CN101918680A - Apparatus for variably adjusting the control times of gas exchange valves in an internal combustion engine - Google Patents

Apparatus for variably adjusting the control times of gas exchange valves in an internal combustion engine Download PDF

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Publication number
CN101918680A
CN101918680A CN2008801175326A CN200880117532A CN101918680A CN 101918680 A CN101918680 A CN 101918680A CN 2008801175326 A CN2008801175326 A CN 2008801175326A CN 200880117532 A CN200880117532 A CN 200880117532A CN 101918680 A CN101918680 A CN 101918680A
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CN
China
Prior art keywords
pressure
chamber
pressure medium
accumulator
control
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Pending
Application number
CN2008801175326A
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Chinese (zh)
Inventor
约亨·奥克特
安德烈亚斯·亨普夫林
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of CN101918680A publication Critical patent/CN101918680A/en
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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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type
    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • 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
    • F01L13/0005—Deactivating valves
    • 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
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • 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
    • F01L2001/34446—Fluid accumulators for the feeding circuit

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The invention relates to an apparatus (10) for variably adjusting the control times of gas exchange valves (9a, b) in an internal combustion engine (1). Said apparatus (10) comprises a driving element (22), an output element (23), at least one pressure chamber (35, 36), a pressurized medium supply device (37), and at least one pressure accumulator (43). The pressurized medium supply device (37) allows pressurized medium to be fed to or discharged from the at least one pressure chamber (35, 36). A phase angle of the output element (23) relative to the input element (22) can be changed by feeding or discharging pressurized medium to or from the pressure chamber (35, 36). The pressure accumulator (43) encompasses a movable element (45) that has a first pressure surface (47) which partially delimits a storage space (49). The storage space (49) is or can be connected to the pressurized medium supply device (37). An energy store applies a force to the movable element (45) in the direction of an initial position. The movable element (45) can be moved against the force of the energy store (46) by pressurizing the storage space (49).

Description

Be used for the gas exchange valves of internal combustion engine port timing is carried out the device of variable adjustment
Technical field
The present invention relates to a kind of device that is used for the gas exchange valves of internal combustion engine port timing is carried out variable adjustment, this device has driving component, driven member, at least one pressure chamber, pressure medium supply unit and at least one accumulator, wherein, by pressure medium supply unit can at least one pressure chamber's discharge pressure medium or from this pressure chamber the head pressure medium, wherein, by to pressure chamber's discharge pressure medium or from the pressure chamber head pressure medium, can change the phase place of driven member with respect to driving component, wherein, accumulator has displaceable element, this element has first pressure side that partly defines reserve chamber, wherein, reserve chamber is connected with pressure medium supply unit or can be attached thereto, wherein, accumulator imposes power towards the direction of initial position to displaceable element, and wherein, by reserve chamber is exerted pressure, displaceable element is moved against trying hard to recommend of accumulator.
Background technique
In the internal-combustion engine in modern times, use the device that the scavenging air valve port timing is carried out variable adjustment, in the angular range that limits so that the phase relationship between bent axle and the camshaft is being constituted between position and the maximum slow position the most very early in the morning changeably.This device generally includes regulating device, this regulating device by the bent axle transmission and with the transmission of torque of regulating device to camshaft.At this, constitute the hydraulic servo drive unit in the inside of regulating device, the hydraulic servo drive unit can exert an influence to the phase place between bent axle and the camshaft targetedly.In order to provide pressure medium, be provided with pressure medium supply unit to regulating device.
This device is for example known by EP 1 025 343 B1.This device comprises two rotors that can reverse toward each other, and wherein, external rotor is in transmission connection with bent axle and internal rotor is connected with camshaft is antitorque.This device comprises a plurality of cavitys, and wherein, each cavity is divided into the pressure chamber of two relativities by blade.By to pressure chamber's discharge pressure medium or from the pressure chamber head pressure medium, therefore blade is pushed in the inside of pressure chamber, rotor is reversed toward each other targetedly and camshaft and bent axle reverse targetedly.
All control by pressure medium supply unit to pressure chamber's discharge pressure medium or from pressure chamber's head pressure medium, this pressure medium supply unit comprises pressure medium pump, fuel tank, control valve and a plurality of pressure medium pipeline.At this, a pressure medium pipeline is connected pressure medium pump with control valve.Each other pressure medium pipeline is connected one of working interface of control valve with the pressure chamber.Pressure medium is taken from the lubricant medium loop of internal-combustion engine usually.
For guaranteeing the function of this device, the pressure in the pressure medium system all must surpass the numerical value of determining in each operation phase of internal-combustion engine.This point is particularly abnormally dangerous in the idling stage of internal-combustion engine, this be because pressure medium pump by the bent axle transmission and therefore system pressure rise along with the rotating speed of internal-combustion engine.The system pressure that is provided by pressure medium pump also depends on the pressure medium temperature, and wherein, system pressure descends under the situation that temperature rises.Therefore pressure medium pump must design as follows, that is, pressure medium pump also provides enough system pressures under worst condition, enough apace the phase place of internal rotor and external rotor is adjusted guaranteeing.Even for also guaranteeing desired regulating the speed in (under high pressure medium temperature and/or slow-revving situation) under the worst pressure condition, pressure medium pump must correspondingly therewith design.This point causes using following pressure medium pump, and this pressure medium pump designs and therefore crosses during most operation phase of internal-combustion engine and set size greatly according to the peak demand of regulating device.Alternatively, can use adjustable pressure medium pump, this pressure medium pump provides pressure medium according to demand.The spending of Zeng Jiaing has a negative impact to cost, structure space demand and the fuel consumption of internal-combustion engine in both cases.
US 5,775, and 279A discloses another kind of this type of device.In this embodiment, be provided with the accumulator that is communicated with pressure medium supply unit between pressure medium pump and the control valve.This accumulator is at the high stage filling pressure medium of system pressure.If system pressure descends, so automatic emptying accumulator, pressure medium supply unit provides additional pressure medium thus.Therefore the adjustment mutually of this device is supported.The shortcoming of this mode of execution is, is not based on adjustment process at system pressure, and is based on other external circumstances, and for example under the situation about reducing by rotating speed, accumulator also is drained.Therefore can be for the pressure support of subsequently phase adjustment process use littler and still less from the pressure medium volume of accumulator.Another shortcoming is, pressure medium supply unit can be used for supporting the pressure maximum of accumulator to be equivalent to just be in the pressure in the pressure medium supply unit before the phase adjustment process.If engine controlling unit proposes to adjust requirement to this device under high temperature and slow-speed of revolution situation, the pressure support of accumulator stops so, because the system pressure that accumulator is annotated is very little.This point can cause implementing adjustment process or regulate the speed obviously descending.Therefore in this case, pressure medium pump also needs according to following the maximum load that produces defective thus to design.
Summary of the invention
The present invention is based on following task, that is, provide a kind of device that is used for the gas exchange valves of internal combustion engine port timing is carried out variable adjustment, wherein, should guarantee in each operation phase of internal-combustion engine under the situation that height is regulated the speed, port timing reliable in function ground is adjusted.At this, should be the same with the application of cancellation variable pressure medium pump, the oversized dimensions (designing) of cancellation pressure medium pump according to the maximum load of being estimated.
This task is achieved as follows according to the present invention, that is, displaceable element has the back pressure face that defines the back pressure chamber at least in part, wherein, by the medium of being exerted pressure in the back pressure chamber, displaceable element is moved towards the direction of initial position.Displaceable element for example can constitute pressure piston, and this pressure piston can move against trying hard to recommend of the accumulator that for example constitutes spring part in the inside of pressurized container.To reserve chamber discharge pressure medium the time, the volume of reserve chamber is that cost enlarges with the back pressure cavity space.If the system pressure in the pressure medium supply unit descends, the power of accumulator surpasses the power first pressure side, that produce by system pressure that acts on so.Therefore pressure piston is pressed into initial position by accumulator, in this initial position, and reserve chamber volume minimum.
As alternatively, also can use other forms of accumulator, for example by the possibility of reversal body that plays the colloid supporting or the capsule of inflation for spring part.The medium if exerted pressure during the operation phase of internal-combustion engine in the back pressure chamber, accumulator need be with the pressure medium dispatch to pressure medium supply unit during this period, act on so displaceable element except the power of accumulator, in addition this displaceable element is pressed to other power of initial position direction.Power that should be additional is from the pressure that acts on the back pressure face in the counter-pressure chamber.Amount F for this additional power is suitable for: F=pA G, wherein, p is equivalent to act on the pressure and the A of back pressure face GThe area that is equivalent to the back pressure face.
By the pressure that is provided by accumulator is provided, accumulator can be stabilized peak value consumption, thereby pressure medium pump can design according to the normal operation of internal-combustion engine.Do not need excessive setting size or adjusted pressure medium pump to guarantee phase place is carried out reliable in function and adjustment apace.Additional being improved of regulating the speed of regulating device.As selection, under the identical situation of regulating the speed, regulating device can be set size lessly.Reduce quality, moment of inertia and cost thus.
In improvement project of the present invention, displaceable element has at least one second pressure side that partly defines control chamber, wherein, pressurization by control chamber can make displaceable element move against trying hard to recommend of accumulator, and wherein, the internalized prohibition pressure medium at accumulator flows in the control chamber from reserve chamber.Can be set in addition, reserve chamber and control chamber are not interconnected in the inside of accumulator.What have advantage is, the same with medium that control chamber is exerted pressure to the reserve chamber medium of exerting pressure, and displaceable element is moved on identical direction, and what have advantage is to remove from the initial position of displaceable element.Have the structural scheme of following displaceable element by accumulator, this displaceable element partly defines the isolated each other pressure chamber in accumulator inside, and these two pressure chambers can be controlled separately, just filling and/or emptying.Unless leak, between pressure chamber, do not have connection.So for example different pressure sources can be used to annotate reserve chamber and control chamber.As selection, also can be provided with the pressure medium link between the reserve chamber of accumulator inside and the control chamber.The pressure medium that is transported to control chamber can enter in the reserve chamber by this pressure medium link.At this, need to guarantee: forbid the pressure medium flow conversely from the reserve chamber to the control chamber.This point for example can realize by the pressure piston of accumulator or the pressure medium channel in the pressurized container, be provided with safety check in this pressure medium channel.In this case, the filling of reserve chamber and control chamber is only undertaken by the filling to control chamber.If accumulator should emptying, so control chamber is switched to fuel tank.Reserve chamber is emptied in the pressure medium supply unit, is emptied in the fuel tank to the control chamber decompression.Prevent that by safety check pressure medium from overflowing in control chamber from reserve chamber.If be set to: the pressure medium of reserve chamber applied make displaceable element move applying on the identical direction with pressure medium to control chamber, control chamber can be supported to the filling of reserve chamber so.For this purpose, control chamber same filling pressure medium during the filling process of reserve chamber.Thus, the masterpiece that acts on this pressure piston is used for two pressure sides of pressure piston, thus, stores higher power (spring part is subjected to compressing more consumingly) in the accumulator.If the accumulator of being annotated is received instruction support phase adjustment process from engine controlling unit, control chamber can not rely on reserve chamber ground emptying so.That is to say, in reserve chamber is emptied to pressure medium supply unit and therefore, support during the phase adjustment process that control chamber can be against barometric pressure exhaust in fuel tank.By suitable design, the exhaust of control chamber can be carried out quickly than the emptying of reserve chamber in pressure medium supply unit.Therefore the whole power that are stored in the accumulator act on reserve chamber by first pressure side.As consequence, when supporting process began, pressure depends on the load that acts on accumulator on this time point can be to improve until following coefficient, and this coefficient is
A 1 + A 2 A 1 .
At this, A 1The area and the A that are equivalent to first pressure side 2The area that is equivalent to second pressure side.If for example use spring part as accumulator, so if spring also do not reach its maximum compressive state, pressure when supporting process begins just with complete (voll) coefficient
Figure GPA00001140644000052
Improve.
In improvement project of the present invention, the back pressure chamber can be connected with pressure source or with fuel tank selectively.Can have control mechanism, wherein, the back pressure chamber can be connected with fuel tank selectively or be connected with pressure source by control mechanism.At this, the back pressure chamber can be connected with the internal-combustion engine pressure medium pump.The back pressure chamber can be connected with the fuel tank of internal-combustion engine.
Pressure source for example can be the pressure medium pump of pressure medium supply unit or pressure medium supply unit or separated source, the pressure source of for example servo customer (for example servo steering spare).Under second kind of situation, in the operation phase of low system pressure, accumulator also can be annotated fully.Select to be connected by control mechanism with having of pressure source or fuel tank, the two-position three-way distribution valve that for example is distributing valve (for example seat valve (Sitzventil)) or Proportional valve (for example guiding valve) form produces.Also can consider two control mechanisms as selecting, wherein, the connection of the connection of the blocking-up of one of control mechanism or release pressure source-control chamber and the blocking-up of other control mechanism or release control chamber-fuel tank.Control mechanism for example can be the hydrovalve of eletromagnetic-operating, as selector valve (for example distributing valve or Proportional valve), can remove the safety check of blocking-up etc.These control mechanisms receive control signal from the engine controlling unit of internal-combustion engine, according to control signal annotated or emptying in the back pressure chamber, and just, be the accumulator or should support evacuation procedure of should annotating.Can consider to use the hydraulically operated control mechanism equally.At this, the apply device of control mechanism is communicated with pressure medium supply unit.The pressure of control mechanism in pressure medium supply unit drops under the situation under definite numerical value and automaticallyes switch like this.Obviously reduce thus and regulate spending.If the fuel tank and/or the pressure medium pump of internal-combustion engine are used for being annotated or exhaust in the back pressure chamber, the parts that in internal-combustion engine, already exist, need not miscellaneous part so.In addition, lower to the seal request between pressure medium container and the pressure piston, because the pressure medium of authorized pressure medium in reserve chamber and back pressure chamber mixes.Therefore can cancel the Sealing between pressure piston and the pressurized container.
Be set in addition, selector valve is set to control mechanism, and selector valve has each interface that is connected with pressure source, fuel tank and back pressure chamber.In improvement project of the present invention, can be provided with the other interface that is connected with reserve chamber or control chamber.
The pressure support of accumulator also can activate by switching one or more control mechanism simply.At this, following pressure medium volume is provided, in keeping constant operation phase, the internal-combustion engine phase place accumulates in the reserve chamber.The pressure support of accumulator can be used in each phase adjustment process.For this purpose, control mechanism (selector valve and/or can remove the safety check of blocking-up) always is admitted under the situation that requires to adjust mutually in the position of reserve chamber emptying.In the operation phase of adjusting mutually between requiring, can annotate to accumulator.Another kind of possibility is that the pressure support of accumulator depends on to be needed to connect.If the pressure that is provided by pressure medium pump is provided engine controlling unit or the volume flow of adjusting mutually is not enough, the transmitter control gear is supported by the accumulator release pressure so.Therefore the time that this way prolongation accumulator can be annotated also prolonged the application of accumulator during pressure is supported.As selection, the pressure support of accumulator can only for example needing be used for high volume flow or high critical adjustment process of regulating the speed as " supercharging (boost) " function.Need to start this critical adjustment process if engine controlling unit detects, this engine controlling unit comes the release pressure support by suitable adjustment control mechanism so.
Can consider that equally control mechanism and control valve constitute integratedly, this control valve flows into the pressure chamber of regulating device to pressure medium and controls from pressure chamber's outflow of regulating device.
What have advantage is, the maximum volume of reserve chamber is equivalent to from the slow position of maximum to adjust volume required twice mutually to position the most very early in the morning at least.Accumulator for example can feed in the pressure medium pipeline between pressure medium pump and the control valve.As selection, accumulator feeds in one of pressure medium pipeline, and this pressure medium pipeline is connected one of working interface of control valve with one group of pressure chamber.Additional in this embodiment second accumulator that is provided with, second accumulator feed in other working interfaces of control valve and the pressure medium pipeline that the pressure chamber of other groups is connected.
Description of drawings
Reach accompanying drawing acquisition other features of the present invention that the embodiment of the invention is shown by simplification by following specification.Wherein:
Fig. 1 only very schematically illustrates internal-combustion engine;
Fig. 2 a illustrates the longitudinal section of regulating device;
Fig. 2 b illustrates the cross section of regulating device;
Fig. 3 illustrates this device according to first mode of execution of the present invention;
Fig. 4 illustrates this device according to second mode of execution of the present invention;
Fig. 5 illustrates this device according to the 3rd mode of execution of the present invention.
Embodiment
Fig. 1 medium-height grass is drawn internal-combustion engine 1, and wherein, the piston 3 that is placed on the bent axle 2 illustrates in cylinder 4.Bent axle 2 is connected with inlet cam axle 6 or outlet camshaft 7 by each traction mechanism drive 5 in the embodiment shown, and wherein, first device and second device 10 can be responsible for relatively rotating between bent axle 2 and camshaft 6,7.This device 10 comprises separately hydraulic adjustment device 10a, a b and pressure medium supply unit 37.The cam 8 of camshaft 6,7 is operated one or more import scavenging air valve 9a or one or more outlet scavenging air valve 9b.Can be set to equally: in the camshaft 6,7 only one be equipped with device 10 only to be provided with a camshaft 6,7 that device 10 is housed in other words.
Fig. 3 illustrates first mode of execution according to device 10 of the present invention, has regulating device 10a, b, pressure medium supply unit 37 and accumulator 43.Fig. 2 a and 2b illustrate regulating device 10a, b with longitudinal section and cross section.Regulating device 10a, b have the driving component that constitutes external rotor 22 and constitute the driven member of internal rotor 23.External rotor 22 has housing 22a and two side covers 24,25, and side cover 24,25 is arranged on the axial sides of housing 22a.Internal rotor 23 constitutes and has the hub spare 26 of cylindrical enforcement basically with the form of impeller, in the embodiment shown, from the housing face diameter of the external cylindrical of hub spare 26 to extending outward five blades 27.Blade 27 constitutes dividually with internal rotor 23 and is arranged in the blade groove 28, and blade groove 28 is configured on the hub spare 26.Blade 27 applies power by the leaf spring 27a radially outward between groove bottom that is arranged on blade groove 28 and the blade 27.
From the outer periphery wall 29 of housing 22a, extend radially inwardly out a plurality of lug bosses 30.In the embodiment shown, lug boss 30 constitutes integratedly with periphery wall 29.External rotor 22 is rotatably supported on this internal rotor 23 with respect to internal rotor 23 by the radially built-in periphery wall of lug boss 30.
The external shell dignity of periphery wall 29 is provided with sprocket wheel 21, torque can be delivered on the external rotor 22 from bent axle 2 by unshowned chain transmission by this sprocket wheel 21.
Each side cover 24,25 is arranged on one of axial sides of housing 22a and goes up and antitorque being fixed on this axial sides.For this purpose, be provided with axially open in each lug boss 30, this axially open is run through by for example fixed block 32 of bolt, and fixed block 32 is used for side cover 24,25 is fixed on housing 22a antitorquely.
In regulating device 10a, b inside, at the formation cavity 33 between the adjacent lug boss 30 that makes progress in each two week.Each cavity 33 was upwards defined by the opposed radially-arranged basically wall 34 that defines of adjacent protrusion portion 30 in week, side cover 24,25 axially on radially inwardly define and radially outward is defined by periphery wall 29 by hub spare 26.Blade 27 stretches in each cavity 33, and wherein, blade 27 constitutes as follows, that is, blade 27 had both abutted on the side cover 24,25, also abutted on the periphery wall 29.Therefore, therefore each blade 27 is divided into two pressure chambers 35,36 of effect toward each other with cavity 33 separately.
Internal rotor 23 is to rotate with respect to external rotor 22 in the angular range of determining.This angular range is defined on the sense of rotation of internal rotor 23 as follows, that is, blade 27 abuts in the defining on the wall 34 (backstop 34a early) of each correspondence of cavity 33.Similarly, this angular range defines on another sense of rotation as follows, that is, blade 27 abuts in cavity 33 and defines on the wall 34 as another of slow backstop 34b.
By 35,36 pressurizations of one group of pressure chamber and another group pressure release, can change the phase place of external rotor 22 with respect to internal rotor 23.By 35,36 pressurizations of two groups of pressure chambers, the phase place of two rotors 22,23 is remained unchanged each other.Alternatively can be set to, during the constant phase place stage, pressure chamber 35,36 pressure medium of not annotating.Usually use the pressure medium of the lubricant oil of internal-combustion engine 1 as hydraulic pressure.
For to pressure chamber's 35,36 delivery hydraulic pressure media or from the pressure chamber 35,36 released liquor piezodielectrics, be provided with pressure medium supply unit shown in Figure 3 37.Pressure medium supply unit 37 comprises pressure source, fuel tank 39, control valve 40 and a plurality of pressure medium pipeline 41 that constitutes pressure medium pump 38.Control valve 40 has input interface P, fuel tank interface T and two working interface A, B.Each pressure medium pipeline 41 is connected pressure medium pump 38, the first working interface A is connected with first pressure chamber 35, the second working interface B is connected with second pressure chamber 36 and fuel tank interface T is connected with fuel tank 39 with input interface P.Therefore, pressure medium can arrive the input interface P of control valve 40 from pressure medium pump 38 via pressure medium pipeline 41.On the primary importance of control valve 40, input interface P is connected with first pressure chamber 35, and second pressure chamber 36 then is connected with fuel tank 39.Be set on the second place of control valve 40, pressure chamber 35,36 is not communicated with fuel tank 39 and input interface P.On the 3rd position of control valve 40, input interface P is connected with second pressure chamber 36, and first pressure chamber 35 then is connected with fuel tank 39.
At internal-combustion engine 1 duration of work, the conversion moment loading that causes by the rolling of cam 8 on cam auxiliary equipment (Nockenfolger) is in camshaft 6,7.At this, the power of valve spring until scavenging air valve open fully and inhibition act on camshaft 6,7.Subsequently, camshaft 6,7 power by valve spring are accelerated.The result is: the inside of regulating device 10a, b produces pressure peak, and the pressure chamber 35,36 that this pressure peak causes being connected with input interface P is to pressure medium pump 38 emptyings, thereby it is obviously slack-off to cause regulating the speed.For preventing this point, be provided with safety check 42a with in pressure medium pump 38 and the pressure medium pipeline 41 that control valve 40 is connected.Safety check 42a stops pressure medium 35,36 to reflux to pressure medium pump 38 via control valve 40 from the pressure chamber.Pressure peak is supported on safety check 42a, effectively prevents pressure chamber's 35,36 undesirable emptyings thus also therefore, and the rigidity of transmission of torque is improved with regulating the speed.
Pressure that pressure medium pump 38 provided or the pressure medium volume flow that is provided are provided for the regulating the speed of regulating device 10a, b.Pressure that is provided or the pressure medium volume flow that is provided depend on a large amount of factors aspect that at it, for example the rotating speed of internal-combustion engine 1 and pressure medium temperature.Even under worst situation, for example also guarantee desired regulating the speed when the image height pressure medium temperature and/or the slow-speed of revolution, pressure medium pump 38 is respective design therewith.This point causes using that the peak demand according to regulating device 10a, b designs and the therefore pressure medium pump of excessive setting size during most operation phase of internal-combustion engine 1.Also can use adjustable pressure medium pump 38 as selecting, pressure medium pump 38 provides pressure medium as required.The spending of Zeng Jiaing has a negative impact for the cost and the fuel consumption of internal-combustion engine in both cases.
For avoiding these shortcomings, be provided with accumulator 43 according to device 10 of the present invention.Accumulator 43 comprises the displaceable element that is embodied as pressure piston 46, and this displaceable element can move against trying hard to recommend of accumulator in the inside of pressurized container 44.In the embodiment shown, accumulator constitutes spring part 46.But also can consider the accumulator of other types, for example as the bullet colloid of suitably moulding or the capsule of inflation.
Pressure piston 45 has two pressure sides 47,48.First pressure side 47 defines reserve chamber 49 jointly with pressurized container 44, and wherein, first pressure side 47 defines reserve chamber 49 on the movement direction of pressure piston 45.Pressurized container 44 and pressure piston 45 define control chamber 50, and wherein, second pressure side 48 defines control chamber 50 equally on the movement direction of pressure piston 45.At this, pressure piston 45 and pressurized container 44 constitute as follows,, in the inside of accumulator 43, do not have being connected between two chambers 49 and 50 that is.Unless leak, the pressure medium exchange do not take place between these pressure chambers 49,50 in the embodiment shown.In the embodiment shown, pressure side 47,48 is provided with on the movement direction of pressure piston 45 each other with staggering, and wherein, first pressure side 47 is centered on by second pressure side 48 in the plane that the movement direction by pressure piston 45 vertically passes through.First pressure side 47 constitutes circularly and second pressure side 48 constitutes ringwise.By medium that pressure chamber 49,50 is exerted pressure, pressure piston 45 moves against trying hard to recommend of spring part 46, and the volume of pressure chamber 49,50 rises thus.Pressure piston 45 can define by the backstops 54 in pressurized container 44 inner formations against the stroke that spring part 46 moves.Backstop 54 is provided with as follows, that is, backstop 54 stops reserve chamber 49 to be connected with control chamber 50.
Spring part 46 1 sides are supported on the side that deviates from pressure chamber 49,50 of pressure piston 45 and opposite side is supported on the side that deviates from pressure chamber 49,50 of pressurized container 44.At this, the spring part 46 with lug boss is assemblied in the accumulator 43, thereby the volume of pressure chamber 49,50 is minimum under the situation of low system pressure.On this initial position, pressure piston 45 abuts on the pressurized container 44 on it deviates from the side of spring part 46.
The zone that deviates from pressure side 47,48 of pressurized container 44 is constituted pressure chamber (back pressure chamber).At this, the face towards back pressure chamber 58 of pressure piston 45 constitutes back pressure face 59.By the medium of being exerted pressure in back pressure chamber 58, via back pressure face 59, the masterpiece parallel with the power of spring part 46 is used for pressure piston 45.In the embodiment shown, back pressure face 59 flatly constitutes, and wherein, this back pressure face 59 is with the mode orientation perpendicular to the moving direction of pressure piston 45.Can consider that equally the face or the back pressure face 59 that are proposed have other functors, thereby this functor is different with smooth form.On back pressure face 59, for example constitute holder like this for spring part 46.
Reserve chamber 49 is connected with pressure medium supply unit 37 by deposit pipeline 51.Deposit pipeline 51 feeds in the pressure medium supply unit 37 in the downstream of safety check 42a on the one hand and feeds in the reserve chamber 49 by interface 56 on the other hand.Be provided with safety check 42c at deposit in the pipeline, safety check 42c allows from reserve chamber 49 to the pressure medium flow of pressure medium supply unit 37 and stop opposite pressure medium flow.What reach thus is: the pressure peak that produces in regulating device 10a, the b can not be marched forward until the reserve chamber 49 of accumulator 43, but is supported on safety check 42c.Therefore, improved and installed 10 hydraulic pressure rigidity.
Control chamber 50 can be connected with fuel tank 39 or be connected with pressure source by pilot line 52 selectively.In the embodiment shown, the pressure medium pump 38 of working pressure medium supply apparatus 37 is as pressure source.But be contemplated that equally, use other pressure source, for example as the pressure medium pump 38 of servo customer (Servoverbraucher) (for example servo steering spare).In this case, the pressure medium that flows out from control chamber 50 is not the fuel tank 39 that imports internal-combustion engine 1 oil circuit, but the corresponding fuel tank 39 of the servo customer that leads.Be provided with another safety check 42b in the pilot line 52, safety check 42b prevents that pressure medium from refluxing to pressure medium supply unit 37 from control chamber 50.
Control in order pressure medium to be flowed into control chamber 50 and back pressure chamber 58 and from control chamber 50 and back pressure chamber 58, to flow out, be provided with the control mechanism 60 that is selector valve 53 forms.Selector valve 53 constitutes two position and four-way reversing valves and has pressure interface P 1, two working interface A 1, B 1With fuel tank interface T 1Pressure interface P 1Be connected with pressure source, in the embodiment shown, be connected with pressure medium supply unit 37 by pilot line 52.The 3rd working interface A 1Be connected the 4th working interface B with control chamber 50 1Be connected and fuel tank interface T with back pressure chamber 58 1Be connected with fuel tank 39.On first control position of selector valve 53, the 3rd working interface A 1With pressure interface P 1Connect, and the 4th working interface B 1Then with fuel tank interface T 1Be communicated with.On second control position of selector valve 53, the 3rd working interface A 1With fuel tank interface T 1Connect, and pressure interface P 1Then with the 4th working interface B 1Be communicated with.
Pilot line feeds in the control chamber 50 by second interface 56 in the back of selector valve 53.In addition, be provided with the connection set 55 that pilot line 52 is connected with deposit pipeline 51.Connection set 55 feeds between first interface 56 of safety check 42c and reserve chamber 49 in the deposit pipeline 51 and on the other hand between second interface 56 at selector valve 53 and control chamber 50 in the feeding pilot line 52 on the one hand.Another safety check 42d is set in connecting pipeline 55, and safety check 42d allows to flow to the pressure medium flow of deposit pipeline 51 and stop opposite pressure medium flow from pilot line 52.
If at internal-combustion engine 1 run duration, engine controlling unit does not send the adjustment requirement to device 10, and control valve 40 is in second (centre) position and selector valve 53 is in primary importance so.Therefore pressure medium does not flow to regulating device 10a or flows out from regulating device 10a.Pressure medium obtains stoping by the flow through safety check 42d of deposit pipeline 51 to reserve chamber 49 from pressure medium supply unit 37.By pilot line 52 and selector valve 53 to control chamber 50 medium of exerting pressure.Pressure medium enters reserve chamber 49 by pilot line 52, connecting pipeline 55 and deposit pipeline 51 simultaneously.Back pressure chamber 58 is connected with fuel tank 39 by selector valve 53 simultaneously.The pressure medium that enters in reserve chamber 49 or the control chamber 50 acts on first pressure side 47 or second pressure side 48, thus, pressure piston 45 moves against trying hard to recommend of spring part 46 towards the direction of backstop 54, thereby the volume of the volume of control chamber 50 and reserve chamber 49 all increases to some extent.Back pressure chamber 58 exhaust in fuel tank 39 simultaneously.If engine controlling unit requires the phase angular adjustment, control valve 40 is transformed into its primary importance or the 3rd position so.Therefore, pressure medium flows to first pressure chamber 35 or second pressure chamber 36 from pressure medium pump 38, thus, adjusts the generation by regulating device 10a, b mutually.If too small by the volume flow that pressure medium pump 38 is carried, for guaranteeing to adjust or should reach higher regulating the speed, first selector valve 53 is transformed in its second control position so.On this second control position, control chamber 50 is connected with fuel tank 39.Therefore the pressure medium that is in the control chamber 50 under the pressure is connected control chamber 50 emptying rapidly thus with barometric pressure.Reserve chamber 49 emptying in pressure medium supply unit 37 simultaneously.If the pressure medium emptying of control chamber 50 is rapid like this, pressure piston 45 is only supported with respect to reserve chamber 49 by first pressure side 47, whole power of spring part 46 only act on reserve chamber 49 so.Pressure p when therefore evacuation procedure being begun in the reserve chamber 49 is suitable for:
p = p sys ( A 1 + A 2 ) A 1
Add the pressure that produces by 58 filling of back pressure chamber.This point is suitable for during deflection fully as yet at pressure piston 45, is suitable in the time of just on not abutting in backstop 54.At this, p SysThe system pressure of the pressure medium supply unit 37 when being equivalent to be in accumulator 43 emptyings and beginning.Because the safety check 42a in the pressure medium pipeline 41 is arranged on the upstream of deposit pipeline 51, can and not flow out the oil circuit that enters internal-combustion engine 1 for regulating device 10a use so guarantee the total pressure p of reserve chamber 49 and total volume.Therefore, as in the application of traditional accumulator, not only provide current system pressure, but also provide with coefficient 1+A 2/ A 1The pressure that improves.
Additionally, pressure medium is imported back pressure chamber 58 from pilot line 52.This pressure medium applies power on the power equidirectional with spring part 46 to the back pressure face 59 of pressure piston 45.The additional thus pressure that improves in the reserve chamber 49.
Therefore pressure medium supply unit 37 can obtain the pressure support by second control position of adjusting on first selector valve 53, and this pressure support is higher than traditional accumulator.Therefore regulating the speed of regulating device 10a constitutes under obvious raising or regulating device 10a under the identical situation of physical dimension are regulating the speed identical situation lessly, and needn't adopt excessive setting size or adjusted pressure medium pump 38.
Be contemplated that following mode of execution equally, wherein, cancellation connecting pipeline 55 and the safety check 42c layout in deposit pipeline 53.In the invariable operation phase of the operation phase place maintenance of internal-combustion engine 1, accumulator 43 is by reserve chamber 51 and pilot line 52 filling.If system pressure descends, there is not pressure medium to flow out so from control chamber 50.Although cause control chamber 50 and reserve chamber 49 volumes under the situation that pressure medium supply unit 37 internal pressures descend, still to remain unchanged like this.At this, the stroke x from its initial position deflection is suitable for for pressure piston 45:
x = P max ( A 1 + A 2 ) D
Wherein, A 1The area that is equivalent to first pressure side 47, A 2The area that is equivalent to second pressure side 48, p MaxBe equivalent to the spring constant that maximum system pressure that is occurred during the filling stage and D are equivalent to spring part 46.At this, the maximum stroke of passing defines by backstop 54.If selector valve 53 is transformed into the second switch position, so the pressure p that is provided by accumulator 43 during deflection fully as yet at pressure piston 45 is suitable for:
p = p max ( A 1 + A 2 ) A 1
Add the pressure that produces by 58 filling of back pressure chamber.
Improve for realizing pressure, must be to from the pressure medium flow of control chamber 50 and ratio Q from the pressure medium flow of reserve chamber 49 D/ Q VMust be suitable for:
Q D Q V > A 2 A 1 .
Be set to for reaching this point, to the minimum passage section A between control chamber 50 and the fuel tank 39 DBe suitable for:
A D > A 2 A 1 A V ,
Wherein, A VBe equivalent between reserve chamber 49 and the regulating device 10a or the minimum passage section between regulating device 10a and the fuel tank 39.
Be contemplated that equally except the first regulating device 10a, one or more other regulating device 10b, 10c also can control via other pressure medium pipeline 41 and other control valve 40 by pressure medium supply unit 37.At this, other control systems 10b can have benefited from accumulator 43 equally.For this purpose, the branch road that leads to this regulating device 10b is in safety check 42a back on flow direction.If accumulator 43 is only supported the first regulating device 10a, the branch road that leads to other regulating devices 10c so is arranged on safety check 42a front on flow direction.
Be contemplated that equally safety check 42a is arranged on the downstream of leading to the branch road of laying in pipeline 51.In this case, control gear 10a, b and the pressure peak of leading between the branch road of laying in pipeline 51 are supported.Therefore pressure peak can not reach accumulator 43, realizes the transmission of torque of rigidity more by regulating device 10a, b thus.Be contemplated that equally, in pressure medium pipeline 41, use safety check 42a separately at the upstream and downstream that leads to the branch road of laying in pipeline 51.In this case, both reached rigidity transmission of torque, prevented also that the pressure of reserve chamber 49 or pressure medium volume from flowing out the oil circuit that enters internal-combustion engine 1 by control gear 10a, b.
In the change scheme slightly of this mode of execution, safety check 42b and/or safety check 42a are arranged at total pressure medium pipeline 41 wherein, also can cancel between the feeding point of accumulator 43.
Fig. 4 illustrates the another kind of device 10 according to embodiments of the present invention.The pressure piston 45 of accumulator 43 is divided into pressurized container 44 reserve chamber 49 and back pressure chamber 58 in this embodiment, wherein, control chamber 50 is not set.On the movement direction of pressure piston 45, reserve chamber 49 is defined by first pressure side 47 and back pressure chamber 58 is defined by back pressure face 59.Reserve chamber 49 can impose pressure medium from pressure medium supply unit 37 by deposit pipeline 51.Back pressure chamber 58 can be connected with pressure source by pilot line 52.In the embodiment shown, pilot line feeds in the pressure medium supply unit 37.Therefore pilot line 52 is connected with the pressure medium pump 38 of internal-combustion engine 1.Alternatively, also can use other pressure sources, as the pressure medium pump of servo customer.In pilot line 51, be provided with the selector valve 53 that is configured to two-position three-way distribution valve.Selector valve 53 has pressure interface P 1, working interface A 1, working interface B 1With fuel tank interface T 1Pressure interface P 1Be connected with pressure medium pump 38, working interface B 1Be connected and fuel tank interface T with back pressure chamber 58 1Be connected with fuel tank 39.On first control position of selector valve 53, working interface B 1With fuel tank interface T 1Connect, and pressure interface P 1Then not with other interfaces B 1, T 1Be communicated with.If selector valve 53 is on this control position, back pressure chamber 58 is connected with fuel tank 39 so.On second control position of selector valve 53, working interface B 1With pressure interface P 1Connect, and fuel tank interface T 1Then not with other interfaces B 1, P 1Be communicated with.If selector valve 53 is on this control position, back pressure chamber 58 is by pressure medium pump 38 medium of exerting pressure so.
During the 43 filling stages of accumulator, selector valve 53 is on first control position.Pressure medium flows to reserve chamber 49.The result is that pressure piston 45 moves against trying hard to recommend of spring part 46.The volume of reserve chamber 49 enlarges according to the consumption in back pressure chamber 58.In the pressure support stage, selector valve is in second control position.On this position, carry the pressure medium that acts on back pressure face 59 to back pressure chamber 58.Consequent pressure has improved by spring part 46 and has been applied to power on the pressure piston 45.Therefore, be improved from the support pressure that reserve chamber 49 provides by accumulator 43.Also can consider following mode of execution, wherein, the area of back pressure face 59 surpasses first pressure side, 47 areas.Reach thus the force value that can provide is produced the pressure conversion of positive impact than (Druck ü bersetzung).
Fig. 5 illustrates according to the another kind of mode of execution of device of the present invention.This mode of execution is equivalent to mode of execution shown in Figure 4 basically.Be with the difference of Fig. 4 mode of execution, in deposit pipeline 51 and pilot line 52, be provided with each safety check 42b, a c.In addition, selector valve constitutes two position and four-way reversing valves, wherein, and additional working interface A 1Be connected with reserve chamber 49.On first control position of selector valve 53, additional working interface A 1With pressure interface P 1Connect.On second control position of selector valve 53, working interface A 1Not with other interface B 1, P 1, T 1Be communicated with.In this embodiment, as long as selector valve 53 is on first control position, pressure medium just can enter in the reserve chamber 49 by pilot line 52 and selector valve 53 from pressure medium pump 38.Back pressure chamber 58 is to fuel tank 39 exhausts simultaneously.If selector valve 53 is on second control position, working interface A 1Passing and back pressure chamber 58 are by the medium that pressed by pressure medium pump 38.Reserve chamber 49 emptying in pressure medium supply unit 37 simultaneously.Safety check 42c shielding accumulator 43 avoids resulting from the influence of the pressure peak in regulating device 10a, the b.
Shown in whole mode of executions in, accumulator 43 feeds in pressure medium pump 38 and the pressure medium pipeline 41 that one or more control valves 40 are connected.Same admissible mode of execution is, one or more accumulators 43 feed in one or more control valves 40 and the pressure medium pipeline 41 that regulating device 10a, b are connected.
Be used for internal-combustion engine 1 port timing carried out the application of variable adjustment except accumulator 43 is used, accumulator 43 also can be used in during other automobiles use, and for example is used in the switchable cam auxiliary equipment or is used in the application of automatic transmission.
Reference numerals list
1 internal combustion engine
2 bent axles
3 pistons
4 cylinders
5 traction mechanism drives
6 inlet cam axles
7 outlet camshafts
8 cams
9a import scavenging air valve
9b exports scavenging air valve
10 devices
10a first regulating device
Other regulating devices of 10b
21 sprocket wheels
22 external rotors
The 22a housing
23 internal rotors
24 side covers
25 side covers
26 hub spares
27 blades
The 27a leaf spring
28 blade grooves
29 periphery walls
30 lug bosses
32 fixed blocks
33 cavitys
34 define wall
34a is backstop early
The slow backstop of 34b
35 first pressure chambers
36 second pressure chambers
37 pressure medium supply units
38 pressure medium pump
39 fuel tanks
40 control valves
41 pressure medium pipelines
The 42a safety check
The 42b safety check
The 42c safety check
The 42d safety check
43 accumulators
44 pressurized containers
45 pressure pistons
46 spring parts
47 first pressure sides
48 second pressure sides
49 reserve chamber
50 control chambers
51 deposit pipelines
52 pilot line
53 selector valves
54 backstops
55 connecting pipelines
56 interfaces
58 back pressure chambeies
59 back pressure faces
60 control mechanisms
A first working interface
B second working interface
The P input interface
The T output interface
A 1The 3rd working interface
B 1The 4th working interface
P 1Pressure interface
T 1The fuel tank interface

Claims (10)

1. be used for the device (10) that the port timing of the scavenging air valve (9a, b) to internal-combustion engine (1) is carried out variable adjustment, described device (10) has
Driving component (22), driven member (23), at least one pressure chamber (35,36), pressure medium supply unit (37) and at least one accumulator (43),
Wherein, by described pressure medium supply unit (37) can to described at least one pressure chamber (35,36) discharge pressure medium or from described at least one pressure chamber (35,36) the head pressure medium,
Wherein, by to described pressure chamber (35,36) discharge pressure medium or from described pressure chamber (35,36) the head pressure medium, can change the phase place of described driven member (23) with respect to described driving component (22),
Wherein, described accumulator (43) has displaceable element (45), and described displaceable element (45) is provided with first pressure side (47), and described first pressure side (47) partly defines reserve chamber (49),
Wherein, described reserve chamber (49) is connected with described pressure medium supply unit (37) or can be connected with described pressure medium supply unit (37),
Wherein, accumulator applies power to the direction of initial position to described displaceable element (45), and
Wherein, by pressurization described displaceable element (45) is moved against trying hard to recommend of described accumulator (46) to described reserve chamber (49), it is characterized in that, described displaceable element (45) has back pressure face (59), described back pressure face (59) defines back pressure chamber (58) at least in part, wherein, by the medium of being exerted pressure in described back pressure chamber (58), described displaceable element (45) can be passed to the direction of initial position.
2. by the described device of claim 1 (10), it is characterized in that, described displaceable element (45) has at least one second pressure side (48), described second pressure side (48) partly defines control chamber (50), wherein, by the pressurization to described control chamber (50) described displaceable element (45) is moved against trying hard to recommend of described accumulator (46), and wherein, the authorized pressure medium does not flow into described control chamber (50) from described reserve chamber (49) in the inside of described accumulator (43).
3. by the described device of claim 2 (10), it is characterized in that, the same to described reserve chamber (49) medium of exerting pressure with medium that described control chamber (50) is exerted pressure, make described displaceable element (45) mobile on identical direction.
4. by the described device of claim 1 (10), it is characterized in that described back pressure chamber (58) can be connected with pressure source (38) or be connected with fuel tank (39) selectively.
5. by claim 1 or 2 described devices (10), it is characterized in that be provided with control mechanism (60), wherein, described back pressure chamber (58) can be connected with fuel tank (39) or pressure source (38) selectively by described control mechanism (60).
6. by the described device of claim 1 (10), it is characterized in that described back pressure chamber can be connected with the described pressure medium pump (38) of described internal-combustion engine (1).
7. by the described device of claim 1 (10), it is characterized in that described back pressure chamber can be connected with the described fuel tank (39) of described internal-combustion engine (1).
8. by the described device of claim 5 (10), it is characterized in that, selector valve (56) is set to control mechanism (60), and described selector valve (56) has each interface (G, B, T) that is connected with described pressure source (38), described fuel tank (39) and described back pressure chamber (58).
9. by the described device of claim 8 (10), it is characterized in that described selector valve (56) has the other interface (A) that is connected with described reserve chamber (49) or described control chamber (50).
10. by the described device of claim 2 (10), it is characterized in that described reserve chamber (49) and described control chamber (50) are not interconnected in the inside of described accumulator (43).
CN2008801175326A 2007-11-24 2008-11-04 Apparatus for variably adjusting the control times of gas exchange valves in an internal combustion engine Pending CN101918680A (en)

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DE102007056685.0 2007-11-24
DE102007056685A DE102007056685A1 (en) 2007-11-24 2007-11-24 Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
PCT/EP2008/064942 WO2009065730A1 (en) 2007-11-24 2008-11-04 Apparatus for variably adjusting the control times of gas exchange valves in an internal combustion engine

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EP (1) EP2215332B1 (en)
KR (1) KR101468261B1 (en)
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105189977A (en) * 2013-03-29 2015-12-23 马自达汽车株式会社 Control device for multi-cylinder engine
CN107407167A (en) * 2015-03-06 2017-11-28 舍弗勒技术股份两合公司 Camshaft adjuster

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008036876A1 (en) * 2008-08-07 2010-04-15 Schaeffler Kg Camshaft adjusting device for an internal combustion engine
DE102010012482B4 (en) 2010-03-24 2018-07-12 Schaeffler Technologies AG & Co. KG Device for changing the relative angular position of a camshaft relative to a crankshaft of an internal combustion engine
DE102010053685B4 (en) * 2010-12-08 2014-10-30 Schwäbische Hüttenwerke Automotive GmbH Device for adjusting the rotational angular position of a camshaft
DE102013220322B4 (en) * 2013-10-09 2020-11-26 Schaeffler Technologies AG & Co. KG Camshaft adjustment device
DE102013221268A1 (en) * 2013-10-14 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Check valve unit in active accumulator
SE540733C2 (en) * 2016-06-15 2018-10-23 Scania Cv Ab Internal combustion engine and vehicle comprising a hydraulic phase displacement device
DE102017109139B3 (en) 2017-04-28 2018-06-07 Schaeffler Technologies AG & Co. KG Hydraulic camshaft adjuster and a method for controlling a hydraulic camshaft adjuster
DE102018105852B4 (en) * 2018-03-14 2022-04-21 Denso Corporation Camshaft actuator with a fluid accumulator and a pressure boosting structure
US11242870B2 (en) * 2020-05-27 2022-02-08 NORWOOD SALES, Inc. Cylinder bypass

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3907001A (en) * 1973-02-12 1975-09-23 Pneumo Dynamics Corp Combination accumulator reservoir
US4187682A (en) * 1979-01-02 1980-02-12 The Boeing Company Constant pressure hydraulic accumulator
DE3929621A1 (en) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag DEVICE FOR RELATIVELY ADJUSTING A SHAFT TO A DRIVE WHEEL, IN PARTICULAR CAMSHAFT OF AN INTERNAL COMBUSTION ENGINE
DE19529277A1 (en) * 1995-08-09 1997-02-13 Bayerische Motoren Werke Ag Method for operating a hydraulically controlled / regulated camshaft adjusting device for internal combustion engines
EP2320037B8 (en) 1996-03-28 2013-11-13 Aisin Seiki Kabushiki Kaisha Camshaft phasing device
US5971027A (en) * 1996-07-01 1999-10-26 Wisconsin Alumni Research Foundation Accumulator for energy storage and delivery at multiple pressures
JPH1054215A (en) * 1996-08-14 1998-02-24 Nippon Soken Inc Hydraulic pressure controller in lubrication circuit of internal combustion engine
JP3786511B2 (en) * 1997-11-20 2006-06-14 株式会社日本自動車部品総合研究所 Oil quantity control device in lubricating oil circuit of internal combustion engine
US6234125B1 (en) * 1998-03-30 2001-05-22 Aft Atlas Fahrzeugtechnik Gmbh Apparatus for angular adjustment of camshafts relative to crankshafts in combustion engines
DE19823619A1 (en) 1998-05-27 1999-12-02 Porsche Ag Device for changing the relative rotational position of a shaft to the drive wheel
US6871620B2 (en) * 2002-04-09 2005-03-29 Ford Global Technologies, Llc Variable cam timing unit oil supply arrangement
US6941909B2 (en) * 2003-06-10 2005-09-13 Caterpillar Inc System and method for actuating an engine valve
US7665431B2 (en) * 2006-10-11 2010-02-23 Gm Global Technology Operations, Inc. Drive piston assembly for a valve actuator assembly
US20090126360A1 (en) * 2007-11-20 2009-05-21 Bordwell Mark A Hydraulic system with accumulator assist
US20100307156A1 (en) * 2009-06-04 2010-12-09 Bollinger Benjamin R Systems and Methods for Improving Drivetrain Efficiency for Compressed Gas Energy Storage and Recovery Systems
DE102009030201A1 (en) * 2009-06-24 2010-12-30 Schaeffler Technologies Gmbh & Co. Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
US8171728B2 (en) * 2010-04-08 2012-05-08 Sustainx, Inc. High-efficiency liquid heat exchange in compressed-gas energy storage systems

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105189977A (en) * 2013-03-29 2015-12-23 马自达汽车株式会社 Control device for multi-cylinder engine
CN107407167A (en) * 2015-03-06 2017-11-28 舍弗勒技术股份两合公司 Camshaft adjuster
US10352206B2 (en) 2015-03-06 2019-07-16 Schaeffler Technologies AG & Co. KG Camshaft adjuster
CN107407167B (en) * 2015-03-06 2020-12-22 舍弗勒技术股份两合公司 Camshaft adjuster

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KR101468261B1 (en) 2014-12-02
EP2215332A1 (en) 2010-08-11
ATE513981T1 (en) 2011-07-15
KR20100093528A (en) 2010-08-25

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Application publication date: 20101215