EP2504534A1 - Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkaftmaschine - Google Patents
Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkaftmaschineInfo
- Publication number
- EP2504534A1 EP2504534A1 EP10781511A EP10781511A EP2504534A1 EP 2504534 A1 EP2504534 A1 EP 2504534A1 EP 10781511 A EP10781511 A EP 10781511A EP 10781511 A EP10781511 A EP 10781511A EP 2504534 A1 EP2504534 A1 EP 2504534A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- camshaft
- chamber
- sub
- pressure
- openings
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
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
- 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
- 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
- F01L1/34409—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 by torque-responsive means
-
- 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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0476—Camshaft bearings
-
- 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
-
- 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
- F01L2001/34433—Location oil control valves
Definitions
- the invention relates to a device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine with a hydraulic phase adjusting device, wherein the phase adjusting device can be brought into driving connection with a crankshaft and a camshaft and at least one Aktverstellhunt and at least one phoneverstellhunt which supplied via pressure medium lines pressure medium or from this can be dissipated, with a phasing of the camshaft relative to the crankshaft can be adjusted by pressure medium supply to the adjustment.
- a hydraulic phase adjusting device of the device is integrated into a drive train, via which torque is transmitted from the crankshaft to the camshaft.
- This drive train can be realized for example as a belt, chain or gear drive.
- Essential characteristics of such devices are the phase displacement speed and the demand for pressure medium.
- Phase adjustment speeds desirable.
- an ever lower pressure medium requirement is required in order to be able to design the pressure medium pump of the internal combustion engine smaller or to be able to reduce the delivery rate when using regulated pressure medium pumps.
- Such a device is known, for example, from EP 0 806 550 A1.
- the device comprises a vane-type phase-adjusting device with a drive element, which is in drive connection with the crankshaft, and an output element, which is non-rotatably connected to the camshaft.
- a plurality of pressure chambers are formed, wherein each of the pressure chambers is divided by means of a wing into two counteracting pressure chambers.
- the pressure medium required for the phase adjustment is provided by a pressure medium pump of the internal combustion engine and directed by means of a control valve selectively to the early or late adjustment.
- the pressure medium flowing out of the phase adjusting device is conducted into a pressure medium reservoir, the oil sump of the internal combustion engine.
- the phase adjustment thus takes place by means of the system pressure provided by the pressure medium pump of the internal combustion engine.
- Another device is known for example from US 5,107,804 A.
- the phase adjusting device is also formed in copezellenbauart and several early or late adjustment provided.
- EP 0 806 550 A1 the phase adjustment does not take place by pressure medium loading of the pressure chambers by a pressure medium pump, but alternating moments are used which act on the camshaft.
- the alternating moments are caused by the rolling of the cams on each biased with a valve spring gas exchange valves.
- These alternating moments are transmitted to the phase adjusting device, so that the wings are periodically applied in the direction of the late and early attack with a force.
- pressure peaks are generated alternately in the advance chambers and the retard chambers. If the phase position is to be kept constant, then a flow of pressure medium from the pressure chambers is prevented. In the case of a phase adjustment in the direction of earlier control times, a drainage of pressure medium from the advance chambers is prevented, even at the times in which pressure peaks are generated in the advance chambers.
- the pressure medium ejected from the pressure chambers is returned to a control valve which controls the pressure medium supply to or the pressure medium discharge from the pressure chambers.
- This pressure medium passes via check valves within the control valve to the inlet connection, which is connected to the pressure medium pump, wherein a part of the pressure medium is ejected into the pressure medium reservoir of the internal combustion engine.
- EP 2 075 421 A1 discloses a valve for a phaser.
- the valve comprises a valve piston which is rotatably arranged in a valve housing. Inlets and outlets for pressure oil, are arranged so that by adjusting the valve piston pressure oil chambers to the adjustment and can be passed to a locking mechanism.
- the locking mechanism can be activated not only in an end position of the camshaft adjuster, ie in a stop in the late or early position, but also in an intermediate position.
- a Mittenlagenverriegelung is possible, which may be useful depending on the engine application.
- DE 198 50 947 shows a device for controlling the timing of an internal combustion engine with at least one drive means, at least one camshaft with cam, at least one hydraulically actuated adjusting device for adjusting the relative angle of rotation between the drive means and the camshaft, at least one hydraulic fluid supply means for acting the adjusting device and at least one positive control device by which the hydraulic actuation of the adjusting device in dependence on the absolute angle of rotation of the camshaft and / or the cam is at least partially and / or at least partially influenced.
- a flow connection to the adjustment chambers is selectively interrupted when torque fluctuations cause pressure fluctuations which would react back and forth on the adjustment chambers of the camshaft when the cam is running up or down.
- US Pat. No. 6,186,104 B1 discloses a vane-type valve timing control device for an internal combustion engine, in which a pressure distribution device is interposed between the pressure cells and the control valve driving the latter, by means of which disturbing camshaft torques are masked out.
- a pressure distribution device is interposed between the pressure cells and the control valve driving the latter, by means of which disturbing camshaft torques are masked out.
- the oil supply to the pressure cells is interrupted when an early torque occurs. vice at an early adjustment, the supply of oil to the pressure cells is interrupted when a late torque occurs.
- DE 198 50 947 so a back swing of the adjusting device is prevented due to the adjustment against set camshaft moments.
- the invention has for its object to provide a device for variable adjustment of the timing of gas exchange valves of an internal combustion engine with a high Phasenverstellieri.
- the object is achieved by specifying a camshaft adjuster for a camshaft, are actuated by the cylinder valves of an internal combustion engine, with the camshaft with incoming cams late torques towards later Zylinderventilö Stamms founded and expiring cam opposite early torques in the direction of early Zylinderventilö Stamms founded to act on the camshaft adjuster,
- the adjusting means divides the pressure chamber into a first sub-chamber and a second sub-chamber
- first and the second sub-chamber pressure medium can be supplied or from the first sub-chamber and second sub-chamber pressure medium is discharged, so that by a pressure difference between the first sub-chamber and second sub-chamber, the adjusting means is movable, resulting in a rotation of the camshaft,
- control device optionally a torque mode or a pump mode is adjustable
- the invention is not limited to a particular type of camshaft adjuster, so it can be used for example a diegelzellenversteller in which a plurality of pairs of sub-chambers are formed, wherein the adjusting means is a parting chambers separating wings, for example, in one piece from a rotor is formed or plugged into this.
- the control device comprises a control valve and a rotary transformer arranged on the camshaft, wherein pressure medium via the control valve and the rotary transformer through first openings in the camshaft to the first sub-chamber and second openings in the camshaft to the second sub-chamber can be conducted or discharged, wherein a Opening cover is arranged in the rotary transformer so that depending on the rotation angle of the camshaft, the first openings and second openings are enabled or blocked.
- the supply and discharge of pressure medium to and from the sub-chambers is accomplished by means of a control valve, a downstream rotary transformer and openings or oil passages in the camshaft.
- the supply and removal of pressure medium is dependent on a rotation angle of the camshaft. This in turn corresponds to the camshaft moments, so that an inflow and outflow of pressure fluid can be synchronized with the respective camshaft torques depending on the desired adjustment direction.
- the opening cover in the rotary transformer releases the first or second openings corresponding respectively to the partial chamber to be actuated.
- the first and second openings need not be in an integrally formed with the rest of the camshaft area, the camshaft is in this sense also an attached component, adapter or the like to be expected, which rotates with the camshaft.
- the opening cover may be an inside of a cylinder comprising the camshaft, the recesses being e.g. are formed by grooves.
- a groove corresponding to the first and second openings are provided and a further groove for the inlet of pressure medium.
- the grooves then extend in the circumferential direction along a pitch circle, preferably approximately along a quarter circle in a four-cylinder engine.
- the opening cover is formed by the inside of a bearing shell, in which the camshaft is mounted, wherein the opening cover is interrupted by recesses so that in the area the recesses, the first openings and second openings are released while they are locked in the region of the opening cover.
- the first openings and the second openings are each equally spaced circumferentially at an angular distance and with respect to the opening cover arranged in phase so that a relative rotation of the valve piston relative to the valve housing by the angular distance leads to a geometrically identical arrangement.
- the pump mode or the torque mode is adjustable by an axial displacement of a valve piston arranged in a valve housing of the control valve.
- the valve housing has a pump opening, through which the supply of pressure medium to either the first sub-chamber or the second sub-chamber is adjustable, so that either the first sub-chamber or the second sub-chamber is under pressure, the flow of pressure fluid from the the first sub-chamber or the second sub-chamber via partial chamber openings in the valve housing is adjustable.
- the concept is pursued to effect an adjustment by controlling the flow of pressure medium.
- Pressure medium is supplied to the sub-chambers via the pump opening in the valve housing, wherein, depending on the position of the first openings or the second openings, the pump opening corresponds to the first sub-chamber or second sub-chamber.
- five switch positions are adjustable for the relative axial position of the valve piston, wherein
- the pump mode in a first position the pump mode is set for an adjustment of the camshaft after late cylinder valve opening times, in the second, axially following switching position, the torque mode is set for an adjustment of the camshaft after late cylinder valve opening times,
- a locking mechanism is provided, by means of which the camshaft adjuster is mechanically locked in a locking position against displacement, wherein the locking mechanism is hydraulically unlockable by means of the pressure medium and wherein an inlet of pressure medium to the locking mechanism is switched so that only in an axial Switching position of the valve piston, which corresponds to an adjustment after early cylinder valve opening times, the locking device unlocked.
- a locking of a camshaft adjuster is required in particular when the engine is switched off, so that when the engine is restarted, if there is still insufficient oil pressure in the adjuster, there is no rattling impact on the engine freely movable adjuster element occurs.
- switching off the engine is thus generally carried out an adjustment to late and a locking by means of a locking pin.
- the locking pin corresponds to one of the sub-chambers, so that after a sufficient pressure build-up after an engine start pressure medium from the sub-chambers of the hydraulically unlockable locking pin is pushed back against a spring and the adjuster is thus unlocked.
- a separate inlet of pressure medium to the locking device is switched so that during a state of a position corresponding to a late position, no pressure medium passes through the control valve to the locking pin.
- a pressure pulse for example by air, which is inserted by the penetrating pressure medium. Since the basic position is set to late, the adjuster must be unlocked only when the rotational position of the camshaft is to be changed, ie in an adjustment to early. For this purpose, the valve piston is moved axially from the basic position.
- the inlet preferably corresponds with locking openings in the camshaft, which are arranged in the axial direction at the same height as the second openings but spaced apart in the circumferential direction to the second openings, can now be achieved that the inlet only in a switching position Released early and thus pressure medium reaches the locking pin.
- two locking openings are arranged in the circumferential direction between each two second openings.
- FIG. 2 shows a schematic representation of a control valve
- FIG. 3 shows a valve piston and a valve housing
- FIG. 4 shows a representation of the camshaft torques as a function of time
- Fig. 5-14 is a schematic representation of the various switching positions in OPA method
- FIG. 15 a representation of the change of the flow rates at different control edges as a function of the switching position in the OPA method
- FIG. 16 a representation of the opening of the control edges as a function of the switching position in the OPA method
- FIGS. 17-20 a schematic representation of the various switching positions in CTA methods.
- 21 shows a representation of the change in the flow rates at different control edges as a function of the switching position in the CTA method
- Figure 22 is an illustration of the opening of the control edges as a function of the switching position in the CTA method
- Figure 23 shows a first variant control device with rotary transformer, control valve and camshaft
- Figure 24-28 is a schematic representation of the control of pressure medium as a function of the camshaft torque by means of rotary transformer, camshaft and control valve in the first variant Figure 29-29c, a second variant control device with rotary transformer, control valve and camshaft with a locking mechanism
- Figure 30-35 is a schematic representation of the control of pressure medium in
- FIG. 36 A schematic hydraulic circuit diagram for the five switching positions Detailed description of the drawings
- an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
- the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, with a first and a second camshaft adjuster 1 1 for variable adjustment of the timing of gas exchange valves 9,10 an internal combustion engine 1 for a relative rotation between Crankshaft 2 and the camshafts 6, 7 can provide.
- Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more outlet gas exchange valves 10.
- the inlet gas exchange valves 9 and the outlet gas exchange valves 10 are referred to below as cylinder valves 12.
- FIG. 2 shows a schematic illustration of a control device 20.
- the control device 20 comprises a valve housing 29 and a valve piston 27 arranged therein.
- the control valve 20 is arranged with one end in a camshaft 35.
- a restoring spring 31 acts on the valve piston 27.
- the restoring spring 31 is mounted via an axial bearing 33, designed as a roller bearing.
- the valve piston 27 is connected on its end facing away from the camshaft 35 with a magnetic piston 23 which is axially movable by an electromagnet 21.
- An anti-rotation device 25 connects the magnetic piston 23 with the valve piston 27 so that it can not rotate.
- an axial movement takes place through the valve housing 29 and a rotational movement through the valve piston 27 with a correspondingly changed environmental configuration.
- FIG. 3 shows the valve piston 27 and the valve housing 29 in a perspective view.
- the valve housing 29 has distributed around its circumference first openings 41. Axially offset to the first openings 41 approximately in the middle of the valve housing 29 are distributed around the circumference third openings 45 are arranged. Again axially offset, second openings 43 follow, which are arranged in the circumferential direction at the same position as the first openings 41.
- the valve piston 27 is inserted in a rotationally appropriate manner.
- the valve piston 27 has on its surface 53 an opening cover 51 which is formed by a radially elevated part of the surface 53.
- the opening cover has a first partial cover 51A at one axial end of the valve piston 27 and a second partial cover 51B at the opposite end.
- Both partial covers 51 A, 51 B are crown-like, ie they form a ring around the surface 53 with a respective outer edge BT, AT.
- the outer edge BT of the first partial cover 51 A simultaneously forms the one axial end of the valve piston 27, while the outer edge AT of the second partial cover 51 B simultaneously forms the other axial end of the valve piston 27.
- the in each case axially directed to the center of the surface 53 inner edge PB, PA of the partial covers 51 A, 51 B is serrated jagged.
- a crown 52 of a partial cover 51 A, 51 B is oriented in the circumferential direction so that it is between two crowns 52 is the other part of the cover 51 B, 51 A, but with an axial distance between the inner edges PB, PA is.
- valve piston 27 is now rotationally arranged in the valve housing 29, so that the opening cover 51 for each correct phase position, the first openings 41 and second openings 43 releases or blocks.
- Figure 4 shows the course of the camshaft torques using the example of a four-cylinder engine, plotted in the y-direction against the rotational position of the camshaft, plotted in the x direction. A following from the friction of the camshaft, at the same speed constant torque is not considered here.
- Camshaft moments greater than zero correspond to a moment in the direction of an early adjustment, i. in a direction where there is an earlier opening of the cylinder valves 12.
- Camshaft moments less than zero correspond to a moment in the direction of a late adjustment, i. in a direction in which there is a later opening of the cylinder valves 12.
- the camshaft torques have an approximately sinusoidal course depending on the rotational position of the camshaft. At fixed angular positions, premature torques occur alternately with late torques. This is now utilized specifically in the adjustment of the camshaft.
- a switching position for adjusting the camshaft is schematically plotted so that the opening cover 51 of the valve piston 27 is shown unwound in a plane.
- the result for the first partial cover 51A is thus a rectangular profile with the inner edge PB and a straight extension edge BT.
- the second partial cover 51 B is then shown with the inner edge PA and the outer edge AT.
- At the outer edge AT of the valve piston 27 is connected to the return spring 31, which presses the valve piston 27 against a magnet 21, not shown here.
- Also shown schematically are the first openings 41 and the second openings 43, as they are arranged according to the axial position and rotational position of the valve housing 29 relative to the valve piston 27 to the opening cover 51.
- the first openings 41 correspond to a second sub-chamber B and the second openings 43 correspond to a first sub-chamber A.
- the sub-chambers A, B are separated by an adjusting means 67 forming wings 67, which divides a pressure chamber 69 in the sub-chambers A, B.
- the wing 67 is connected to a rotor 65 of a camshaft adjuster 1 1.
- the pressure chamber 69 is formed in a stator 63 of the camshaft adjuster 1 1.
- a first oil passage 71 leads to the first sub-chamber A, a second oil passage 73 leads to the second sub-chamber B. Shown here is only a section of the camshaft adjuster 1 1.
- the camshaft adjuster 1 1 is designed as diegelzellenversteller and has a plurality of pressure chambers, Detailkam- men, wings and supply channels, which are not shown here for clarity.
- the resulting pressure difference between the sub-chambers A, B leads to a force on the wing 67 and thus on the rotor 65 in a rotational direction to the left.
- the rotor 65 is connected to the camshaft 35. Thus, there is a rotation of the camshaft 35 in the direction of "late”.
- FIG. 5 shows on the right next to the schematic representation of the valve piston 27 and the first and second openings 41, 43 of the valve housing the known from Figure 4 course of the camshaft torques as a function of the rotational angle of the camshaft 35.
- the valve housing 29 and thus the first and second openings 41, 43 now rotate in a defined relative to this camshaft profile, as shown by the comparison.
- the first and second openings in FIG. 5 are just synchronous with a late-camshaft moment.
- the second openings 43 receive a pressure peak in the direction of retardation, as a result of which the oil in the first sub-chamber A can be rapidly ejected.
- FIG. 6 shows an image corresponding to FIG. 5, but now the first and second openings 41, 43 are rotated relative to the opening cover 51. In terms of time, this corresponds to the occurrence of an early camshaft torque.
- the first openings 41 are released by the first part of the cover 51 A little, while the second openings 43 are wide open to the pressure supply from the pump P.
- the pump P acts on both partial chambers A, B.
- sub-chamber B it now acts against an early torque, which essentially leads to a compensation and no adjustment takes place.
- the sub-chamber A is flowed through by pressure medium and emptied into the tank T.
- Figures 5 and 6 show a switching position for an adjustment to "late”, in which an adjustment to the "Oil Pressure Actuated” - principle, short OPA, is realized and in a direction of adjustment late.
- This switching position which thus predominantly utilizes the adjusting force of the pump and where camshaft lenmomente are only supportive, is realized by the axial position of the valve piston 27 shown.
- the axial switching position is adjusted by means of the magnet 21. In the example shown, this is the basic position, without energization of the electromagnet 21st
- different rotational positions of the valve piston 27 relative to the valve housing 29 are realized in the axial shift position and, in addition, the corresponding camshaft torques are utilized.
- 7 and 8 show the corresponding representation for an adjustment to "early.”
- the effects for the subchambers A, B are interchanged, but otherwise the explanations concerning FIGS. 5 and 6 apply mutatis mutandis.
- FIG. 9 shows a middle position in which, when a late torque occurs, the second openings 43 are completely blocked. This blocks an adjustment.
- FIG. 10 shows a complete blocking of the first openings 41 when an early torque occurs.
- Figures 9 and 10 thus provide an axial switching position of the valve piston 27 again, in which prevents an adjustment of the camshaft 35, so this is to be kept at a given relative angular position to the crankshaft.
- the switching positions shown so far can thus be summarized as follows: There are two OPA adjustment provided, one at low and one at high pump pressure.
- the axial shift positions can be abbreviated as follows:
- Switch position I high pump pressure, late adjustment, Fig. 5, 6
- Switch position II Low pump pressure, late adjustment, Fig. 1 1, 12 Shift position III: Locked adjustment Fig. 9, 10
- Switching position IV Low pump pressure, early adjustment
- FIGS. 13, 14 Switching position V: high pump pressure, early adjustment, FIGS. 7, 8
- the advantage of this adjustability lies, in particular, in the fact that the inlet orifices 41 and 43 to the respective subchambers A, B are not completely closed due to the torque counteracting high pump pressure and one of the desired setting direction, whereby the higher pumping power compared to the weaker camshaft torque despite opposing camshaft torque can still be used for adjustment.
- the times in which oppositely acting camshaft moments occur can also be exploited for the adjustment, resulting in a quick adjustment. But if the pump power is lower than the camshaft moments, the oppositely acting moments are hidden by means of the fully closed openings 41 and 43, so that no recalculation occurs.
- FIG. 15 shows how the flow of pressure medium at the respective inner and outer edges PA, PB, BT, AT changes as a function of the switching position. Shown here are gradients at times with a Camshaft torque to early and solid at camshaft speeds to late.
- the line for the inner edge of the first partial cover 51A, PB is explained:
- the flow at the inner edge PB is high to all axial positions, while at moments early on from the switching position I to the switching position II and following switching positions quickly drops to zero.
- FIG. 16 shows diagrammatically for the switching positions I-V the opening degree of the openings 41, 43 as viewed from the respective inner edges PB, PA and outer edges BT, AT as a function of the switching positions I-V and the direction of adjustment.
- Fully shaded boxes correspond to a fully closed aperture 41, 43
- wholly white panels correspond to a fully opened aperture 41, 43
- partially hatched panels correspond to a partially blocked aperture 41, 43.
- the opening cover 51 is here adjusted by means of the axial position of the valve piston 27 so that upon the occurrence of a late-torque connection of the two sub-chambers A and B on the first and second openings 41, 43 results, while the first openings 41 are far open, so that again results in a strong Entdrosselung and thus a low risk of air suction.
- the second openings 43 are opened slightly to a flow control from the first sub-chamber A adjust.
- the first partial cover 51A completely blocks the first openings 41. Oil can thus not escape from the second sub-chamber B and there is no adjustment. The complete shut-off prevents a return swing. About fully open second openings 43 and thus greatly de-throttled pump pumped P neutral neutral oil in the first sub-chamber A. This prevents air suction.
- FIGS. 19 and 20 show the settings corresponding to FIGS. 18 and 19, only for the reverse direction of adjustment in advance.
- Switch position I pump mode (OPA), adjustment to late
- FIGS. 5, 6 A particularly favorable sequence of switching positions can now be constructed by selecting axially successive switching positions as follows: Switch position I: pump mode (OPA), adjustment to late, FIGS. 5, 6
- Shift position II Moment mode (CTA), advance adjustment, Fig. 19, 20
- Shift position III Locked adjustment Fig. 9, 10
- Shift position IV torque mode (CTA), retardation, Fig. 17, 18
- Switch position V pump mode (OPA), advance adjustment, Fig. 7, 8
- FIG. 21 again shows switching positions for this sequence, such as the flow of pressure medium at the respective control edges, ie inner and outer edges PA, PB, AT, BT, as a function of the axial position of the valve piston 27 and the valve housing 29, ie the switching positions lV changes.
- FIG. 22 shows schematically for the switching positions IV the opening degree of the openings 41, 43 viewed from the respective inner edges PB, PA and outer edges BT, AT as a function of the switching positions IV and the actuating direction.
- Fully hatched fields correspond to a completely blocked opening 41, 43
- completely white fields correspond to a fully opened opening 41, 43
- partially hatched areas correspond to a partially blocked opening 41, 43.
- the previous illustrations and examples related to a variant, in particular as So-called central valve design is suitable, ie a control valve for controlling the supply and removal of pressure medium to the sub-chambers is arranged centrally in a camshaft.
- FIG. 23 shows, in a split state, a camshaft 35 and a rotary transformer designed as a bearing shell for the camshaft 35 in a perspective view.
- a control valve 101 is shown in a longitudinal section.
- the camshaft 35 has concentric inner channels which, as indicated, correspond once to the first sub-chamber A and once to the second sub-chamber B.
- To the inner channels lead through the camshaft wall from the outside first openings 41, which correspond to the first sub-chamber A and second openings 43, which correspond to the second sub-chamber B.
- the rotary transformer 103 encloses the camshaft 35 in the region of the dashed lines.
- an opening cover 51 is arranged, which forms an interrupted, radially inner bearing surface. It is interrupted by recesses 105.
- the opening cover 51 could for example be milled or be formed by an example soldered insert.
- the first openings 41 and second openings 43 are now covered or released by the opening cover 51. Since the rotational position of the camshaft 35 is synchronous with the camshaft moments, thereby an inflow or outflow of pressure medium through the first openings 41 and second openings 43 and thus the inflow and outflow of pressure medium in the sub-chambers A, B in response to the acting camshaft torque be set.
- control valve 101 in a longitudinal section clarifies the assignment to a pump opening 109P and partial chamber openings 109A, 109B in the valve housing 29. These openings are released or closed by the valve housing 29, axially displaceable valve piston 27 and that via the control edges KAT, KPA, KBT, KPB at the sub-chamber openings 109A, 109B and over the control edges P1, P2, P3, P4 at the pump opening 109P.
- These control edges are formed by projections or noses on a cylindrical surface of the valve piston 27, wherein each have a projection or nose a pair of control edges.
- FIGS. 24-28 show, for the variant of the rotary transformer 103 shown in FIG. 23, a schematic representation of the control of pressure medium as a function of the camshaft torque by means of a rotary transformer, camshaft and control valve.
- control valve 101 is again shown in a longitudinal section.
- the valve piston 27 of the control valve 101 is determined in its axial position by a magnet 21.
- a percentage here shows the degree of energization of the electromagnet 21 and thus the degree of axial displacement of the valve piston 27.
- Stator and rotor of a camshaft adjuster 1 1 with subchambers A, B are illustrated schematically on the left under the control valve 101, as shown in earlier figures.
- FIG. 24 now shows a first switching position at 100% energization of the electromagnet 21 and thus at a first axial position of the valve piston 27.
- This switching position corresponds to an adjustment in the direction of late, wherein is set according to the relative rotational position of the rotary transformer 103 and the camshaft 35, an angular position for a camshaft torque to late.
- the dashed and dotted lines schematically show the flow directions of the pressure medium.
- Pressure medium passes via the pump opening 109P in the valve housing 29 via the second openings 43 into the second sub-chamber B. At the same time, pressure medium is discharged from the first sub-chamber A via the first openings 41 and the sub-chamber opening 109A to the tank.
- FIGS. 26 and 27 show an image corresponding to FIGS. 24 and 25, wherein now the electromagnet is only 75% energized and the valve piston 27 thus assumes a new axial switching position in the direction of the magnet 21. This switching position also causes a retardation. But now arises when a late-torque a connection of the sub-chambers A, B, so that by the late-torque pressure in the first sub-can A is built, whereby pressure medium is pushed from the first sub-chamber A in the second sub-chamber B, this leads to the desired adjustment. When an early torque occurs, however, the sequence from the second sub-chamber B is again blocked so that no adjustment can take place.
- FIG. 28 shows a switching position with 50% current supply to the electromagnet 21.
- the angular position of the camshaft 35 is held, i. there is no adjustment. This is achieved in that, when a late-torque occurs, an outflow from the first sub-chamber A is blocked, as shown in FIG. If an early torque, not shown, the first and second openings 41, 43 would come to rest again so that a flow from the second sub-chamber B would be blocked, so that in this case no adjustment is possible.
- a torque mode for an early adjustment and a switching position of 0% can be set to a pump mode for an early adjustment, with correspondingly exchanged release or blocking of the openings .
- a pump mode or a torque mode that is to say an OPA method or a CTA method for the adjustment, depending on the operating state of the internal combustion engine.
- a particularly rapid adjustment is achieved overall.
- FIG. 29 shows a second variant, which corresponds to the representation of FIG. 23, but the opening cover 51 is now delimited by three groove-like recesses 105.
- a locking mechanism 121 is provided in the rotor 65 of the camshaft adjuster 1 1, which can be configured as a locking pin in a manner not shown in a locking link of the stator 63 by pressure of a spring can lock. This will an adjustment locked.
- An unlocking is effected by a hydraulic pressure against the spring, wherein the locking mechanism 121 pressure medium is supplied.
- This pressure medium is now supplied via a separate locking feed line 125, which corresponds to locking openings 123 in the camshaft 35.
- the locking openings 123 are arranged in the axial direction at the same height as the second openings 43 but circumferentially spaced from the second openings 43. Furthermore, two locking openings 123 are arranged in the circumferential direction between each two second openings 43.
- the first openings 41 and the second openings 43 are formed in this variant as axially extending slots.
- FIGS. 30-35 show the various switching positions of the valve piston 27 and the relative orientation of the first and second openings 41, 43 and the locking openings 123 to the opening cover 51.
- the illustration corresponds to the illustration of FIGS. 24-28, but with the described second variant of the first and second openings 41, 43 and the opening cover 51 and the additional locking mechanism 121 being depicted.
- the second openings 43 are in this embodiment now left and the first openings 41 right.
- Figure 30 shows a switching state with 0% current to the magnet 21, so that the valve piston 27 is set in its axial normal position. This is the case, for example, when the internal combustion engine is switched off and the subchambers A, B are not under pressure.
- the wing 67 of the rotor 65 would have to strike in the figure on the left of the stator, ie in an adjustment maximum late.
- the switching position corresponds to a late adjustment, wherein in Figure 30, the case of the occurrence of a late torque is shown.
- one of the second openings 43 corresponds to one of the recesses 105, which is supplied with pressure medium from the pump P via the pump opening 109P of the valve housing 29.
- a discharge of pressure medium from the first sub-chamber A is possible via one of the first openings 41, which corresponds to the recess 105, which is connected to the partial chamber opening A of the valve housing.
- the pressure medium is then led to the tank via the partial chamber opening A released by the valve piston 27 in this axial position. An adjustment does not take place in spite of these settings in this case, because yes, the wing 67 is already on the late stop.
- the locking mechanism 121 In this basic position, the locking mechanism 121 is locked, so that it does not cause a disturbing rattle at an engine start because of the then occurring camshaft moments and the lack of pressure in the sub-chambers A, B, because the wing 67 alternately strikes the stator 63 alternately left and right.
- One of the locking openings 123 corresponds to one of the recesses 105, which corresponds to the partial chamber opening 109B of the valve housing 29. Due to the position of the valve piston 27, however, this partial chamber opening 109B is not supplied with pressure or is shut off. Thus, also a pressure increase, which after engine start e.g. occurs through an air column pushed by the oil, do not reach the locking mechanism 121. Unintentional unlocking is not possible.
- FIG. 31 shows an image corresponding to FIG. 30, except that the rotational position of the camshaft 35 has changed and now an early torque occurs.
- this early torque would not be able to effect an adjustment in the direction of early, since the flow from the sub-chamber B is locked. Thus, there is no return oscillation.
- the adjustment position also remains due to the locking mechanism. The lock does not solve either, since the locking mechanism 121 remains unpressurized.
- FIG. 32 now shows a switching position in which the valve piston 27 has moved axially in accordance with a current supply of the magnet 21 with 25% of the maximum current supplied. It is shown the case of the occurrence of a late torque.
- This switching position corresponds to the torque mode, while the switching position discussed with reference to FIGS. 30 and 31 corresponds to the pump mode.
- the valve piston 27 now releases a connection of the partial chamber opening 109A with the pump opening 109P.
- the pump port 109P corresponds to the second sub-chamber B, while the sub-chamber port 109A corresponds to the first sub-chamber A.
- FIG. 33 shows the rotational position when an early torque occurs.
- the second sub-chamber B is blocked by the position of the valve piston 27, so that no pressure medium can be ejected. The acting on the second sub-chamber B pressure of the early torque thus does not lead to an adjustment.
- the locking mechanism 12 Shortly after the engine start, with still unfilled sub-chamber A, B, the locking mechanism 12 is still locked and is also kept depressurized by a lock as in the 0% shift position, i. It remains locked and an adjustment remains locked.
- FIG. 34 now shows an image corresponding to FIGS. 30-33, wherein now an axial switching position of the valve piston 27 is set at 75%. This is again an adjustment of the moment mode, but now for an adjustment towards early. It applies, with appropriate permutation, the same mechanism for adjusting the camshaft torques as described for Figures 32 and 33, to the fact that now the locking mechanism 121 receives pressure because the Detailschff- tion 109B of the valve housing 29 is now released from the valve piston 27 and thus pressure medium to the locking mechanism 121 passes. As a result, he is pushed back against his pen and unlocked. An adjustment is now possible when an early torque occurs, which is shown in Figure 35. The release of the locking mechanism 121 happens after an engine start but only when sufficient pressure is present so that it does not come to an unwanted unlocking.
- the axial switching position at 100% current corresponds to the pump mode for an early adjustment and similar to the late-adjustment of the pump mode as described with the figures 30 and 31 functions.
- the five axial shift positions and the camshaft torque-dependent rotational position can be summarized in a hydraulic circuit diagram, which is shown in Figure 36. Schematically, the control valve 101 is shown, wherein in five juxtaposed squares, the five switching positions of the valve piston 27 are shown, the 0%, 25%, 50%, 75% and 100% energization of the magnet 21 correspond.
- the subchamber openings 109A, 109B, pump opening 109P, and outflow to the tank T of the valve housing 29 are fixed and can be occupied by the various connections, shown as an arrow, or closures, shown as "T", by the corresponding
- the relative rotational position of the camshaft 35 and the rotary transformer 103 are also schematically represented by an axial positional shift, wherein the coupling to the camshaft moments is imaged by guiding a guide pin 127 in a rectangular-waved guide groove 129 and the guide pin 127 activates the first or second rotational position D1, D2 depending on the occurrence of an early torque or late torque, so guide pin 127 and guide groove 129 are illustrative only and how gesa gt transformed into an axial displacement in order to better map the circuit logic.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009056021A DE102009056021A1 (de) | 2009-11-27 | 2009-11-27 | Vorrichtung zur varibalen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
PCT/EP2010/068079 WO2011064228A1 (de) | 2009-11-27 | 2010-11-24 | Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkaftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2504534A1 true EP2504534A1 (de) | 2012-10-03 |
EP2504534B1 EP2504534B1 (de) | 2013-11-06 |
Family
ID=43501103
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10781511.0A Not-in-force EP2504534B1 (de) | 2009-11-27 | 2010-11-24 | Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkaftmaschine |
Country Status (5)
Country | Link |
---|---|
US (1) | US8584637B2 (de) |
EP (1) | EP2504534B1 (de) |
CN (1) | CN102648339B (de) |
DE (1) | DE102009056021A1 (de) |
WO (1) | WO2011064228A1 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009056020A1 (de) * | 2009-11-27 | 2011-06-01 | Schaeffler Technologies Gmbh & Co. Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE102009056018A1 (de) * | 2009-11-27 | 2011-07-07 | Schaeffler Technologies GmbH & Co. KG, 91074 | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE102011077587A1 (de) * | 2011-06-16 | 2012-12-20 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
US9080470B2 (en) | 2011-10-14 | 2015-07-14 | Borgwarner, Inc. | Shared oil passages and/or control valve for one or more cam phasers |
US10612430B2 (en) * | 2017-06-20 | 2020-04-07 | ECO Holding 1 GmbH | Oil control valve to control a cam phaser with a spool positioned by external actuator |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5107804A (en) | 1989-10-16 | 1992-04-28 | Borg-Warner Automotive Transmission & Engine Components Corporation | Variable camshaft timing for internal combustion engine |
US5263443A (en) * | 1993-01-14 | 1993-11-23 | Ford Motor Company | Hydraulic phaseshifter |
EP2320037B8 (de) | 1996-03-28 | 2013-11-13 | Aisin Seiki Kabushiki Kaisha | Nockenwellen-Verstellvorrichtung |
JP2000179315A (ja) | 1998-10-08 | 2000-06-27 | Unisia Jecs Corp | 内燃機関のバルブタイミング制御装置 |
DE19850947A1 (de) | 1998-11-05 | 2000-05-11 | Schaeffler Waelzlager Ohg | Vorrichtung zur Steuerung der Öffnungs- und Schließzeiten von Gaswechselventilen einer Brennkraftmaschine |
ATE414215T1 (de) * | 2005-08-22 | 2008-11-15 | Delphi Tech Inc | Nockenwellenversteller zur einstellung der phase zwischen einer nockenwelle und einem antriebsrad |
JP4358180B2 (ja) * | 2005-11-04 | 2009-11-04 | 株式会社日立製作所 | 内燃機関のバルブタイミング制御装置 |
DE102006007584A1 (de) * | 2006-02-18 | 2007-08-30 | Schaeffler Kg | Nockenwellenversteller mit einem Überlagerungsgetriebe |
JP4484843B2 (ja) * | 2006-04-28 | 2010-06-16 | 日立オートモティブシステムズ株式会社 | 内燃機関のバルブタイミング制御装置 |
WO2008067935A2 (de) | 2006-12-04 | 2008-06-12 | Daimler Ag | Verstelleinrichtung |
DE102007035672B4 (de) * | 2007-07-27 | 2009-08-06 | Hydraulik-Ring Gmbh | Nockenwellenversteller |
JP4544294B2 (ja) | 2007-11-28 | 2010-09-15 | 株式会社デンソー | バルブタイミング調整装置 |
EP2075421A1 (de) | 2007-12-28 | 2009-07-01 | Delphi Technologies, Inc. | Flüssigkeitssteuerungsventil für einen Nockenwellenversteller |
CN201218116Y (zh) * | 2008-05-27 | 2009-04-08 | 芜湖杰锋汽车动力系统有限公司 | 一种可变气门正时的配气调节装置 |
-
2009
- 2009-11-27 DE DE102009056021A patent/DE102009056021A1/de not_active Withdrawn
-
2010
- 2010-11-24 EP EP10781511.0A patent/EP2504534B1/de not_active Not-in-force
- 2010-11-24 US US13/511,202 patent/US8584637B2/en not_active Expired - Fee Related
- 2010-11-24 WO PCT/EP2010/068079 patent/WO2011064228A1/de active Application Filing
- 2010-11-24 CN CN201080053426.3A patent/CN102648339B/zh not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2011064228A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN102648339A (zh) | 2012-08-22 |
WO2011064228A1 (de) | 2011-06-03 |
EP2504534B1 (de) | 2013-11-06 |
CN102648339B (zh) | 2014-08-20 |
US20120227693A1 (en) | 2012-09-13 |
DE102009056021A1 (de) | 2011-06-01 |
US8584637B2 (en) | 2013-11-19 |
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