CN100529335C - Device for modifying the timing of gas exchange valves in an internal combustion engine - Google Patents
Device for modifying the timing of gas exchange valves in an internal combustion engine Download PDFInfo
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- CN100529335C CN100529335C CNB2005800345078A CN200580034507A CN100529335C CN 100529335 C CN100529335 C CN 100529335C CN B2005800345078 A CNB2005800345078 A CN B2005800345078A CN 200580034507 A CN200580034507 A CN 200580034507A CN 100529335 C CN100529335 C CN 100529335C
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Classifications
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
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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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
- F01L2001/3444—Oil filters
-
- 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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34459—Locking in multiple positions
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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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34476—Restrict range locking means
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The invention relates to a device (101) for modifying the timing of gas exchange valves in an internal combustion engine using a hydraulic regulator (102) and a control valve (103). The inventive device (101) is equipped with a central-position locking mechanism for the hydraulic regulator (102). According to the invention, if a controller (112), which regulates the control valve (103), malfunctions, the hydraulic regulator (102) is locked in the central position until the controller (112) is repaired. In addition, the inventive device (101) permits the internal combustion engine to be started in a locked central position, without a displaceable element (105) of the hydraulic regulator (102) striking a lateral wall of a pressure chamber (104) during said start procedure. The invention also relates to a method for bringing the hydraulic regulator (102) into a locked position and maintaining said position for a new start-up of the internal combustion engine in a locked central position.
Description
Technical field
The present invention relates to a kind of device that is used to change the gas exchange valves of internal combustion engine gate control time.
Background technique
In internal-combustion engine, be provided with the camshaft that is used to operate the ventilation valve.Camshaft is installed in the internal-combustion engine, and the cam that is installed on the camshaft is suitably for cam pack very much, for example cup tappet, draw-bar or rocking bar.When camshaft began to rotate, cam can tumble on the cam pack, and cam pack is operated the ventilation valve once more.Therefore, position by cam and form can determine to take a breath turn-off time of valve and disconnection amplitude and disconnection, closing time point.
Current motor scheme generally is to allow valve mechanism set up changeably.On the other hand should be with the setting of variable valve lift, be closed fully up to one by one cylinder.Some schemes are provided for reaching this purpose, such as the valve control machanism that controlled cam pack or electro-hydraulic formula, electronic type are set.In addition, when the running of internal-combustion engine can have influence on the disconnection of ventilation valve and closing time, also shown its advantage.Such as, in order directionally the valve overlap of appointment to be regulated, can allow the disconnection or the closing time of the air intake valve or the valve of giving vent to anger be affected dividually according to wish.Regulate by the current combined characteristic zone of motor, disconnection or the closing time that for example can exchange air valve by current rotating speed or current load, can reduce special fuel consumption by this method, exhaust gas properties is influenced valuably, and can improve engine efficiency, Maximum Torque and peak output.
The variability in the valve control time of mentioning in the literary composition can realize by the dependent phase that changes between camshaft and the bent axle.For this reason, camshaft keeps driving to be connected by the transmission scheme of chain-driven, driving belt transmission, gear transmission or a similar effect with bent axle mostly.Between the chain-driven of crank-driven or driving belt transmission or gear transmission and the camshaft device that is used to change the internal-combustion engine control time is installed, is also referred to as below and be camshaft adjuster, it can be delivered to moment of torsion on the camshaft from bent axle.This device so is provided with, thereby, in the time of needs, can allows camshaft relative crankshaft rotating in a known angular range making the phase place between bent axle and the camshaft be held safely during the internal combustion engine operation.
Be installed in the camshaft that each root in the internal-combustion engine is used for air inlet and the valve of giving vent to anger and all be equipped with camshaft adjuster.Thereby air inlet and the disconnection and the closing time point of the valve of giving vent to anger can be passed mutually in time, and can directionally be regulated valve overlap.
The cooperation of current camshaft adjuster is positioned at the drive-side end of camshaft mostly.Camshaft adjuster also can be arranged on the part or bent axle that jack shaft maybe can not rotate.Contain one in its composition and driven by bent axle and the driving wheel of fixed position relation is arranged with bent axle, the driving element with camshaft maintenance driving relationship, and energy is delivered to moment of torsion the adjusting mechanical device of drive element from driving wheel.Under camshaft adjuster was not installed in situation on the bent axle, driving wheel can be implemented as chain, line belt or gear, thereby and by chain, driving belt or gear drive by crank-driven.Regulating mechanical device can electrodynamic type ground, be driven to hydraulic type ground or pneumatic type.
The embodiment of two preferred hydraulic type adjustable camshaft regulators has described so-called axial piston regulator and rotary-piston regulator.
With regard to the axial piston regulator, driving wheel keeps being connected by the helical teeth engagement with drive element with piston, piston separately.The cavity that drive element and driving wheel make up is divided into two pressure chambers of axially installing toward each other by piston.When the another one pressure chamber linked to each other with water tank, one of them pressure chamber was loaded pressure medium, thereby piston is passed in the axial direction.Piston mobile also can the engagement by helical teeth in the axial direction allow driving wheel be relevant to the follower rotation, thereby camshaft is with respect to crankshaft rotating.
Second embodiment of hydraulic type camshaft adjuster is so-called rotary-piston regulator.Among them, driving wheel forms antitorque the connection with stator.Rotor is concentric setting mutually with stator, connects by for example 2 class precision press fits, bolt or welding by elongation line or jack shaft with camshaft, camshaft, thereby allows rotor all be correlated with regard to power, form or material aspect.Be provided with many equally spaced in a circumferential direction cavitys in stator, they radially stretch out from rotor.Cavity is in the axial direction by the side cover quilt and compress qualification.All have a wing extending in each such cavity, the wing links to each other with rotor and each cavity is divided into two pressure chambers.The pressure chamber is connected at ground with pressure medium pump or water tank one by one, thereby can regulate or keep the position of camshaft about bent axle.
Need allow sensor catch the characteristic parameter of motor, for example end-state and rotating speed in order to control camshaft adjuster.These parameters are introduced into electronic control unit, and after the combined characteristic with internal-combustion engine compared, electronic control unit flowed into or flows out different pressure chambers pressure medium and controlled.
For the phase place of adjustment cam axle with respect to bent axle, allow in the cavity pressure chamber in two interactional pressure chambers link to each other with pressure medium pump, the another one pressure chamber links to each other with water tank.Pressure medium is introduced a pressure chamber and pressure medium is derived the another one pressure chamber is inter-related, thereby the feasible piston that is separated by the pressure chamber is pushed to the direction of axle, so just can allow camshaft be relevant to bent axle and rotate by the inclined-plane engagement in the axial piston regulator.In the rotary-piston regulator,, can allow the wing be passed like this and directly make camshaft be relevant to bent axle begin rotation to exerting pressure and allow the another one pressure chamber in a pressure chamber by pressure load.For phase place is kept, perhaps allow these two pressure chambers all link to each other with pressure medium pump, perhaps allow them be separated by pressure medium pump and water tank.
The control of the pressure medium flow of inflow or outflow pressure chamber realizes that by control valve control valve mostly is 4/3 proportion valve greatly.Valve pocket all is provided with interface (working interface) to each pressure chamber and leads to the interface of pressure medium pump and at least one leads to the interface of water tank.In being essentially the valve pocket of hollow cylinder, this is provided with axially movable control piston.Control piston can be brought in each position of two designated end positions in the axial direction by the spring force of electromagnetic type control unit and spring element.In addition, control piston also is furnished with circular groove and control edge, and the pressure chamber can link to each other with pressure medium pump or water tank selectively thereby allow one by one.Equally also can be stipulated, be made that the pressure medium chamber can also can be separated by the pressure medium water tank by pressure medium pump in this position the position of control piston.
A kind of such device was described in DE 10064222A1.Wherein relate to be a kind of be the device of structural form with the rotary-piston.Keep driving the stator that is connected with camshaft and rotatably be placed on the rotor, rotor keeps antitorque with camshaft and is connected.Stator is provided with the space of opening wide that is used for rotor.Device axially on be provided with side cover, side cover is limited the scope of device.Stator, rotor and side cover are compressed, thereby make the space be able to closure and form booster cavity.Axial groove is installed in the outer surface of rotor, is provided with the wing that extends in the space in groove.The wing is divided into two pressure chambers interact with each other with booster cavity.By pressure medium is imported from the pressure chamber or derives, the phase place that can optionally allow camshaft be relevant to bent axle is kept or is regulated.
In side cover, be provided with two lockweights, make them on the direction of rotor, apply a power by spring element.The groove of Yan Shening is installed in the end face of rotor in a circumferential direction, and the end face of rotor is towards lockweight.Groove is so arranged and installs, thereby when all grooves all were not loaded pressure medium, two lockweights were engaged in the groove in the neutral position of determining separately.Therefore rotor blocks relevant stator and stops relevant rotation.Can be by first and second pressure pipes with pressure medium injection pressure dielectric chamber.When pressure medium injected the first pressure medium chamber, the end face of lockweight also was loaded pressure medium.Thereby make corresponding lockweight be pressed in the piston skirt of side cover in the marginal pore, and realize rotor relevant with stator to certain direction adjusting.Another groove by the lockweight engagement should be set as follows simultaneously, realizes that promptly an adjusting makes rotor come out from middle position up to arriving maximum value.Correspondingly, also can regulate with respect to stator rotor along other directions.Device is equipped with counterbalance spring, and its end is fixed on the rotor, and the other end is fixed on the stator, and the drag torque that makes camshaft impose on rotor is able to balance.
Described a kind of control valve in DE 19853670A1, it relies on the pressure medium flux of internal-combustion engine present load situation control flows to the pressure chamber.The composition of this control valve comprises a regulon, a valve pocket and a control piston that is essentially hollow cylinder that is essentially hollow cylinder, and control piston can move axially in valve pocket.Be provided with two working interfaces on valve pocket, one is to flow into interface, and another is to flow out interface.Regulon can for example be an electromagnetic element, and by applying flow, it can promote control piston by push rod under the effect of spring force.Rely on valve pocket inner control position of piston that the inflow interface is linked to each other with one of two working interfaces, and each working interface of water tank interface and other is linked to each other, perhaps allow working interface be flowed into or flow out interface and separate.Thereby when flow out a pressure chamber, can allow pressure medium import another pressure chamber at pressure medium, so just can cause that camshaft is relevant to the phase change of bent axle.
This camshaft adjuster control valve that has the neutral position lockweight has significant drawback, and its fact is, under the situation that is not having energising, the interface of pressure medium links to each other with a interface in two working interfaces.When control unit broke down, pressure medium was drawn towards one of them pressure chamber of two pressure chambers, and pressure medium is drawn towards in one of them lockweight of two lockweights simultaneously.Thus one, rely on the configuration of control valve, camshaft adjuster rotates into after regulon breaks down among in two maximum positions one, and makes this phase place be held by the whole driving of internal-combustion engine.In this case, because the camshaft adjuster that is positioned at the neutral position does not have at device to latch under the state of pressurized, internal-combustion engine should have good starting and service performance in camshaft is relevant to the phase place of bent axle, yet, thereby make the starting and the service performance variation of internal-combustion engine because phase place is relevant to the neutral position by being moved the biglyyest.
Summary of the invention
For these reasons, task of the present invention is exactly will avoid these shortcomings that are mentioned and advise a kind of method thus, utilize this method can allow camshaft be relevant to bent axle and be brought into a phase place, the hydraulic type controlling device is in this phase place or be locking, can automatically be brought into locked position of coupler during camshaft rotates for the first time when resetting, and the piston or the wing can not run into end of stroke.
Also have a method in addition, can be brought into locked position of coupler to the controlling device that is in non-latching stand by this method.
Internal-combustion engine among the present invention is furnished with: the hydraulic type controlling device, and it has two synergistic pressure chambers, wherein by pressure medium being imported and deriving the pressure chamber, can keep or on purpose changes the phase place of camshaft with respect to bent axle; Have two working interfaces, a control valve that flows out an interface and an inflow interface, wherein first working interface communicates with first pressure chamber, second working interface communicates with second pressure chamber, flows out interface and communicates with water tank, flows into interface and is loaded pressure medium.Wherein control valve can be utilized regulon and bring four kinds of control positions into.Wherein in first control position of control valve, the inflow interface neither communicates with first working interface and does not also communicate with second working interface; In second control position of control valve, first working interface communicates with flowing out interface, and second working interface communicates with the inflow interface; In the 3rd control position of control valve, first and second working interface neither communicates with the outflow interface and does not also communicate with flowing into interface, and perhaps first and second working interface only communicates with the inflow interface; In the 4th control position of control valve, second working interface communicates with flowing out interface, and first working interface communicates with the inflow interface.
First kind of controlling method that is used for changing at the device in control time of engine shutdown process gas exchange valves of internal combustion engine door of the present invention be successively according to the methods below step implement, thereby solve task of the present invention:
-the phase place of starting and keeping an appointment
-close ignition system,
-regulate the second or the 4th control position (130,132), make phase place
Kept, up to revolution speed sensing device notice rotation speed n=0,
-detect rotation speed n by the revolution speed sensing device,
-control position (130,132) that obtains is kept the time lag given in advance,
-at later inactive regulon (112) of the time lag.
Can allow controlling device be brought in stopping process in the phase place by this method, this phase place departs from a value X ° with the bent axle (KW) of the locked position of coupler that mediates.When controlling device was not filled with by pressure medium as yet, the symbol of X depended on the adjusting direction of controlling device.For example when device is not provided with counterbalance spring or is provided with a counterbalance spring, have only very little moment of torsion that the rotor stator system is influenced, this moment of torsion is less than the drag torque of the camshaft of rotation, and so, locked position of coupler was positioned at direction " in advance " in the middle of phase place was relevant to.By method step, when the moment of torsion of counterbalance spring was oppositely arranged greater than the drag torque of camshaft and with it, locked position of coupler had been positioned at direction " hysteresis " in the middle of this phase place was relevant to.Should occupy such position after ignition system is disconnected, this position stops regulon to move into the neutral position, up to revolution speed sensing device notice rotation speed n=0.Subsequently, the control position that is occupied is held a definite time lag.Why this is necessary, is because the revolution speed sensing device has been notified rotation speed n=0 during the last rotation of camshaft/bent axle, and goes owing to alternation moment makes regulon be moved in the position that is not supposed to by the neutral position.Can stop the influence of loosening of internal-combustion engine, for example piston work relax or the similar situation that can cause occupying errors present equally by this retention time.
Second method that the present invention is used for changing at the device in the control time of engine shutdown process gas exchange valves of internal combustion engine door solves task of the present invention like this, promptly implements following method step between down period successively:
-the phase place of starting and keeping an appointment
-close ignition system,
-regulate the second or the 4th control position (130,132), make phase place
Kept, up to revolution speed sensing device notice rotation speed n=0,
-detect rotation speed n by the revolution speed sensing device,
-control position (130,132) that obtains is kept the time lag given in advance,
-at later inactive regulon (112) of the time lag.
And implement following method step successively during starts:
-adjusting first control position,
The rotation speed n of-detection bent axle or camshaft,
If-rotation speed n＞0, detected pressures pressure medium p then,
If-pressure of pressure medium p greater than value given in advance, then regulates the control position according to the combined characteristic that is stored in the control unit.
What can guarantee thus is, is issued to locking in the situation of releasing state, and when pressure of pressure medium arrive determined value and thus assurance device have enough pressure mediums supply with after locking just be disengaged.Like this can holdout device the collision of issuable piston or the wing when not being supplied to enough pressure mediums and being in non-latching situation.
According to a further aspect in the invention, the controlling method that is used for changing at the device in control time of engine shutdown process gas exchange valves of internal combustion engine door solves task of the present invention like this, wherein implements according to following method step successively:
-adjusting first control position,
The rotation speed n of-detection bent axle or camshaft,
If-rotation speed n＞0, detected pressures pressure medium p then,
If-pressure of pressure medium p greater than value given in advance, then regulates the control position according to the combined characteristic that is stored in the control unit.
Description of drawings
Further feature of the present invention is described simply by following description and inventive embodiments figure.They are:
Fig. 1 is that figure is cutd open in the longitudinal section of hydraulic type controlling device,
Fig. 2 is the hydraulic type controlling device cross section according to Fig. 1,
Fig. 3 is the flow chart that is used for the method for cranking internal combustion engine, and internal-combustion engine wherein has the device that is used to change the scavenging air valve gate control time according to invention,
Fig. 4 is the schematic representation of apparatus that is used to change the gas exchange valves of internal combustion engine gate control time according to the present invention,
Fig. 5 a is in first control position, cuts open figure according to the longitudinal section of the control valve of the device that is used to change the gas exchange valves of internal combustion engine gate control time of the present invention,
Fig. 5 b is in second control position, and figure is cutd open in the longitudinal section that comes from the control valve of Fig. 5 a,
Fig. 5 c is in the 3rd control position, and figure is cutd open in the longitudinal section that comes from the control valve of Fig. 5 a,
Fig. 5 d is in the 4th control position, and figure is cutd open in the longitudinal section that comes from the control valve of Fig. 5 a,
Fig. 6 is from flowing into interface to the volume flowrate of pressure chamber and the control piston dependence with respect to housing position,
Fig. 7 is the flow chart that is used for controllably closing the method for internal-combustion engine, this internal-combustion engine have according to the device that is used to change the scavenging air valve gate control time of the present invention and
Fig. 8 is according to prior art, is used to change the schematic representation of apparatus of gas exchange valves of internal combustion engine gate control time.
Embodiment
Fig. 1 and Fig. 2 show is the hydraulic type controlling device 1a that is used to change the device 1 of gas exchange valves of internal combustion engine gate control time.Controlling device 1a forms by stator 2 with the rotor 3 of stator 2 concentric settings in essence.Driving wheel 4 also is set to sprocket wheel in the embodiment shown with 2 antitorque linking to each other of stator.Same conceivable is that driving wheel 4 is embodied as driving belt or gear.Stator 2 rotatably mounted putting on rotor 3, in the embodiment who is demonstrated, the internal surface of stator 2 is provided with five equally spaced in a circumferential direction spaces 5.Space 5 is limited by stator 2 and rotor 3 diametrically, and two sidewalls 6 by stator 2 limit and limited by first side cover and second side cover 7,8 in the axial direction in a circumferential direction.Each space 5 is all closed by densification ground by this method.First side cover and second side cover 7,8 link to each other with stator 2 by connecting element 9, for example bolt.
On the outer surface of rotor 3, be provided with the wing groove 10 that distributes vertically, in each wing groove 10, be provided with the wing 11 that radially extends.The wing 11 extends in each space 5, and the wing 11 is pressed close to stator 2 diametrically, pressed close to side cover 7,8 in the axial direction.Each wing 11 is separated into two pressure chambers of working toward each other 12,13 with space 5.For guarantee with the wing 11 densification abut on the stator 2, between the bottom land 14 of wing groove 10 and the wing 11, leaf spring element 15 is installed, they apply a power to the wing 11 diametrically.
By first and second pressure pipes 16,17 first and second pressure chambers 12,13 are linked to each other with pressure medium pump or water tank by control valve, control valve and pressure medium pump and water tank are not expressed out in the drawings.Thereby the adjusting drive unit can be set, and it makes stator 2 be achieved at the relevant rotation of rotor 3.What need simultaneously to stipulate is, or allows all first pressure chambers 12 link to each other with pressure medium pump, otherwise just allows all second pressure chambers 13 link to each other with water tank, i.e. two antipodal configurations.When first pressure chamber 12 links to each other with pressure medium pump and second pressure chamber 13 when linking to each other with water tank, therefore first pressure chamber 12 will extend to the consumption of second pressure chamber 13.Produce the wing 11 moving according to the direction of first arrow 21 in a circumferential direction thus.By moving of the wing 11, make rotor 3 be relevant to stator 2 rotations.
In the embodiment who is showed, stator 2 is by the unshowned chain-driven of meshing on driving wheel 4 and by crank-driven.What it is contemplated that equally is that the driving of stator 2 can be by driving belt or gear drive.By for example press fit or by the bolt of central bolt connect can make that rotor is 3 force-closed, form sealing or material sealing ground links to each other with the camshaft that is not demonstrated.Pressure medium is imported or derivation pressure chamber 12,13, make rotor 3 be relevant to stator 2 and rotate relatively, thereby between camshaft and bent axle, produce phase shifts.By on purpose pressure medium being introduced or being drawn pressure chamber 12,13, can on purpose change the control time of gas exchange valves of internal combustion engine door.
The sidewall 6 of radially-arranged in essence groove 5 has concavo-convex body 23, and concavo-convex body 23 stretches in the groove 5 in a circumferential direction.Concavo-convex body 23 is used as the block of the wing 11, and has guaranteed can give pressure chamber's 12,13 supply pressure media when rotor 3 occupies when it is relevant to one of two limit positions of stator 2, and the wing 11 is close to one of sidewall 6 in these two positions.
When device 1 pressure medium is supplied with not enough the time, for example in the engine starting process, it is mobile out of control that the alternation moment that camshaft imposes on rotor 3 and drag torque make that rotor 3 is relevant to stator 2.In the phase I, the drag torque of camshaft is relevant to the stator extruding with rotor on the circumferencial direction opposite with the stator sense of rotation, keep off on sidewall 6 up to it.Next, the alternation moment that camshaft is applied on the rotor 3 causes the wing 11 in rotor 3 and the groove 5 to oscillate, and at least one pressure chamber in pressure chamber 12,13 is filled with by pressure medium fully.This can cause very high wearing and tearing and noise in device 1.For being avoided, it in device 1, is provided with two blocking elements 24.Each blocking element 24 is made up of a pot shape piston 26, and this piston is set in the axial bore 25 of rotor 3.Spring 27 applies a power to piston 26 diametrically.The axially last side upper support at expulsion element 28 of spring 27 comes and is provided with separate with it a, axial end within pot shape piston 26.
In first side cover 7, each blocking element 24 constitutes chutes 29 like this, thus make rotor 3 be relevant to stator 2 on a position by locking, this position is corresponding to the position when the engine starting.In this configuration, piston 26 is extruded in the chute 29 by spring 27 when the pressure medium supply of device 1 is not enough.Take measures then, allow piston 26 when device 1 supply reaches, be got back in the axial bore 25 and and cancel locking with this by the pressure medium extruding.This realizes by pressure medium that generally it is directed in the positive terminal ditch 30 of the lid side that is arranged at piston 26 by the pressure pipes that is not demonstrated.When phase place corresponding to the internal-combustion engine initial position
And when the neutral position of the wing between the two side 6 11 is corresponding, by use two blocking elements 24 and the coupling chute 29 can make hydraulic type controlling device 1a in this position by locking.
For leakage of oil is drawn in the spring space of axial bore 25, expulsion element 28 is provided with the groove of axial distribution, pressure medium can be guided into hole in second side cover 8 along groove.
What Fig. 8 showed is according to prior art, is used to change the device 101 of gas exchange valves of internal combustion engine gate control time.It is made up of hydraulic type controlling device 102 and control valve 103.
Control valve 103 is made up of regulon 112, first spring element 113 and valve body 114.Regulon 112 can be arranged to for example form of regulon 112 electronics or hydraulic pressure.Do not set an electrical adjustment unit 112 as limiting ground below, it is implemented as electromagnetic element.Be provided with the first working interface A, the second working interface B at valve body 114 places, flow into interface P and flow out interface T.The first working interface A links to each other with first pressure chamber 106 by first pressure pipes 115, and the second working interface B links to each other with second pressure chamber 107 by second pressure pipes 116.In addition, flowing out interface T links to each other with pressure medium container 117.Flow into interface P and pressure medium is added filter 119 and safety check 120 by pressure medium pump 118.First chute 108 links to each other with first pressure pipes 115 by the 3rd pressure pipes 121.Equally, second chute 109 links to each other with second pressure pipes 116 by the 4th pressure pipes 122.First and second chutes 108,109 are set to groove respectively, their size on the movement direction of displaceable element 105 greater than the size of separately lockweight 110,111.These two lockweights 110,111 are engaged on when the displaceable element of being showed 105 is positioned at the neutral position in separately the chute 108,109, and are set at the end of groove separately on the movement direction of displaceable element 105.
By regulon 112, valve can be brought into second, third and the 4th control position 130,131,132 under the spring force effect of first spring element 113.When valve in second control position 130 time, just the electric current of regulon does not have from little it's time to, the second working interface B only with flow into interface P and link to each other, and the first working interface A only links to each other with outflow interface T.
When valve the time in the 3rd control position 131, when just the electric current of regulon is from little to medium, two working interface A, B neither with flow into interface P and link to each other and also do not link to each other with outflow interface T.What can replace is, allows two working interface A, B only with flow into interface P and link to each other, thereby compensate leakage loss.
When valve in the 4th control position 132 time, just the electric current of regulon is therefrom waited until maximum the time, the first working interface A only with flow into that interface P links to each other and the second working interface B only links to each other with outflow interface T.
In the operation that internal-combustion engine is conditioned, control valve 103 is brought in second control position 130, thereby allows displaceable element 105 be adjusted on the direction " hysteresis ", and direction " hysteresis " is shown in second arrow 126.Pressure medium is drawn towards second pressure chamber 107 from flowing into interface P by the second working interface B and second pressure pipes 116.Meanwhile, pressure medium is introduced in second chute 109 by the 4th pressure pipes 122.Thereby second lockweight 111 is extruded from second chute 109 under the active force of second spring 129.Simultaneously, first pressure chamber 106 is connected pressure medium container 117 by first pressure pipes 115 with outflow interface T.By pressure medium from first pressure chamber 106 outflow and make displaceable element 105 be moved on the direction " hysteresis " to the inflow of second pressure chamber 107.Simultaneously, first and second chute 108,109 is moved on the direction " hysteresis " equally.In the time of outside second lockweight 111 is positioned at second chute 109, first lockweight 110 moves in first chute 108.
In order to keep the phase place of hydraulic type controlling device 102
, control valve 103 is brought in the 3rd control position 131.Two working interface A, B neither do not link to each other with outflow interface T with inflow interface P yet.There is not pressure medium to flow in the pressure chamber 106,107 or outflow, and phase place
Be to keep constant.
In order to realize that a displaceable element 105 is adjusted on the direction " in advance ", control valve 103 is brought in the 4th control position 132, wherein with the 3rd arrow 128 expression directions " in advance ".Pressure medium is drawn towards first pressure chamber 106 from flowing into interface P by the first working interface A and first pressure pipes 115.Meanwhile, pressure medium is introduced in first chute 108 by the 3rd pressure pipes 121.Thereby make first lockweight 110 under the effect of first spring, 127 power, from first chute 108, be extruded out.Simultaneously, second pressure chamber 107 is connected pressure medium container 117 by second pressure pipes 116 with outflow interface T.Pressure medium is from the outflow of second pressure chamber 107 and flow into first pressure chamber 106, thereby makes displaceable element 105 be moved on the direction " in advance ".Simultaneously, first and second chute 108,109 is moved on the direction " in advance " equally.In the time of outside first lockweight 110 is positioned at first chute 108, second lockweight 111 moves in second chute 109.
The reply neutral position is regulated when displaceable element 105 departs from neutral position shown in Figure 8, thereby the lockweight 110,111 of on-load pressure medium not is inserted in separately the chute 108,109.Give another lockweight 110,111 on-load pressure media simultaneously, allow it be positioned at outside the chute 108,109.Move the restriction of the lockweight 110,111 that only is inserted into.
If hydraulic type controlling device 102 is positioned at the neutral position that Fig. 8 shows, and installs 101 and be not supplied to enough pressure mediums, such as in engine starting, two lockweights 110,111 are inserted in separately the chute 108,109.Simultaneously, lockweight 110,111 is set like this and implements chute 108,109 like this, make lockweight 110,111 be positioned at chute 108,109 mutual distances end farthest.Thus that displaceable element 105 is fixing with respect to related pressure chamber 104.What can substitute is to allow lockweight 110,111 be positioned at the nearest end of chute 108,109.In this alternate embodiment, first chute 108 must must be by first pressure pipes, 115 on-load pressure media by second pressure pipes 116 and second chute 109.What can expect equally is for example by the volute groove, to give chute 108,109 on-load pressure media by each pressure chamber 106,107.
In the stopping process of internal-combustion engine, exist following possible, in the position after promptly displaceable element 105 is positioned in and is relevant to the neutral position and leans on.When resetting, device 101 is not also filled with by pressure medium fully.Because the drag torque of camshaft, element 105 are driven on the direction of backstop 133 and colliding the there.This has caused component wear to be enhanced and undesirable noise.
When the regulon 112 of control valve 103 can't work by the interruption of damage, power supply or the electrical connection of for example electromagnetic element, control valve 103 will be set at 130 li of second control positions.This can cause second lockweight 111 to be thrown off and camshaft is relevant to bent axle and is adjusted on the direction " hysteresis ".Such result is, the degradation of the internal-combustion engine with optimum neutral position in the time of starting and running that makes in Fig. 8 to be showed.
Schematically hydraulic type controlling device 102 relates to for example axial piston regulator or rotary-piston regulator.Only relate to the embodiment of rotary-piston regulator below, it is not construed as limiting.Pressure chamber 104 is corresponding with the groove 5 among Fig. 1.Displaceable element 105 is corresponding with the wing 11.Lockweight 110,111 can be arranged in the side cover of rotary-piston regulator according to Fig. 1 in this embodiment, perhaps is arranged in the rotor of the rotary-piston regulator in the hole (being preferably blind hole).Each chute 108,109 is arranged in other assemblies one by one.
What show in Fig. 4 is schematic, similar to a Fig. 8 device 101 according to invention.Its major part can be discerned by the content shown in Fig. 8, Here it is why to same component application same reference character.This difference according to the device 101 of invention is that control valve 103 also has first control position 140.When regulon 112 is in electric current from little during to the state that do not have, first control position 140 is activated.In this case, first spring element 113 is arrived the control position 140 of winning.In this position, flow into interface P and neither also do not link to each other with the second working interface B with the first working interface A.According to the configuring condition of hydraulic type controlling device 102, can link to each other with the first working interface A or with the second working interface B flowing out interface T, and another working interface A, B does not communicate with outflow interface T.The embodiment that can expect is equally, and in first control position 140, the first and second working interface A, B neither do not communicate with flowing out interface T with flowing into interface P yet, perhaps two working interface A, B only with flow out interface T and link to each other.
Except first control position 140, second, third that control valve 103 also has in Fig. 8 to be showed and the 4th control position 130,131,132, wherein, the electric current of regulon 112 occupies second control position 130 from little to medium the time, therefrom wait until to occupy the 3rd control position 131 when big, occupy the 4th control position 132 from greatly to maximum the time.
When regulon 112 has fault or the electric current introducing appearance mistake in its inside, control valve 103 can arrive first control position 140 automatically, control valve 103 maintains this position simultaneously, is repaired up to regulon 112 or its power supply.After internal-combustion engine is reset because that the pressure medium of hydraulic type controlling device 102 is supplied with is not enough, displaceable element 105 when internal-combustion engine is pent and its location independent ground sail the neutral position into owing to drag torque and alternation moment.Two lockweights 110,111 can be latched in there in the chute 108,109 separately, and the fixing position of displaceable element 105 in pressure chamber 104 thus.Because the configuration of first control position 140, make that not having pressure medium during internal combustion engine operation is introduced in pressure chamber 106,107 and the corresponding chute 108,109.Such result is that displaceable element 105 is relevant to pressure chamber 104 holding positions and fixes, and the phase place between camshaft and the bent axle
Remained on the selflubricating position consistently, in the selflubricating position, internal-combustion engine has good starting feature and running feature.
Fig. 5 a to 5d has exemplarily showed the valve body 114 according to the control valve 103 of the device 101 of invention.Valve body 114 is made up of valve pocket 141 and control piston 142.Valve pocket 141 is embodied as hollow cylinder in itself, is provided with three axial equally spaced circular grooves 143,144,145 in its outer surface.Each circular groove in the circular groove 143 to 145 is represented an interface of valve, and in the axial direction, the circular groove 143,145 of outside constitutes working interface A, B, and middle circular groove 144 constitutes inflow interface P.Flowing out interface T is set in the end face of valve pocket 141 by an opening.Each circular groove in the circular groove 143 to 145 links to each other with the inside of valve pocket 141 by first radial opening 146.Axially movably being provided with one in the valve pocket 141 is the control piston 142 of hollow cylinder in essence.An end face of control piston 142 is applied with a power by second spring element 147, and the push rod 148 that another end face is conditioned unit 112 applies a power.By can allowing control piston 142 be moved under the effect of the power of second spring element 147 in the arbitrary position that is positioned between first and second end of stroke 149,150 for regulon 112 energisings.
Control piston 142 is provided with first and second piston ring land 151,152.The internal diameter of the external diameter of piston ring land 151,152 and valve pocket 141 is complementary.In control piston 142, be provided with the second radial opening 146a between the end face of grasping push rod 148 end and the piston ring land 152 on its of control piston, thereby the inside of realizing control piston 142 links to each other with the inside of valve pocket 141 in addition.First and second piston ring land 151,152 according to such form setting and be installed on the outer surface of control piston 142, make control edge 153 to 156 depend on position separating or closed jet incoming interface P and the working interface A of control piston 142 with respect to valve pocket 141, connection between the B, and separation or closed working interface A, B with flow out being connected between the interface T.The external diameter of control piston 142 is between the push rod 148 and second piston ring land 152 and the internal diameter that is set to less than valve pocket 141 in the scope between the first piston ring bank 151 and second piston ring land 152.Just the 4th circular groove 157 can be set between first and second piston ring land 151,152 thus.In the 4th circular groove 157, be provided with the 3rd piston ring land 158.The internal diameter of the external diameter of the 3rd piston ring land 158 and valve pocket 141 is complementary.In addition the 3rd piston ring land 158 is located like this, promptly allow it in first control position 140 of control valve 103, make flow into and being connected between interface P and the second working interface B be able to closure.
What Fig. 5 a showed is first control position 140 of control valve 103, and in this position, control piston 142 is conditioned unit 112 and imposes on one at minimum force and less power F by push rod 148
1Between power.The end face of control piston 142 push rod sides is positioned at first end of stroke 149 (mobile route=0 millimeter) and mobile route s
1Between scope in.Flow into being connected by the 3rd piston ring land 158 closures between interface P and the second working interface B, the connection between the inflow interface P and the first working interface A is by first piston ring bank 151 closures.In addition, the second working interface B with flow out being connected between the interface T by second piston ring land, 152 closures, and pressure medium flows to from the first working interface A and flows out interface T.Because pressure medium flows to two lockweights 110,111 and two pressure chambers 106,107 are blocked, so in first control position 140, need not carry out adjusting initiatively.By being connected of first pressure chamber 106 and container 11 with 106 emptyings of first pressure chamber.Rely on the position of hydraulic type controlling device 102 displaceable element 105 can be driven to the neutral position by the traction of camshaft or alternation moment at once or a definite time after and be latched in enduringly there, why needing this time of determining, is for second pressure chamber 107 is turned based on leakage.
This control position is corresponding to the configuration of control valve 103 when regulon 112 is not powered, thereby control piston 142 is moved to first end of stroke, 149 places by second spring element 147, and mobile route is zero.When regulon 112 breaks down or its power supply when being interrupted, valve is arranged in this position.
What Fig. 5 b showed is second control position 130 of control valve 103, and in this position, control piston 142 is conditioned unit 112 and applies one at less power F by push rod 148
1With moderate force F
2Between power, and F
2＞F
1Thus, control piston 142 moves a S apart from first end of stroke 149 of push rod side
1To S
2The path, and S
2＞S
1First piston ring bank 151 further blocks the first working interface A and flows into being connected between the interface P, and pressure medium flows out interface T from first working interface continuation flow direction.In addition, being connected between second piston ring land 152 retardance, the second working interface B and the outflow interface T, and the second and the 3rd piston ring land 152,158 will flow into the releasing that is connected between interface P and the second working interface B.In this position, pressure medium is directed the second and the 4th pressure pipes 116 to second pressure chamber 107 and second chute 109 by the second working interface B, 122, thus make second lockweight 111 throw off and hydraulic type controlling device 102 is regulated to direction " hysteresis ".Meanwhile pressure medium flows to the first working interface A and flows to therefrom by first pressure pipes 115 and flows out interface T from first pressure chamber 106.
What Fig. 5 c showed is the 3rd control position 131 of control valve 103, and in valve, control piston 142 is conditioned unit 112 and imposes on one at moderate force F by push rod 148
2With F more energetically
3Between power, and F
3＞F
2Thus, control piston 142 is passed a S apart from first end of stroke 149 of push rod one side
2To S
3The path, and S
3＞S
2In distributing this position of valve, first and second piston ring land 151,152 not only blocks working interface A, and B is connected and blocks working interface A between the interface P with flowing into, being connected between B and the outflow interface T.Pressure medium can not be drawn towards pressure chamber 106,107 in this position of control valve 103, and pressure medium can not 106,107 outflows from the pressure chamber.This control position is corresponding to a holding position, in this position, and the phase place between camshaft and the bent axle
Kept consistently.
What Fig. 5 d showed is the 4th control position 132 of control valve 103, and in this position, control piston 142 is conditioned unit 112 and imposes on one at F more energetically by push rod 148
3With maximum, force F
4Between power, and F
4＞F
3Thus, control piston 142 moves a S apart from first end of stroke 149 of push rod side
3To S
4The path, and S
4＞S
3In this configuration, first piston ring bank 151 blocks the first working interface A and flows out being connected between the interface T, separates with being connected by first piston ring bank 151 and the 3rd piston ring land 158 of the first working interface A and flow into interface P.Subsequently, flow into being connected between interface P and the second working interface B, and pressure medium arrives the inside of control piston 142 and flows to outflow interface T therefrom by the second working interface B and the second radial opening 146a by 152 retardances of second piston ring land.In this position of control valve 103, pressure medium by second pressure pipes 116 from guiding second working interface B of second pressure chamber 107 and pilot flow outgoing interface T therefrom.Meanwhile, pressure medium is directed to first pressure chamber 106 and first chute 108 by the first working interface A, first pressure pipes 115 and the 3rd pressure pipes 121.Allow first lockweight 110 throw off and hydraulic type controlling device 102 is regulated forward thus.
Use the control valve 103 of 4/4 bypath valve 103 as device 101 in the invention, thereby do not need attached module (for example Fu Jia control valve) to describe to have automatically the device 101 at the neutral position locking mechanism of the neutral position of locking starting, wherein element 105 (wing in wing regulator) stops collision at the block place.Compare with the embodiment who describes on the prior art, both increase the structure space and also increase manufacturing or mounting cost.When regulon 112 broke down, device 101 was brought into the neutral position and is latched in the there and repaired up to regulon 112 simultaneously.
Fig. 6 shows is dependence from the dutycycle that flows into interface T 106,107 volume flowrate and regulon 112 to the pressure chamber.Regulon 112 has been applied in zero volt or peaked voltage.Dutycycle has shown that regulon 112 is applied in the time portion of voltage max.Dutycycle is big more, and is big more by the power that push rod 148 imposes on control piston 142 from regulon 112.Therefore dutycycle is mobile measure of the control piston 142 of valve pocket 141 inside with respect to first end of stroke 149.
In the first area dutycycle is from zero to first value TV1, control valve 103 occupies first control position 140.In this control position 140, flow into interface P and working interface A, the connection between the B is closed, and finds out that from leakage flux volume flowrate is 0.
When dutycycle when first value TV1 is worth between the TV2 with second, control valve 103 is arranged in second control position 130.Pressure medium can flow to the second working interface B from flowing into interface P, is closed being connected between interface P and the first working interface A and flow into.When dutycycle was worth TV1 to the 3rd value TV3 raising from first, volume flowrate continued to increase, and when its continued to second value TV2 raising, the volume flowrate continuous decrease also had been approximately zero in final arrival value TV2.Preferable methods is, for 130 zones of using between TV3 and the TV2, second control position.
Dutycycle in the 3rd zone between value TV2 and value TV4 is called as the maintenance dutycycle below, and volume flowrate is approximately zero.This zone is corresponding to the 3rd control position 131 of control valve 103, and in this position, two working interface A, B do not link to each other with inflow interface P.
When dutyfactor value from value TV4 continue to improve until 100% time, from flow into volume flowrate that interface P flow to pressure chamber 106,107 continue increase thereafter.Volume flowrate can continue to be elevated to 100% dutycycle, but is limited at all the time within the maximum value of design.This zone is corresponding to the 4th control position 132 of control valve 103, and in this position, pressure medium flows to the first working interface A from flowing into interface P, and flow between interface P and the second working interface B be connected blocked.
Under the situation that regulon 112 interrupts, when internal-combustion engine is reset, hydraulic type controlling device 102 is latched in the neutral position and keeps this locking, except this advantage, can also when regulon 112 is intact, realize when internal-combustion engine cuts out locking hydraulic type controlling device 102 or the location of realizing hydraulic type controlling device 102 so like this according to device 101 of the present invention, make and in the restarting of internal-combustion engine, can bring hydraulic type controlling device 102 into neutral position and be latched in there.Such advantage is, in starting process, the device 101 sufficiently be not full of as yet by pressure medium in, hydraulic type controlling device 102 reliably is latched in the neutral position, thereby avoid displaceable element 105 to collide the sidewall of pressure chamber 104, can avoid the enhancing and the noise that wear and tear thus.
Must know different dutycycles in order to drive internal-combustion engine, especially the maintenance dutycycle TV of TV1 to TV3 and engine controller
HalteKeep dutycycle from engine controller, to determine and be stored in the storage unit according to standard.In order to determine TV1, there are two possibilities in TV2 and TV3.
Can directly depend on maintenance dutycycle TV by note in the design and valve feature wherein
HalteDetermine TV1, TV2 and TV3.Declinate Y
1, Y
2With Y
3By permanent storage in storage unit.Engine controller can determine to keep dutycycle TV in the early stage of internal combustion engine operation
HalteTo TV1, TV2 and TV3:
TV1＝TV
Halte-Y1，
TV2＝TV
Halte-Y2，
TV3＝TV
Halte-Y3。
Second method be, equally after restarting at every turn, can be determined TV1 and TV2 and be placed in the combined characteristic by engine controller.In order to determine TV1 and TV3, can use camshaft angle signal and crankshaft angles signal.It is primary that what utilize is the variation along with the time of the relative phase of two axles and phase place.For example can transport in the following method.Promptly dutycycle is regulated from 0% toward high.When adjustment process begins (on this aspect, one of one of pressure chamber 106,107 and lockweight 110,111 are loaded pressure medium, and the hydraulic type controlling device is conditioned, and this can detect by camshaft angle sensor and crankshaft angle sensor) arrival value TV1.Arrival value TV3 when surpassing maximal regulated speed.Arrival value TV2 when phase place keeps constant.Fixed value is deposited in storage subsequently.
Fig. 7 shows is flow chart according to the controlling method of device 101 in the engine shutdown process of invention; can bring hydraulic type controlling device 102 into a position by it; in this position; hydraulic type controlling device 102 after internal-combustion engine stops or by locking, or after internal-combustion engine restarts, directly be pushed into the neutral position and be latched in the there.
Rotation speed n when the stopping process of internal-combustion engine begins＞zero.Phase place between camshaft and the bent axle
Be brought in the shutdown phase place this phase place and locking phase place by control valve 103
The value X that departs from a qualification.For the device 101 that is not equipped with counterbalance spring, shut down phase place with respect to the locking phase place
Move to direction " in advance ".Same reason has been suitable for being equipped with the device 101 of moment of torsion less than the counterbalance spring of the drag torque of camshaft.The moment of torsion that applies for having is shut down phase place with respect to the locking phase place greater than the device 101 of the counterbalance spring of the drag torque of camshaft
Move to direction " hysteresis ".When reaching preassigned shutdown phase place, ignition system is closed, and dutyfactor value is conditioned, thereby keeps this phase place reliably
To shut down phase place when " preceding " regulated, dutycycle will shut down phase place with respect to the locking phase place between TV2 and 100%
When " back " regulated, dutycycle was between TV3 and TV4.This dutycycle will be kept, and be zero up to speed probe notice rotating speed.After this, before regulon 112 outages dutycycle that is conditioned is kept definite time lag Y.The endurance of Y stoped internal-combustion engine is last rotate during, speed probe notified rotation speed n=0 o'clock, because the pressure surge that produces by alternation moment makes lockweight 110,111 be pushed in the wrong position by the neutral position by disengagement and displaceable element 105.Hydraulic type controlling device 102 or be in blocking because of the last rotation of bent axle, be in the another one position, in this position, follow starting of internal-combustion engine, it pushes in the locked position of coupler automatically and at once by the drag torque of camshaft or by the moment of torsion of counterbalance spring.
Fig. 3 shows is to be used for starting the flow chart that has according to the method for the internal-combustion engine of the device 101 of invention, can guarantee to allow the locking of displaceable element 105 that existed or between bent axle on-stream period for the first time be held by this method, rise to the required value of device 101 safe handlings up to the oil pressure of internal combustion engines.For the beginning of starting process, rotation speed n and dutycycle equal zero.As long as speed probe notice rotation speed n=zero, dutycycle just be maintained at 0% and value TV1 between.If speed probe notice rotating speed＞zero, the value that just can read oil pressure sensor.As long as the value of oil pressure p drives according to the required minimum value p that determines of the device 101 of invention than reliable
MinLittle, dutyfactor value just be maintained at 0% and value TV1 between.When oil pressure p surpassed setting pressure, device 101 changed the transmission that is conditioned over to, and dutycycle is conditioned between TV3 and 100% according to the load condition of machine.
Just some typical implementing methods that the front is told about.Working interface A, B also can exchange certainly.Device 101 with neutral position locking of hydraulic type controlling device 102 should all be included within the protection domain, wherein can only allow a lockweight be engaged in chute or the ladder type chute.Equally, on any one locking phase place, has the device of one or more lockweights also within protection scope of the present invention.Can ignore the pressure loss that causes because leak when between observation volume flowrate and valve distinct interface, connecting.
Reference numeral
1 device
1a fluid pressure type adjusting device
2 stators
3 rotors
4 driving wheels
5 spaces
6 sidewalls
7 first side covers
8 second side covers
9 Connection Elements
10 wing grooves
11 wings
12 first pressure chambers
13 second pressure chambers
14 bottom lands
15 leaf spring elements
16 first pressure pipes
17 second pressure pipes
21 first arrows
22 central holes
23 concavo-convex bodies
24 blocking elements
25 axial bores
26 pistons
27 springs
28 expulsion elements
29 chutes
30 ditches
101 devices
102 hydraulic type controlling devices
103 control valves
104 pressure chambers
105 elements
106 first pressure chambers
107 second pressure chambers
108 first chutes
109 second chutes
110 first lockweights
111 second lockweights
112 regulons
113 first spring elements
114 valve bodies
115 first pressure pipes
116 second pressure pipes
117 pressure medium containers
118 pressure medium pump
119 filters
120 safety check
121 the 3rd pressure pipes
122 the 4th pressure pipes
126 second arrows
127 first springs
128 the 3rd arrows
129 second springs
130 second control positions
131 the 3rd control positions
132 the 4th control positions
133 backstops
140 first control positions
141 valve pockets
142 control pistons
143 circular grooves
144 circular grooves
145 circular grooves
146 first radial openings
146a second radial opening
147 second spring elements
148 push rods
149 first end of stroke
150 second end of stroke
151 first piston ring banks
152 second piston ring lands
153 first control edges
154 second control edges
155 the 3rd control edges
156 the 4th control edges
157 the 4th circular grooves
158 the 3rd piston ring lands
P flows into interface
T flows out interface
A first working interface
B second working interface
The locking phase place
The X value
Y
1Declinate
Y
2Declinate
Y
3Declinate
TV
HalteKeep dutycycle
p
MinOil pressure
Claims (3)
1. be used for changing the controlling method at the device (101) in control time of engine shutdown process gas exchange valves of internal combustion engine door, this internal-combustion engine is furnished with
-hydraulic type controlling device (102), it has two synergistic pressure chambers (106,107),
-wherein by pressure medium being imported and deriving pressure chamber (106,107), can keep or on purpose change the phase place of camshaft with respect to bent axle
-internal-combustion engine also is furnished with one and has two working interface (A, B), one flows out interface (T) and a control valve (103) that flows into interface (P), wherein first working interface (A) communicates with first pressure chamber (106), second working interface (B) communicates with second pressure chamber (107), flow out interface (T) and communicate, flow into interface (P) and be loaded pressure medium with water tank;
-wherein control valve (103) can be utilized regulon (112) and brings four kinds of control positions (130,131,132,140) into;
-wherein in first control position (140) of control valve (103), inflow interface (P) neither communicates with first working interface (A) and does not also communicate with second working interface (B);
-in second control position (130) of control valve (103), first working interface (A) communicates with flowing out interface (T), and second working interface (B) communicates with inflow interface (P);
-in the 3rd control position (131) of control valve (103), first and second working interface (A B) neither communicates and does not also communicate with flowing into interface (P) with flowing out interface (T), perhaps first and second working interface (A, B) only with flow into interface (P) and communicate;
-in the 4th control position (132) of control valve (103), second working interface (B) communicates with flowing out interface (T), and first working interface (A) communicates with inflow interface (P); It is characterized in that, implement following method step successively:
-the phase place of starting and keeping an appointment
-close ignition system,
-regulate the second or the 4th control position (130,132), to keep phase place
Up to revolution speed sensing device notice rotation speed n=0,
-detect rotation speed n by the revolution speed sensing device,
-control position (130,132) that obtains is kept the time lag given in advance,
-at later inactive regulon (112) of the time lag.
2. be used for changing the controlling method at the device (101) in control time of engine shutdown process gas exchange valves of internal combustion engine door, this internal-combustion engine is furnished with
-hydraulic type controlling device (102), it has two synergistic pressure chambers (106,107),
-wherein by pressure medium being imported and deriving pressure chamber (106,107), can keep or on purpose change the phase place of camshaft with respect to bent axle
-internal-combustion engine also is furnished with one and has two working interface (A, B), one flows out interface (T) and a control valve (103) that flows into interface (P), wherein first working interface (A) communicates with first pressure chamber (106), second working interface (B) communicates with second pressure chamber (107), flow out interface (T) and communicate, flow into interface (P) and be loaded pressure medium with water tank;
-wherein control valve (103) can be utilized regulon (112) and brings four kinds of control positions (130,131,132,140) into;
-wherein in first control position (140) of control valve (103), inflow interface (P) neither communicates with first working interface (A) and does not also communicate with second working interface (B);
-in second control position (130) of control valve (103), first working interface (A) communicates with flowing out interface (T), and second working interface (B) communicates with inflow interface (P);
-in the 3rd control position (131) of control valve (103), first and second working interface (A B) neither communicates and does not also communicate with flowing into interface (P) with flowing out interface (T), perhaps first and second working interface (A, B) only with flow into interface (P) and communicate;
-in the 4th control position (132) of control valve (103), second working interface (B) communicates with flowing out interface (T), and first working interface (A) communicates with inflow interface (P); It is characterized in that, implement following method step successively:
-adjusting first control position,
The rotation speed n of-detection bent axle or camshaft,
If-rotation speed n＞0, detected pressures pressure medium p then,
If-pressure of pressure medium p greater than value given in advance, then regulates the control position according to the combined characteristic that is stored in the control unit.
3. be used for changing the controlling method at the device (101) in control time of engine shutdown process gas exchange valves of internal combustion engine door, this internal-combustion engine is furnished with
-hydraulic type controlling device (102), it has two synergistic pressure chambers (106,107),
-wherein by pressure medium being imported and deriving pressure chamber (106,107), can keep or on purpose change the phase place of camshaft with respect to bent axle
-internal-combustion engine also is furnished with one and has two working interface (A, B), one flows out interface (T) and a control valve (103) that flows into interface (P), wherein first working interface (A) communicates with first pressure chamber (106), second working interface (B) communicates with second pressure chamber (107), flow out interface (T) and communicate, flow into interface (P) and be loaded pressure medium with water tank;
-wherein control valve (103) can be utilized regulon (112) and brings four kinds of control positions (130,131,132,140) into;
-wherein in first control position (140) of control valve (103), inflow interface (P) neither communicates with first working interface (A) and does not also communicate with second working interface (B);
-in second control position (130) of control valve (103), first working interface (A) communicates with flowing out interface (T), and second working interface (B) communicates with inflow interface (P);
-in the 3rd control position (131) of control valve (103), first and second working interface (A B) neither communicates and does not also communicate with flowing into interface (P) with flowing out interface (T), perhaps first and second working interface (A, B) only with flow into interface (P) and communicate;
-in the 4th control position (132) of control valve (103), second working interface (B) communicates with flowing out interface (T), and first working interface (A) communicates with inflow interface (P); It is characterized in that, during stopping process, implement following method step successively:
-the phase place of starting and keeping an appointment
-close ignition system,
-regulate the second or the 4th control position (130,132), to keep phase place
Up to revolution speed sensing device notice rotation speed n=0,
-detect rotation speed n by the revolution speed sensing device,
-control position (130,132) that obtains is kept the time lag given in advance,
-at later inactive regulon (112) of the time lag;
And during starting process, implement following method step successively:
-adjusting first control position,
The rotation speed n of-detection bent axle or camshaft,
If-rotation speed n＞0, detected pressures pressure medium p then,
If-pressure of pressure medium p greater than value given in advance, then regulates the control position according to the combined characteristic that is stored in the control unit.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102004049123A DE102004049123A1 (en) | 2004-10-07 | 2004-10-07 | Device for changing the timing of gas exchange valves of an internal combustion engine |
| DE102004049123.2 | 2004-10-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101040102A CN101040102A (en) | 2007-09-19 |
| CN100529335C true CN100529335C (en) | 2009-08-19 |
Family
ID=35170006
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800345078A Expired - Fee Related CN100529335C (en) | 2004-10-07 | 2005-09-03 | Device for modifying the timing of gas exchange valves in an internal combustion engine |
Country Status (6)
| Country | Link |
|---|---|
| EP (2) | EP1797285B1 (en) |
| JP (1) | JP4982867B2 (en) |
| KR (1) | KR101201609B1 (en) |
| CN (1) | CN100529335C (en) |
| DE (3) | DE102004049123A1 (en) |
| WO (1) | WO2006039966A1 (en) |
Families Citing this family (20)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102008056796A1 (en) | 2008-11-11 | 2010-05-12 | Schaeffler Kg | Rotary piston adjuster with torsion spring |
| DE102009008056A1 (en) | 2009-02-09 | 2010-08-12 | Schaeffler Technologies Gmbh & Co. Kg | Control valves for controlling pressure medium flows |
| DE102009009252B4 (en) | 2009-02-17 | 2017-10-26 | Schaeffler Technologies AG & Co. KG | Hydraulic camshaft adjuster with axial screw plug |
| CN101655020B (en) * | 2009-09-21 | 2012-03-21 | 芜湖杰锋汽车动力系统有限公司 | Novel mechanical variable tappet mechanism and control method thereof |
| DE102009051310A1 (en) | 2009-10-29 | 2011-05-05 | Schaeffler Technologies Gmbh & Co. Kg | Fastening arrangement of a camshaft adjuster |
| DE102009054051A1 (en) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Switchable device for pressure supply with passive additional pressure accumulator |
| DE102009054052B4 (en) | 2009-11-20 | 2018-08-23 | Schaeffler Technologies AG & Co. KG | Switchable device for pressure supply |
| DE102009054050A1 (en) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Switchable device for supplying pressure to lubricating oil system of internal-combustion engine, has braking device switched into switched-off condition, in which rotating motion of screw pillar is not prevented |
| DE102009054055A1 (en) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Switchable device for pressure supply |
| DE102009054053A1 (en) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Pressure reservoir for hydraulic system, has housing, movable element and energy storage, where movable element is arranged within housing |
| DE102009054048A1 (en) | 2009-11-20 | 2011-05-26 | Schaeffler Technologies Gmbh & Co. Kg | Assembly for mounting hydraulic rotary piston adjuster i.e. belt camshaft adjuster, in internal combustion engine, has fastening screws formed as adjusting screws for adjusting locking play and connecting plates in both directions |
| DE102010045358A1 (en) * | 2010-04-10 | 2011-10-13 | Hydraulik-Ring Gmbh | Schwenkmotornockenwellenversteller with a hydraulic valve |
| DE102010063390A1 (en) | 2010-12-17 | 2012-06-21 | Schaeffler Technologies Gmbh & Co. Kg | Pressure accumulator unit for supporting e.g. camshaft for supporting during starting engine of vehicle, has guide comprising hollow-cylinder-shaped base element and ring-shaped bearing element that is arranged between base element and rod |
| DE102011005472A1 (en) | 2011-03-14 | 2012-09-20 | Schaeffler Technologies Gmbh & Co. Kg | Accumulator unit for a camshaft and reciprocating piston for an accumulator unit |
| JP5990061B2 (en) * | 2011-09-20 | 2016-09-07 | 日立オートモティブシステムズ株式会社 | Control device for variable valve mechanism |
| DE102012200685B4 (en) * | 2012-01-18 | 2020-10-22 | Schaeffler Technologies AG & Co. KG | Valve arrangement for camshaft adjuster |
| CN104121051B (en) * | 2013-04-26 | 2016-03-30 | 重庆长安汽车股份有限公司 | A kind of oil circuit device of motor car engine VVT |
| CN103850743B (en) * | 2014-04-02 | 2016-01-06 | 广西玉柴机器股份有限公司 | Variable Valve Time drive unit |
| US9410453B2 (en) | 2014-10-21 | 2016-08-09 | Ford Global Technologies, Llc | Method and system for variable cam timing device |
| CN113107636B (en) * | 2021-05-14 | 2022-08-05 | 北京理工大学 | Two-section type hydraulic tappet, two-section type variable valve lift mechanism and control method thereof |
Family Cites Families (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3351090B2 (en) * | 1994-03-31 | 2002-11-25 | 株式会社デンソー | Valve timing control device for internal combustion engine |
| JP3666072B2 (en) * | 1995-09-13 | 2005-06-29 | アイシン精機株式会社 | Switching valve |
| DE19854891C2 (en) * | 1997-11-28 | 2003-02-06 | Aisin Seiki | Valve timing control device |
| JP4081893B2 (en) * | 1997-11-28 | 2008-04-30 | アイシン精機株式会社 | Valve timing control device |
| JPH11280427A (en) * | 1998-03-31 | 1999-10-12 | Aisin Seiki Co Ltd | Control device for valve opening/closing timing |
| JP3918971B2 (en) * | 1998-04-27 | 2007-05-23 | アイシン精機株式会社 | Valve timing control device |
| JP3925672B2 (en) * | 1998-05-28 | 2007-06-06 | アイシン精機株式会社 | Valve timing control device |
| DE19853670C5 (en) * | 1998-11-20 | 2019-01-10 | Hilite Germany Gmbh | Camshaft adjustment device |
| JP2001050063A (en) * | 1999-08-05 | 2001-02-23 | Denso Corp | Variable valve timing control device for internal combustion engine |
| JP4103277B2 (en) * | 1999-12-06 | 2008-06-18 | 株式会社デンソー | Variable valve timing control device for internal combustion engine |
| DE10064222B4 (en) | 1999-12-24 | 2006-02-09 | Aisin Seiki K.K., Kariya | Adjustable valve control system |
| JP2001254638A (en) * | 2000-03-10 | 2001-09-21 | Honda Motor Co Ltd | Valve timing control device of internal combustion engine |
| JP2001329812A (en) * | 2000-05-19 | 2001-11-30 | Mitsubishi Motors Corp | Variable valve system |
| JP2002030909A (en) * | 2000-07-18 | 2002-01-31 | Toyota Motor Corp | Valve timing control device of internal combustion engine |
| JP4457284B2 (en) * | 2001-02-21 | 2010-04-28 | アイシン精機株式会社 | Valve timing control device |
| DE10213831A1 (en) * | 2001-03-28 | 2002-11-07 | Denso Corp | Variable valve timing device |
| JP2002327607A (en) * | 2001-04-27 | 2002-11-15 | Unisia Jecs Corp | Valve timing control device for internal combustion engine |
| JP4007071B2 (en) * | 2002-05-29 | 2007-11-14 | トヨタ自動車株式会社 | Valve opening / closing timing control device |
-
2004
- 2004-10-07 DE DE102004049123A patent/DE102004049123A1/en not_active Withdrawn
-
2005
- 2005-09-03 DE DE502005008502T patent/DE502005008502D1/en active Active
- 2005-09-03 EP EP05782451A patent/EP1797285B1/en not_active Not-in-force
- 2005-09-03 CN CNB2005800345078A patent/CN100529335C/en not_active Expired - Fee Related
- 2005-09-03 JP JP2007535034A patent/JP4982867B2/en not_active Expired - Fee Related
- 2005-09-03 KR KR1020077007842A patent/KR101201609B1/en active IP Right Grant
- 2005-09-03 EP EP08150439A patent/EP1914395B1/en not_active Not-in-force
- 2005-09-03 DE DE502005007868T patent/DE502005007868D1/en active Active
- 2005-09-03 WO PCT/EP2005/009487 patent/WO2006039966A1/en active Application Filing
Also Published As
| Publication number | Publication date |
|---|---|
| EP1797285A1 (en) | 2007-06-20 |
| CN101040102A (en) | 2007-09-19 |
| DE102004049123A1 (en) | 2006-04-13 |
| KR20070100231A (en) | 2007-10-10 |
| EP1797285B1 (en) | 2009-11-11 |
| JP2008516129A (en) | 2008-05-15 |
| JP4982867B2 (en) | 2012-07-25 |
| WO2006039966A1 (en) | 2006-04-20 |
| EP1914395A1 (en) | 2008-04-23 |
| KR101201609B1 (en) | 2012-11-14 |
| DE502005008502D1 (en) | 2009-12-24 |
| EP1914395B1 (en) | 2009-08-05 |
| DE502005007868D1 (en) | 2009-09-17 |
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