EP1521902B1 - Dispositif pour commander des soupapes de changement des gaz - Google Patents

Dispositif pour commander des soupapes de changement des gaz Download PDF

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Publication number
EP1521902B1
EP1521902B1 EP03717127A EP03717127A EP1521902B1 EP 1521902 B1 EP1521902 B1 EP 1521902B1 EP 03717127 A EP03717127 A EP 03717127A EP 03717127 A EP03717127 A EP 03717127A EP 1521902 B1 EP1521902 B1 EP 1521902B1
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EP
European Patent Office
Prior art keywords
valve
working chamber
iia
iib
valves
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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
EP03717127A
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German (de)
English (en)
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EP1521902A1 (fr
Inventor
Udo Diehl
Bernd Rosenau
Christian Grosse
Simon Kieser
Ralph Engelberg
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1521902A1 publication Critical patent/EP1521902A1/fr
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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
    • 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 (see EP-A-647 770 ).
  • each valve actuator whose actuating piston is preferably integrally connected to the valve stem of the associated gas exchange valve, constantly connected to its first working space with a high-pressure fluid fluid source and its second working space on the one hand to a supply line to the fluid pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a leading to a fluid reservoir discharge line alternately releasing or closing second electric control valve.
  • the electrical control valves are designed as 2/2-way solenoid valves with spring return.
  • Gas exchange valve takes the actuator piston of the valve actuator due to the permanently connected to the fluid pressure source first working space and separated by the first electrical control valve from the fluid pressure source and connected by the second electrical control valve with the discharge line second working space a basic position.
  • both electrical control valves are switched.
  • Characterized the second working space of the valve actuator is on the one hand blocked by the second electrical control valve with respect to the discharge line and on the other hand connected by the first electric control valve to the supply line to the fluid pressure source. Since the actuating piston surface delimiting the second working chamber in the valve actuator is greater than the actuating piston surface delimiting the first working chamber, the actuating piston moves out of its basic position while reducing the volume of the first working chamber and thereby opens the gas exchange valve.
  • the size of the opening stroke depends on the configuration of the electric control signal applied to the first electric control valve, and the opening speed depends on the fluid pressure supplied from the fluid pressure source.
  • the first electric control valve is then switched so that it shuts off the supply line to the second working space of the valve actuator. In this way, all opening positions of the gas exchange valve can be adjusted by means of an electrical control device for generating control signals.
  • the closing of the gas exchange valve is carried out by resetting the second electrical control valve in its open position, so that the first working space of the valve actuator back to the Relief line is connected.
  • two electrical control valves are required in each case act on the second working space of the associated valve actuator in accordance with fluid pressure or depressurize.
  • the inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by replacing a first electric control valve of a valve actuator in the valve actuator pair by a simple switching valve, via which the fluid pressure in the second working space by means of the second working space of the other Controlled valve actuator pending fluid pressure, the number of electrical control valves per valve pair is reduced.
  • a second electrical control valve in the valve actuator pair replaced by a simple check valve that connects the second working space of a valve actuator with the second valve control valve associated second electrical control valve, so can be saved per valve actuator pair two solenoid valves.
  • the switching valve is arranged in a connecting line between the second working spaces of the two valve actuators of the valve actuator pair. If this is either electromotive, electromagnetically or hydraulically actuated, designed as a 2/2-way valve switching unlocked, the second working space of a valve actuator is supplied via the second working space of the other valve actuator with fluid pressure and thus the actuator piston of the valve actuator in the direction of opening the gas exchange valve , By a suitable choice of the timing of the unlocking of the switching valve can different opening times of the actuated by this valve actuator gas exchange valve can be realized or this gas exchange valve can be kept closed if necessary.
  • the only first electrical control valve in the valve actuator pair must be designed so that in extreme cases, it can provide the total volume flow that both valve actuators of a valve actuator pair need to perform a simultaneous or staggered but always parallel stroke.
  • By controlling the second electrical control valves different closing times can be realized on both gas exchange valves. If, as noted above, one of the two second electrical control valves replaced by a check valve, the closing of the gas exchange valves is effected at the same time.
  • the changeover valve is a hydraulically operated 2/2-way valve with two hydraulic control inputs and is designed so that a valve unlocking occurs only when both control inputs.
  • One control input is connected to the second working space connected to the single first electrical control valve and the other control input is connected to the outlet of a further switching valve acted on the input side by a fluid pressure.
  • the second working space of the valve actuator connected to the changeover valve is connected directly to the fluid pressure source via the changeover valve. As soon as the only first electric control valve is actuated, the fluid pressure which it supplies into the second working space is also applied to the one control input of the changeover valve.
  • the unlocking of the switching valve can then at any time by applying the second control input are performed wherein flows with switching of the switching valve fluid directly from the fluid pressure source into the second working space of the other valve actuator.
  • This embodiment has the advantage that the only first electric control valve in the valve pair to be dimensioned only for the supply of a single valve actuator and not the entire amount of fluid must switch to control both valve actuator.
  • discontinuities in the lifting movement of a valve actuator which can be caused during the stroke of its actuating piston by the connection of the other valve actuator and by the thus occurring, additional fluid requirement of the second working chamber of the subsequent valve actuator, avoided.
  • all switching valves of the existing valve pairs are unlocked with the further switching valve, so that only a single further switching valve is present in the device, which brings advantages in terms of reducing manufacturing costs and space with it.
  • the application of the further switching valve with fluid pressure is effected by the fact that the valve inlet is connected via a check valve to the connected to the single first electrical control valve second working space of the valve pair.
  • the pressurization of the further switching valve can also be effected by an external fluid pressure source, for example the low-pressure circuit of the internal combustion engine.
  • Fig. 1 shown in the diagram device for controlling gas exchange valves in combustion cylinders of an internal combustion engine is for the control of a total of eight gas exchange valves 10, such as one in Fig. 3 schematically outlined, each of which are 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 in the combustion cylinders act.
  • the device comprises a plurality of hydraulic valve actuators 11, in the exemplary embodiment a total of eight valve actuators 11, of which one each actuates a gas exchange valve 10.
  • 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 pressure or working spaces 121 and 122 and is fixedly connected to a valve tappet 14 of the gas exchange valve 10.
  • Fig. 3 is a schematic representation of a valve actuator 11 in conjunction with an open gas exchange valve 10 is shown in enlarged scale.
  • the valve stem 14 carries at its end remote from the actuating piston 13 a valve sealing surface 15 which cooperates to control an opening cross-section with a formed in the cylinder head 16 of the combustion cylinder of the internal combustion engine valve seat surface 17.
  • the working cylinder 12 has a total of three hydraulic connections, of which two hydraulic ports 122a and 122b in the upper pressure chamber or second working space 122 and a hydraulic connection 121a in the lower pressure chamber or first working space 121 open.
  • the device further has a pressure supply device 20, whose output 201 forms a fluid pressure source for feeding the valve actuator 11.
  • the pressure supply device 20 comprises a high-pressure pump 21, which promotes fluid from a fluid reservoir 18, a discharge valve 22 arranged on the outlet side of the high-pressure pump 21 and a storage 23 for pulsation damping and energy storage.
  • the output 201 of the pressure supply device 20, which is tapped between the check valve 22 and the memory 23, is connected via a line 24 with the Hydraulic connections 121a of the first working spaces 121 connected in all of the total of eight valve actuators 11, so that the first working spaces 121 of the valve plate 11 are constantly applied to the output 201 of the pressure supply means 20 pending, high fluid or hydraulic pressure.
  • valve actuators 11 Of the total of eight existing valve actuators 11, two valve actuators 11 are combined to form a pair of valve actuators each controlling two intake valves or two exhaust valves in the same combustion cylinder.
  • the assigned combustion cylinder is in Fig. 1 symbolized by dotted border 19 of the valve actuator pair with the associated control means.
  • the valve actuators 11 of a valve actuator pair are referred to below as 11a and 11b, and the description is restricted to a valve actuator pair associated with a combustion cylinder. However, it applies equally to the remaining three valve pairs associated with the remaining combustion cylinders.
  • the fluid connection 122a of the second working space 122 of the valve actuator 11a is connected to the line leading to the output 201 of the pressure supply device 20 via a first electrical control valve 25, which is designed as a 2/2-way solenoid valve with spring return, while the fluid connection 122b of the second Working space 122 of the valve actuator 11 a to a second electrical control valve 26, which is also designed as a 2/2-way solenoid valve with spring return is set.
  • the second electrical control valve 26 opens at an opening in the fluid reservoir 18 Return line 27 connected.
  • the fluid port 122a of the second working chamber 122 of the valve actuator 11b is connected to the fluid port 122b on the valve actuator 11a via a connecting line 28 in which a hydraulically releasable switching valve 29 is arranged with spring return.
  • the fluid port 122b of the second working space 122 of the valve actuator 11b is also connected via a check valve 30 to the inlet of the second electrical control valve 26.
  • the switching valve 29 has a hydraulic control input 291 which is connected via a control line 31 at the outlet of an electromagnetically actuated further switching valve 32.
  • the further switching valve 32 is connected via a check valve 33 to the second working chamber 122 of the valve actuator 11a.
  • the inlet side of the further switching valve 32 may also be connected to the outlet 201 of the pressure supply device 20 or to a low-pressure circuit of the internal combustion engine.
  • the outlet side of the further switching valve 32 is placed over corresponding control lines 31 to all control inputs 291 of the switching valves 29 for all valve actuator pairs. Is the switching valve 32 as in the embodiment of Fig.
  • valve actuators 11a and 11b of a valve actuator pair assume their basic position in which the first electrical control valve 25 shuts off the second working chamber 122 of the valve actuator 11a from the outlet 201 of the pressure supply device 20 and the second electrical control valve 26 closes the second working chamber 122 of the valve actuator 11a connects to the return line 27.
  • the second working space 122 of the valve actuator 11b is also connected to the return line 27 via the check valve 30 and the opened second electrical control valve 26.
  • the two changeover valves 29, 32 take their blocking position by the return action of their return springs.
  • the control valves 25, 26 are de-energized and the switching valve 29 is depressurized.
  • the second electrical control valve 26 is first transferred to its closed or shut-off position, so that the two second working chambers 122 of the two valve actuators 11a and 11b are completed.
  • the relief valve 35 is in his closed position transferred.
  • the first electrical control valve 25 is transferred to its working or open position, so that the second working chamber 122 of the valve actuator 11a is connected to the pressure supply device 20 and the available at the output 201 of the pressure supply device 20 system pressure is now present in the second working chamber 122 of the valve actuator 11a , Since the piston surface of the actuating piston 13, which limits the first working space 121, is smaller than the piston surface of the actuating piston 13, which limits the second working space 122, a displacement force is generated which causes the actuating piston 13 in FIG Fig. 1 moved to the right, whereby the gas exchange valve 10 is opened.
  • the size of the opening stroke of the gas exchange valve 10 is dependent on the opening duration and opening speed of the first electric control valve 25.
  • the first electrical control valve 25 is switched again (in the embodiment of Fig. 1 de-energized), so that it separates the second working space 122 of the valve actuator 11a from the line 24 to the pressure supply device 20.
  • the second electrical control valve 26 is also switched over (in the embodiment of FIGS Fig. 1 de-energized), so that it connects the working spaces 122 of the two valve actuators 11a and 11b to the return line 27. Due to the system pressure in the first working spaces 121 of the valve actuators 11a and 11b, the actuating pistons 13 in the working cylinders 12 of the two valve actuators 11a and 11b become in the Fig. 1 shown basic position, whereby the gas exchange valves 10 are closed with the same closing times.
  • the check valve 30 is replaced by another second electrical control valve 26, which is also designed as a 2/2-way solenoid valve and the inlet side of the second working chamber 122 of the valve actuator 11 b and outlet side to connect directly to the return line 27.
  • an electric or electromagnetic unlockable changeover valve can also be used.
  • the further switching valve 32 can also be replaced by an electric actuator that unlocks all reversing valves 29 directly by electric motor or also hydraulically.
  • Fig. 2 partially shown device for controlling gas exchange valves in combustion cylinders of an internal combustion engine is compared to the Fig. 1 described insofar as the local switching valve 29 is replaced with connecting line 28 between the second working chambers 122 of the two valve actuators 11a and 11b by a hydraulically controlled changeover valve 34, via which the second working chamber 122 of the valve actuator 11b directly to the line 24 to the output 201th the pressure supply device 20 is connected.
  • the control valve designed as "AND gate" control valve 34 has two hydraulic control inputs 341, 342, which must be acted upon for switching the change-over valve 34 both with a hydraulic pressure.
  • the switching valve 34 still has a hydraulic return input 343, which is used to transfer the switching valve 34 in the in Fig.
  • the electrically controlled switching valve 32 is designed here as a 3/3-way solenoid valve with spring return, the second valve outlet is connected to the fluid reservoir 18. Depending on the switching position of the 3/3-way solenoid valve, pressure can be built up in the control line 31, pressure maintained or pressure reduced.
  • the switching valve 32 may also but as in Fig. 1 be designed as a 2/2-way solenoid valve. In this case, as well as in Fig. 1 still vorzuhalten the designed as a 2/2-way solenoid valve relief valve 35.
  • the switching device according to Fig. 2 unchanged, so that the same components are provided with the same reference numerals.
  • the switching valve 34 can be unlocked by driving the other switching valve 32.
  • the switching valve 34 With the unlocking of the switching valve 34, fluid flows directly from the conduit 24 into the second working chamber 122 of the valve actuator 11b, and the actuating piston 13 in the working cylinder 12 of the valve actuator 11b is displaced in a parallel stroke to the actuating piston 13 in the working cylinder 12 of the valve actuator 11a that the gas exchange valve 10 actuated by the valve actuator 11b is opened accordingly.
  • the first electric control valve 25 must be dimensioned only for the supply of the valve actuator 11a with fluid, since the valve actuator 11b directly from the pressure supply device 20 is fed. At the same time discontinuities in the lifting movement of the valve actuator 11 a are avoided, which in the control device according to Fig. 1 can be caused by the additional fluid requirement of the valve actuator 11b during the connection of the valve actuator 11b during the stroke of the valve actuator 11a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Flow Control (AREA)

Claims (11)

  1. Dispositif pour commander des soupapes d'échange de gaz (10) dans des cylindres de combustion d'un moteur à combustion interne, comprenant à chaque fois des dispositifs hydrauliques de réglage de soupape (11) associés à une soupape d'échange de gaz (10), qui présentent chacun un piston de commande (13) agissant sur la soupape d'échange de gaz (10) et deux espaces de travail hydrauliques (121, 122) limités par le piston de commande (13), dont le premier espace de travail (121) sollicitant la soupape d'échange de gaz (10) dans la direction de fermeture est rempli d'un fluide constamment sous pression par connexion à une source de pression de fluide (201) et dont le deuxième espace de travail (122) sollicitant la soupape d'échange de gaz (10) dans la direction d'ouverture peut être rempli avec le fluide sous pression au moyen d'une première soupape de commande électrique (25) placée du côté de l'entrée contre la source de pression de fluide (201), et peut être déchargé au moyen d'une deuxième soupape de commande électrique (26) située du côté de la sortie à un niveau de pression inférieur, une première soupape de commande électrique unique (25) étant prévue pour une paire respective de dispositifs de réglage de soupape (IIa, IIb), laquelle est raccordée du côté de la sortie au deuxième espace de travail (122) de l'un des deux dispositifs de réglage de soupape (IIa), et en ce que le remplissage de fluide du deuxième espace de travail (122) de l'autre dispositif de réglage de soupape (IIb) est effectué au moyen d'une soupape d'inversion (29) pouvant être commutée entre une position de blocage et une position de passage et au moyen de la pression de fluide dans le deuxième espace de travail (122) connecté à la première soupape de commande électrique unique (25) de l'un des dispositifs de réglage de soupape (IIa), la soupape d'inversion (29) étant disposée dans une conduite de connexion (28) entre les deuxièmes espaces de travail (122) des deux dispositifs de réglage de soupape (IIa, IIb) de la paire de dispositifs de réglage de soupape (IIa, IIb), caractérisé en ce que la soupape d'inversion (29) est une soupape à 2/2 voies activée hydrauliquement et présente une entrée de commande qui se situe au niveau de la sortie de soupape d'une autre soupape d'inversion (32) sollicitée par une pression de fluide et, en vue de la sollicitation par la pression de fluide de l'autre soupape d'inversion (32), son entrée de soupape étant raccordée par le biais d'une soupape de non retour (33) au deuxième espace de travail (122) de la paire de dispositifs de réglage de soupape, connecté à la première soupape de commande électrique unique (25), ou la sollicitation en pression de l'autre soupape d'inversion (32) étant provoquée par une source de pression de fluide externe.
  2. Dispositif selon la revendication 1, caractérisé en ce que la paire de dispositifs de réglage de soupape comprend deux de ces dispositifs de réglage de soupape (IIa, IIb), qui sont associés à deux soupapes d'échange de gaz (10) de même type, soit deux soupapes de sortie soit deux soupapes d'entrée, dans le même cylindre de combustion (19).
  3. Dispositif selon la revendication 1, caractérisé en ce que la soupape d'inversion (29) est une soupape à 2/2 voies pouvant être actionnée par un moteur électrique ou par voie électromagnétique.
  4. Dispositif selon la revendication 3, caractérisé en ce que la soupape à 2/2 voies présente un ressort de rappel (292) pour la ramener dans la position de blocage.
  5. Dispositif selon la revendication 4, caractérisé en ce que la soupape à 2/2 voies présente une entrée de commande de rappel hydraulique (343) pour le rappel dans la position de blocage, et en ce que l'entrée de commande de rappel est raccordée à la source de pression de fluide (201).
  6. Dispositif selon la revendication 5, caractérisé en ce que l'autre soupape d'inversion (32) est réalisée sous forme d'électrovanne à 2/2 voies avec un rappel par ressort et en ce qu'une soupape de décharge (35) réalisée de préférence sous forme d'électrovanne à 2/2 voies avec rappel par ressort est raccordée à sa sortie de soupape, et permet de créer une connexion à un réservoir de fluide (18).
  7. Dispositif selon la revendication 5, caractérisé en ce que l'autre soupape d'inversion (32) est réalisée sous forme d'électrovanne à 3/3 voies avec rappel par ressort, sa deuxième sortie de soupape étant connectée à un réservoir de fluide (18).
  8. Dispositif selon l'une quelconque des revendications 1 à 7, caractérisé en ce que pour une paire de dispositifs de réglage de soupape respectifs (IIa, IIb), on prévoit une deuxième soupape de commande électrique unique (26) dont l'entrée de soupape est raccordée directement au deuxième espace de travail (122) de l'un des dispositifs de réglage de soupape (IIa), connecté à la première soupape de commande électrique unique (25), et est raccordée au deuxième espace de travail (122) de l'autre dispositif de réglage de soupape (IIb) par le biais d'une soupape de non retour (30).
  9. Dispositif selon l'une quelconque des revendications 1 à 8, caractérisé en ce que pour une paire de dispositifs de réglage de soupape respectifs (IIa, IIb), on prévoit deux deuxièmes soupapes de commande électriques (26), dont à chaque fois l'une est raccordée du côté de l'entrée à un deuxième espace de travail (122) des deux dispositifs de réglage de soupape (IIa, IIb).
  10. Dispositif selon l'une quelconque des revendications 1 à 9, caractérisé en ce que pour chaque cylindre de combustion, au moins une paire de dispositifs de réglage de soupape (IIa, IIb) est prévue, et en ce que l'autre soupape d'inversion (32) est connectée du côté de la sortie à toutes les soupapes d'inversion hydrauliques (29) associées à chaque fois à une paire de dispositifs de réglage de soupape (IIa, IIb).
  11. Dispositif selon les revendications 1 et 10, caractérisé en ce que le raccordement de l'entrée de soupape de l'autre soupape d'inversion (32) est effectué dans toutes les paires de dispositifs de réglage de soupape (IIa, IIb).
EP03717127A 2002-07-06 2003-03-05 Dispositif pour commander des soupapes de changement des gaz Expired - Lifetime EP1521902B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10230478 2002-07-06
DE10230478A DE10230478A1 (de) 2002-07-06 2002-07-06 Vorrichtung zur Steuerung von Gaswechselventilen
PCT/DE2003/000697 WO2004005679A1 (fr) 2002-07-06 2003-03-05 Dispositif pour commander des soupapes de changement des gaz

Publications (2)

Publication Number Publication Date
EP1521902A1 EP1521902A1 (fr) 2005-04-13
EP1521902B1 true EP1521902B1 (fr) 2009-06-17

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EP03717127A Expired - Lifetime EP1521902B1 (fr) 2002-07-06 2003-03-05 Dispositif pour commander des soupapes de changement des gaz

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US (1) US7134408B2 (fr)
EP (1) EP1521902B1 (fr)
JP (1) JP4399360B2 (fr)
AT (1) ATE434117T1 (fr)
DE (2) DE10230478A1 (fr)
WO (1) WO2004005679A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7204212B2 (en) * 2005-01-12 2007-04-17 Temic Automotive Of North America, Inc. Camless engine hydraulic valve actuated system
EP2063075A1 (fr) * 2007-11-23 2009-05-27 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Commande de soupape entraînée par fluide
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
FI20106256A0 (fi) * 2010-11-30 2010-11-30 Waertsilae Finland Oy Järjestelmä ja menetelmä polttomoottorin kaasunvaihtoventtiilin käyttämiseksi, sylinterinkansi ja menetelmä polttomoottorin uudistamiseksi
US10113453B2 (en) * 2015-04-24 2018-10-30 Randy Wayne McReynolds Multi-fuel compression ignition engine
KR102371063B1 (ko) * 2017-11-20 2022-03-07 현대자동차주식회사 가변밸브기구 제어 시스템 및 그것을 구성하는 오일 컨트롤 밸브

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Publication number Priority date Publication date Assignee Title
DE69218971T2 (de) * 1991-06-24 1997-07-24 Ford Werke Ag Hydraulische Ventilsteuervorrichtung für eine Brennkraftmaschine
DE4407585C2 (de) 1994-03-08 1996-09-19 Mtu Friedrichshafen Gmbh Variable Ventilsteuerung
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
DE19826047A1 (de) 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen

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Publication number Publication date
US7134408B2 (en) 2006-11-14
EP1521902A1 (fr) 2005-04-13
JP2005532496A (ja) 2005-10-27
DE50311613D1 (de) 2009-07-30
ATE434117T1 (de) 2009-07-15
DE10230478A1 (de) 2004-01-15
JP4399360B2 (ja) 2010-01-13
US20050005881A1 (en) 2005-01-13
WO2004005679A1 (fr) 2004-01-15

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