid valves quite small, so that also reduces the space required for the valve control device space requirement compared to the known valve control.
  • the invention is at the control input of the hydraulically controlled changeover valves' permanently on a hydraulic pressure, which is increased for reversing the change-over valves in their working position by means of a reciprocating piston.
  • the reciprocating piston can be driven by a cam which rotates with respect to the rotational speed of the crankshaft and can be driven to rotate in a pressure chamber communicating with the respective control input.
  • the illustrated in the circuit diagram in Fig. 1 apparatus for controlling gas exchange valves in combustion cylinders of an internal combustion engine is used to control a total of four gas exchange valves 10 (Fig. 2), of which one is arranged in a combustion cylinder of a four-cylinder four-stroke engine.
  • the gas exchange valves 10 may be the intake valves or the exhaust valves of the combustion cylinders.
  • the combustion cylinders, not shown here are symbolic with I, II, III and IV, which are assigned in Fig. 1 the valve actuators 11 for the gas exchange valves 10 of the respective combustion cylinder.
  • the device has a total of four hydraulic valve actuator 11, one of which is associated with 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 axially displaceable.
  • the actuating piston 13 divides the working cylinder 12 in two limited by him, hydraulic working spaces 121 and 122 and is fixedly connected to the valve stem 14 of the gas exchange valve 10.
  • a valve plate 11 is shown schematically in conjunction with a gas exchange valve 10 in an enlarged view.
  • the valve stem 14 carries at its end remote from the actuating piston 13 a plate-shaped valve sealing surface 15 which cooperates to control an opening cross section with a formed on the housing 16 of the combustion cylinder of the engine valve seat surface 17.
  • the 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 a hydraulic connection 121a in the first working space 121.
  • the device further comprises 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.
  • 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 tapped between the check valve 20 and the memory 21 output 221 of Pressure supply device 22 is connected via a line 23 to all hydraulic ports 121a of the four valve actuators 11, so that the first working chambers 121 of the valve plate 11 are constantly acted upon by the output 221 of the pressure supply device 22 pending hydraulic pressure.
  • the second working chambers 122 of the working cylinders 12 are connected on the one hand via first electrical control valves 24 and 26 to the output 221 of the pressure supply device 22 and on the other hand via second electrical control valves 25 and 27 to a discharge 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 control valve pair, with the respective two valve actuators 11 are controlled alternately.
  • 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 combustion cylinders of this type whose ignition times are offset by 360 ° crank angle from one another.
  • 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, the valve plate 11 for the gas exchange valves 10 in the second and fourth combustion cylinder II and IV, wherein the control of each two valve actuator 11 takes place alternately and the switching of the control valve pair 24, 25 or 26, 27 of the one valve actuator 11 to the other valve actuator 11 during the closed state of the two of the Valve actuators 11 actuated gas exchange valves 10 is performed.
  • the Umschaltüng the two control valves 24 and 25 or 26 and 27 of each control valve pair is synchronous.
  • switching valves 30 - 33 For switching the two control valve pairs 24, 25 and 26, 27 of the one valve actuator 11 to the other valve actuator 11 is effected by switching valves 30 - 33, which are formed in the embodiment of FIG. 1 as a hydraulically controlled 3/2-way valves with spring return.
  • Each switching valve 30-33 has two switching positions and three controlled valve ports 34-36, of which the first valve port 34 is connected to the respective associated control valves 24 and 25 or 26 and 27 and the two connectable to the first valve port 34 further valve ports 35th and 36 are connected to the second working spaces 122 of the valve actuator 11.
  • the first valve port 34 to the first control valve 24, the second valve port 25 to the second working chamber 122 of the valve actuator 11 for the first combustion cylinder I and the second valve port 36 to the second working space 122 of the valve actuator 11 for the third combustion cylinder III connected.
  • the first valve port 34 of the switching valve 31 is connected to the second control valve 25, the second valve port 35 to the second working space 122 of the valve actuator 11 for the first combustion cylinder I and the third valve port 36 to the working space 122 of the valve actuator 11 for the third combustion cylinder III.
  • the control of the changeover valves 30-33 is hydraulically against the spring force of a return spring, to which the control inputs of the changeover valves 30 and 31 via a check valve 37 and the control inputs of the changeover valves 32 and 33 are connected via a check valve 38 to the outlet of the prefeed pump 29.
  • the switching valves 30-33 are designed so that they can not be moved out of their rest position shown in Fig. 1 by the pending at the outlet of the prefeed pump 29 hydraulic pressure.
  • the hydraulic pressure at the control inputs of the changeover valves 30-34 is increased by means of a reciprocating piston 40 and 41.
  • Each reciprocating piston 40 and 41 defines a fluid-filled pressure chamber 42 or 43 communicating with the outlet of the prefeed pump 29 and is driven by a cam 44 or 45 for lifting 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 run at half the speed of the crankshaft, with each cam rotation of the voltage applied to the control inputs hydraulic pressure from the pressure level at the outlet of the feed pump 29 increases to a required to switch the switching valves 30 - 33 maximum pressure and back to the original pressure level is reduced.
  • By moving the pistons 41 and 42 in Fig. 1 upwards the pressure is increased and the associated changeover valves 30 - 33 switch over.
  • the provision of the piston 41, 42 takes place by the restoring force of the return springs of the changeover valves and by the permanently applied pressure of the prefeed pump 29.
  • the prefeed pump 29 also provides for the compensation of leakage losses.
  • Fig. 3 respectively shows the valve lift in dependence on the crank angle for the various valves.
  • Diagram a, b, f and g shows respectively the valve lift of the here intake valves forming gas exchange valves 10 in the first, third, second and fourth combustion cylinder I, III, II and IV, diagram c the valve lift of the changeover valves 30 31, diagram h the valve lift of 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 for closing the gas exchange valve 10 of the second working chamber 122 of the valve actuator 11 via the second electrical control valve 25 and 27 connected to the discharge line 28 and via the first electric control valve 24 and 26 is shut off from the outlet 221 of the pressure supply device 22.
  • pressure of 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 in Fig. 1 shown position within the working cylinder 12 of the valve actuator 11 a.
  • All control valves 24 - 27 are de-energized and assume their basic or rest position.
  • the second electric control valve 25 and 27 is transferred to its blocking position in which the second working space 122 is shut off from the discharge line 28, and the first electric control valve 24 and 26 is transferred to its working position, so that the second working space 122 is connected to the output 221 of the pressure supply device 22 and the system pressure is now present in the second working chamber 122 of the valve actuator 11. Since the piston area of the actuating piston 13, which delimits the first working space 121, is smaller than the area of the actuating piston 13, which delimits the second working space 122, a displacement force is produced which moves the actuating piston 13 in FIG. 1 to the right or in FIG moved down, whereby the gas exchange valve 10 is opened. The.
  • the size of the opening stroke of the gas exchange valve 10 is dependent on the opening duration and opening speed of the first control valve 24 and 26, respectively.
  • valve actuator 11 For the control of the gas exchange valve 10 in the combustion cylinder I associated valve actuator 11 are the switching valves 30, 31 in the rest or basic position A shown in Fig. 1, as shown in 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.
  • the switching valves 30, 31 and 32, 33 each have a crankangle range of approximately 300.degree. In position A and in position B. The corresponding changeover is effected by the cams 44, 45, which rotate at half crankshaft speed.
  • the changeover valves can not be operated hydraulically but electrically, the currentless changeover valve occupying position A and the energized changeover valve occupying position B or vice versa. It is also possible, in the described hydraulically controlled switching valves 30 - 33 instead of the spring return, a second hydraulic control input, counteracting the first.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)
EP02745076A 2001-07-24 2002-05-23 Vorrichtung zur steuerung von gaswechselventilen Expired - Lifetime EP1415070B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10136020A DE10136020A1 (de) 2001-07-24 2001-07-24 Vorrichtung zur Steuerung von Gaswechselventilen
DE10136020 2001-07-24
PCT/DE2002/001868 WO2003012263A1 (de) 2001-07-24 2002-05-23 Vorrichtung zur steuerung von gaswechselventilen

Publications (2)

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

Family

ID=7692908

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02745076A Expired - Lifetime EP1415070B1 (de) 2001-07-24 2002-05-23 Vorrichtung zur steuerung von gaswechselventilen

Country Status (7)

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007138057A1 (de) * 2006-05-26 2007-12-06 Robert Bosch Gmbh Verfahren zur steuerung des gaswechsels einer brennkraftmaschine
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
WO2015175213A1 (en) * 2014-05-12 2015-11-19 Borgwarner Inc. Crankshaft driven valve actuation
WO2016010732A1 (en) * 2014-07-16 2016-01-21 Borgwarner Inc. Crankshaft driven valve actuation using a connecting rod
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

Also Published As

Publication number Publication date
WO2003012263A1 (de) 2003-02-13
DE50209020D1 (de) 2007-02-01
US20040035379A1 (en) 2004-02-26
KR20040019331A (ko) 2004-03-05
DE10136020A1 (de) 2003-02-13
US6889639B2 (en) 2005-05-10
EP1415070A1 (de) 2004-05-06
JP2005508469A (ja) 2005-03-31
BR0205797A (pt) 2003-07-22

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