EP0975856B1 - Soupape avec dispositif de commande hydraulique - Google Patents

Soupape avec dispositif de commande hydraulique Download PDF

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Publication number
EP0975856B1
EP0975856B1 EP98917027A EP98917027A EP0975856B1 EP 0975856 B1 EP0975856 B1 EP 0975856B1 EP 98917027 A EP98917027 A EP 98917027A EP 98917027 A EP98917027 A EP 98917027A EP 0975856 B1 EP0975856 B1 EP 0975856B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
spring means
hydraulically
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
EP98917027A
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German (de)
English (en)
Other versions
EP0975856A1 (fr
Inventor
Ulrich Letsche
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.)
Daimler AG
Original Assignee
DaimlerChrysler AG
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 DaimlerChrysler AG filed Critical DaimlerChrysler AG
Publication of EP0975856A1 publication Critical patent/EP0975856A1/fr
Application granted granted Critical
Publication of EP0975856B1 publication Critical patent/EP0975856B1/fr
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 globe valve, in particular in a Internal combustion engine, with a hydraulic control device according to the preamble of claim 1.
  • a valve control which hinges a linearly movable lift valve. It includes a valve stem a helical compression spring in the valve closing direction and temporarily an oil pressure spring in the valve opening direction act. It also includes a fixed to the valve stem connected, arranged in a work space and with a working fluid Actuating spool in the area each of its end positions belongs to the work area, hydraulically limited by this separable diving area. If the control piston is immersed in one of its diving rooms, i.e. if it is in the area of its end position, the diving room relieves pressure, which stabilizes the pressure in the work area this valve position. That leaves the control piston and therefore the valve stem due to a malfunction standing in an undefined middle position is a provision as well as an elimination of this malfunction only with great effort possible.
  • the object of the present invention is to provide a globe valve to create the type mentioned in the malfunction by simple means can be compensated.
  • the object is achieved by the in the characteristic of Features mentioned claim 1 solved.
  • This ensures that the pressure of the second, hydraulically adjustable spring means separately and quickly can be lowered so far that the pressure force the first spring means that of the second, hydraulically adjustable spring means predominates.
  • the lift valve can thus perform a reset movement by actuation of the auxiliary control member are triggered without the degradation of the supply pressure.
  • the control the auxiliary control element can be used directly together with the control of the actuator or indirectly by controlling the actuator and the resulting adjustment process. Each on request, this can be mechanical, electronic, electrical, electromagnetic or pneumatic, but preferably done hydraulically. In the latter case, that happens Control preferably via the same actuator that the Activation of the control piston enables.
  • auxiliary control element has a 2/2-way valve function having. This function is part of the existing hydraulic system realizable by particularly simple means.
  • An advantageous development of the invention according to claim 3 provides that the auxiliary control member via control lines to a Pressure supply line and a pressure relief line connected which can be acted upon by the actuator. Thereby the connection of the auxiliary control element to the existing one Execute hydraulic system particularly easily.
  • An internal combustion engine especially for driving one Motor vehicle, has several cylinders in a manner known per se on whose combustion chambers each have at least one lift valve to supply a fuel / air mixture or to remove the Exhaust gas are provided.
  • the control of the globe valves takes place by means of engine electronics serving as the central control unit.
  • To control each lift valve 1 is according to FIGS. 1 to 4 a hydraulic control device described in more detail below intended.
  • Each lift valve 1 has a valve stem 2 and one with it connected spring holder 3.
  • the valve stem 2 is over the Spring receptacle 3 by a preloaded serving as the first spring means Compression spring 4 in the valve closing direction with one force acted upon, which the lifting valve 1 in its shown in Fig. 1 Holds rest position.
  • the valve stem 2 is with a piston area in a cylinder guide 5 linearly displaceable, which is part of a Housing 6 is.
  • the cylinder guide 5 is at one point to one Working space 33 widened by the piston area of the Vencilschaftes 2 is penetrated, the piston area in the Work room 33 in one piece in the illustrated embodiment having control piston 7 connected to valve stem 2.
  • the control piston 7 comprises a lower and an upper Plungers 8 and 9, each in the area of an end position immerse the valve stem 2 in pressure chambers 34 and 35.
  • the Pressure chambers 34, 35 are designed so that they are in the end positions of valve stem 2 by plungers 8 and 9, respectively hydraulically separated from the remaining volume of the working space 33 become.
  • the work area is part of one described in more detail below Hydraulic system, the pressure of at least one, not shown Hydraulic pump by appropriate, for a pressure build-up serving supply lines 38 and one for one Pressure relief serving return line 39 is controlled.
  • the control of pressure build-up and pressure relief in the hydraulic system is also carried out via an actuator electromagnetic switching valve 46, which is only indicated in Way through appropriate switching signals of the engine electronics is controlled.
  • a total of five ring channels 22, 24, 27, 29, 31 provided, four ring channels 22, 24, 27, 29 above the Control piston 7 and thus above the working space 33 and a Another ring channel 31 arranged below the working space 33 are.
  • the ring channel 22 is directly connected to the supply line 38 connected while the ring channels 29 and 31 via connecting lines 30, 32 and a switch-shaped branch of the electromagnetic Switching valves 46 either to the further supply line 38 or connectable to the return line 39 are.
  • the ring channel 27 is via a control line 28 for the Control of an auxiliary control element in the form of a 2/2-way valve with a spool 40 in connection.
  • the ring channel 24 closes on the one hand via a connecting line to the return line 39 and the other via a control line 26 to one Working space of the control spool 40 of the 2/2-way valve 37 on.
  • the work space 33 is connected via a connecting line 36 the supply line 38 connected.
  • the piston area of the Valve stem 2 includes cylinder guide 5
  • Pressure chamber 20 on, via a line 21 with a further hydraulic volume 43 is connected.
  • Pressure chamber 20 and hydraulic volume 43 together form an oil pressure spring with a helical compression spring 45, the hydraulic volume via a cylinder 44 43 pressurized, is connected in series.
  • the structure and the function of this hydraulic unit correspond to one hydraulic control device, as in the unpublished German patent application 196 21 951.5 is, so for further explanation on the revelation in this Patent application is referenced.
  • the spring means designed in this way loads the valve stem 2 in the valve opening direction, whereby the pressure chamber 20 simultaneously has a displacement for the valve stem 2 forms.
  • the pressure chamber 20 is in the piston area of the valve stem 2 coaxial channels 11 and 14 with the work space and from there via the connecting line 36 designed as a pressure line can thus be hydraulically connected to the supply line 38, that a ball mounted in an extension 19 of the channel 11 17 by a sufficient gradient between the pressure of the oil pressure spring and the current supply pressure against the force a preloaded compression spring 18 and that on the underside of the Ball-bearing supply pressure from their in the drawings shown rest position is deflected. This is the case if the supply pressure is not fully extended Valve is lowered sharply.
  • the oil pressure spring as explained, relaxed to the supply pressure, whereupon the valve by the force of the helical compression spring 4 closes.
  • the piston area of the valve stem moves 2 and the control piston 7 during a working cycle back and forth between two end positions. That through the plungers 8 or 9 pressure rooms 34 or 35 are in each case in the piston area of the valve stem 2 grooves 15 provided above and below the control piston 7, 16 with the ring channels 29, 31 alternatively connectable to the Connect connecting lines 30 or 32. 1 shows this the position of the valve stem 2 and its piston area in one upper end position, in which the pressure chamber 35 via the groove 16 and applied to the connecting line 30, in the state shown is relieved of pressure.
  • Fig. 4 represents the valve stem 2 and whose piston area in the opposite, lower end position represents in which the pressure chamber 34 via the groove 15 and the pressure line 32 pressurized, depressurized in the state shown is.
  • the pressure-relieved can in each case Pressure chamber 34 or 35 by switching the switching valve 46 be supplied with the supply pressure, so that with a corresponding Dimensioning the balance of forces the globe valve from its upper end position by the pressure of the oil pressure spring on the end face 2 'and from its lower end position the pressure of the compression spring 4 on the spring holder 3 is moved.
  • control piston 7 If the control piston 7 has been moved so far from an end position, that the respective plunger 8 or 9 from the associated Extends pressure chamber 34 or 35, the associated ring channel 31 or 29 shut off by the piston area of the valve stem 2, and the connecting lines 30 and 32 can be reset of the switching valve 46 in its illustrated in Figures 1, 2 and 4 Rest position, and thus by coupling the above Connection lines with the return line 39 relieved of pressure become.
  • valve stem 2 after the movement is triggered through the more tensioned spring means to the opposite Move end position.
  • the mode of operation corresponds the function of the control devices, as in the DE 195 01 495 C1 or DE 196 21 951.5 are described.
  • an auxiliary control element is assigned to the pressure chamber 20, through a 2/2-way valve with a working space 37 and a control slide 40, a control line 28, one Return spring 41 and a connecting line 26 is formed.
  • the pressure chamber 20 and the working space 37 for the control slide 40 are hydraulically connected to each other, however the connection is in the rest position of the spool 40 interrupted by this.
  • the return spring 41 is largely relaxed, the Control line 28 is depressurized.
  • the connecting line 26 is relieved of pressure in every situation as it is via the ring channel 24 is in fixed connection with the connecting line 25.
  • valve stem 2 is in an undefined middle position 2, the control line 28 is via the ring channel 27, a control groove 10 in the piston area of the valve stem 2 and the ring channel 29 is connected to the connecting line 30, by operating the switching valve 46 with the supply pressure can be applied.
  • the one on an end face 40 'of the control slide 40 acting pressure causes a movement of the spool 40 against the force of the return spring 41 in the position shown in Fig. 3.
  • the activated auxiliary control member gives the Connection between the pressure chamber 20 and the connecting line 26 free, whereby the oil pressure spring is relieved of pressure and the Piston area of the valve stem 2 through from its central position the compression spring 4 is pushed back into the end position according to FIG. 1 becomes. If the lift valve 1 has reached its upper end position, there is the hydraulic connection between the ring channels 27 and 29 no longer via the tax groove 10, but is now through a connection of the ring channels 27 and 24 a pressure relief the control line 28 and thus a reset of the control slide 40 to its rest position by the force of the compression spring 41 ensured.
  • control groove 10 and ring channels 27 and 29, which are on it must aim that the two ring channels 27 and 29 at each center position of the piston 4 with each other via the control groove 10 hydraulic connection, from any position of the globe valve and also at any speed of the lift valve, i.e. even with normal function.

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

Claims (4)

  1. Soupape, en particulier dans un moteur à combustion interne, équipée d'un dispositif de commande hydraulique, qui présente une tige de soupape (2), à laquelle sont associés des premiers moyens de ressort (4) agissant dans le sens de fermeture de la soupape et des seconds moyens de ressort à pression d'huile (43) régulés hydrauliquement, et qui (2) est reliée à un piston de commande alimenté hydrauliquement bilatéralement, un processus de fermeture ou d'ouverture de la soupape (1) étant déclenché par un élément de réglage (46) d'une unité de commande centrale, caractérisée en ce qu'aux seconds moyens de ressort à pression d'huile (43) régulés hydrauliquement est associé un élément de réglage auxiliaire (37, 40, 41) agissant hydrauliquement, qui, lors d'un processus de réglage d'un élément de réglage (46) dans le sens de fermeture de la soupape (1) pour une position quelconque de la soupape (1), soulage les seconds moyens de ressort à pression d'huile (43) régulés hydrauliquement dans leur force de pression au-dessous de la force de réglage des premiers moyens de ressort (4).
  2. Soupape selon la revendication 1, caractérisée en ce que l'élément de commande auxiliaire (37, 40, 41) présente une fonction de soupape à 2/2 voies.
  3. Soupape selon la revendication 1 ou 2, caractérisée en ce que l'élément de commande auxiliaire (37, 40, 41) est relié par l'intermédiaire de canalisations de commande à une canalisation d'alimentation en pression (30) et à une canalisation de soulagement de pression (25), qui peuvent être alimentées par l'intermédiaire de l'élément de réglage (46).
  4. Soupape selon l'une des revendications précédentes, caractérisée en ce que l'élément de commande auxiliaire (37, 40) est maintenu dans sa position de repos par un ressort de rappel mécanique (41).
EP98917027A 1997-04-17 1998-03-20 Soupape avec dispositif de commande hydraulique Expired - Lifetime EP0975856B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19716042A DE19716042C1 (de) 1997-04-17 1997-04-17 Hydraulische Steuervorrichtung für wenigstens ein Hubventil
DE19716042 1997-04-17
PCT/EP1998/001630 WO1998048151A1 (fr) 1997-04-17 1998-03-20 Dispositif de commande hydraulique pour au moins une soupape de cylindre

Publications (2)

Publication Number Publication Date
EP0975856A1 EP0975856A1 (fr) 2000-02-02
EP0975856B1 true EP0975856B1 (fr) 2001-12-19

Family

ID=7826782

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98917027A Expired - Lifetime EP0975856B1 (fr) 1997-04-17 1998-03-20 Soupape avec dispositif de commande hydraulique

Country Status (5)

Country Link
US (1) US6167853B1 (fr)
EP (1) EP0975856B1 (fr)
JP (1) JP3348201B2 (fr)
DE (2) DE19716042C1 (fr)
WO (1) WO1998048151A1 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19853355C1 (de) * 1998-11-19 2000-08-31 Daimler Chrysler Ag Hydraulisch steuerbares Hubventil
DE10124869C2 (de) * 2001-05-22 2003-06-26 Caterpillar Motoren Gmbh & Co Hydraulische Steuereinrichtung für gleichwirkende Motorventile eines Dieselmotors
JP2004197588A (ja) * 2002-12-17 2004-07-15 Mitsubishi Motors Corp 内燃機関の動弁装置
GB2423794B (en) 2005-03-01 2008-09-10 Ford Global Tech Llc An internal combustion engine having cylinder disablement and gas recirculation
US7302920B2 (en) * 2005-06-16 2007-12-04 Zheng Lou Variable valve actuator
US7156058B1 (en) * 2005-06-16 2007-01-02 Zheng Lou Variable valve actuator
US7370615B2 (en) * 2005-08-01 2008-05-13 Lgd Technology, Llc Variable valve actuator
US7290509B2 (en) 2005-08-01 2007-11-06 Zheng Lou Variable valve actuator
US7766302B2 (en) * 2006-08-30 2010-08-03 Lgd Technology, Llc Variable valve actuator with latches at both ends
US8978604B2 (en) 2012-03-31 2015-03-17 Jiangsu Gongda Power Technologies Co., Ltd. Variable valve actuator

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3836725C1 (fr) * 1988-10-28 1989-12-21 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De
US5193495A (en) * 1991-07-16 1993-03-16 Southwest Research Institute Internal combustion engine valve control device
US5221072A (en) 1992-01-14 1993-06-22 North American Philips Corporation Resilient hydraulic actuator
DE19501495C1 (de) * 1995-01-19 1995-11-23 Daimler Benz Ag Hydraulische Ventilsteuervorrichtung
JP3368518B2 (ja) * 1995-06-30 2003-01-20 三菱自動車工業株式会社 多段開度弁装置
EP0843779B1 (fr) * 1995-08-08 2001-02-28 Diesel Engine Retarders, Inc. Un systeme de frein moteur par decompression pour moteur a combustion interne
DE19621951C1 (de) * 1996-05-31 1997-07-10 Daimler Benz Ag Hydraulische Venbtilsteuervorrichtung

Also Published As

Publication number Publication date
DE19716042C1 (de) 1998-05-07
EP0975856A1 (fr) 2000-02-02
US6167853B1 (en) 2001-01-02
JP2000515605A (ja) 2000-11-21
DE59802536D1 (de) 2002-01-31
JP3348201B2 (ja) 2002-11-20
WO1998048151A1 (fr) 1998-10-29

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