EP1216345B1 - Brennkraftmaschine mit hydraulischem nockenwellenversteller zur nockenwellenverstellung - Google Patents
Brennkraftmaschine mit hydraulischem nockenwellenversteller zur nockenwellenverstellung Download PDFInfo
- Publication number
- EP1216345B1 EP1216345B1 EP00974375A EP00974375A EP1216345B1 EP 1216345 B1 EP1216345 B1 EP 1216345B1 EP 00974375 A EP00974375 A EP 00974375A EP 00974375 A EP00974375 A EP 00974375A EP 1216345 B1 EP1216345 B1 EP 1216345B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hydraulic pressure
- camshaft
- ring
- cylinder head
- internal combustion
- 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.)
- Revoked
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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
- 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
-
- 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
- F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft
- F01L1/34406—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
-
- 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
- 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
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
-
- 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
- F01L1/053—Camshafts overhead type
- F01L2001/0537—Double overhead camshafts [DOHC]
-
- 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
- F01L2001/3443—Solenoid driven 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
- F01L2001/34486—Location and number of the means for changing the angular relationship
- F01L2001/34496—Two phasers on different camshafts
-
- 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
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/04—Sensors
- F01L2820/041—Camshafts position or phase sensors
Definitions
- the invention relates to an internal combustion engine with a cylinder head and at least a mounted on this camshaft, which is driven by a Crankshaft corresponding gas exchange valves actuated on the cylinder head, where the camshaft, a camshaft adjuster is provided, which is for changing of control times of the gas exchange valves by means of hydraulic pressure, the camshaft rotated relative to the crankshaft, wherein a supply device for hydraulic pressure provided on the camshaft adjuster and as separate from the cylinder head Component is formed and has a ring for each camshaft, wherein each ring has two grooves, which via respective hydraulic pressure channels in the Supply device are connected to a hydraulic pressure valve, according to the preamble of claim 1.
- From DE 197 45 670 A1 is a device for changing the timing of gas exchange valves of an internal combustion engine, wherein at one front end of the gas exchange valves actuated camshaft Camshaft adjuster is arranged.
- Pressure medium channels is the camshaft adjuster with hydraulic pressure for pivoting the camshaft relative to a camshaft driving Supplied crankshaft. The manufacture and installation of the housing cover is but consuming and expensive.
- US 5 540 197 describes a camshaft adjuster with hydraulic pressure supply, which is designed as a separate component and wherein a ring of Hydraulic pressure supply engages around a sleeve attached to the camshaft. In Ring and sleeve are correspondingly communicating grooves for Hydraulic pressure provided. About Hydarulik horritze in the sleeve is a Hydraulic pressure supply of the camshaft adjuster. About appropriate Hydraulic pressure channels in the hydraulic pressure supply is connected to a hydraulic pressure valve.
- the present invention is based on the object, an internal combustion engine to improve the above-mentioned type such that a structurally simple and functionally reliable camshaft adjustment is available.
- each ring engages around a portion of the camshaft and each embraced Section of the camshaft has two annular grooves, which each with a groove of the corresponding ring are aligned, wherein each groove / Ringnutconcentr a Ringes via respective hydraulic pressure channels in the camshaft with a Hydraulic pressure chamber of the camshaft adjuster arranged on this camshaft connected is.
- the supply device for hydraulic pressure in the separate component in one piece following, at least one Hydraulic pressure connection, at least one hydraulic tank connection, at least a receptacle for a hydraulic pressure valve and corresponding hydraulic pressure channels, which are designed such that they each have a hydraulic pressure connection with the receptacle for a hydraulic pressure valve, each hydraulic pressure valve with a groove / Ringnutcru a ring and each receptacle for a Connect hydraulic pressure valve to a hydraulic tank connection.
- the Recording for a hydraulic pressure valve for example, axially parallel or perpendicular arranged to the ring.
- the feeding device is designed such that it Cylinder head is fastened.
- FIG. 1 to 13 For a better illustration of the relationship of the individual views according to FIG. 3 to 8 and 13 to each other in these figures is a "x" marked, dashed Line drawn as reference.
- the rings 12 engage around a respective, not shown, camshaft in one predetermined section and serve as a transition interface for hydraulic fluid in the Camshaft and the camshaft adjuster connected to the camshaft, what will be explained in more detail below.
- the separate component is by means of holes 16 through cross-bolts (not shown) attachable to a cylinder head, not shown.
- a cylinder head not shown.
- the form in Fig. 2 hatched or dashed areas shown corresponding contact surfaces on Cylinder head.
- a holder 18 for a slide not shown for one between a crankshaft (not shown) and that of the rings 12, 13 enclosed camshaft arranged chain or belt drive (not shown) attached.
- the component 10 has a system of hydraulic pressure channels, which will be explained in more detail below.
- This system of hydraulic pressure channels is after the production of the component 10, for example by means of casting introduce appropriate blind and through holes in the component 10th educated. This results for all blind or through holes Of necessity appropriate openings to the environment. Unless these openings for the Operation of the component 10 are not required, they are pressed with balls or bolt pressure-tight.
- balls 112 are indicated in FIG. 15.
- the component 10 is at the back or cylinder side two separate hydraulic pressure ports 20 and 22, which from hydraulic pressure is applied to the cylinder head.
- the first Hydraulic pressure port 20 is, as shown in particular in FIG. 10, over a first hydraulic pressure channel 24 connected to the first receptacle 14 and the second Hydraulic pressure port 22 is, as shown particularly in FIGS. 7 and 10, over a second hydraulic pressure channel 26 connected to the second receptacle 15.
- the first hydraulic pressure channel 24 is thereby starting from the holder 18 through the first Receiving 14 driven through to the first hydraulic pressure port 20 and sealed on the holder side pressure-tight.
- the second hydraulic pressure passage 26 is laterally (in Figs. 7 and 10 from the left) through the second hydraulic pressure port 22 through to second intake 15 propelled and also externally borehole pressure-tight locked.
- the first receptacle 14 is, as shown in particular in FIGS. 8, 9 and 12, over a third hydraulic pressure channel 28, a fourth hydraulic pressure channel 30, a fifth Hydraulic pressure channel 32, a sixth hydraulic pressure channel 34 and a seventh Hydraulic pressure channel 36 connected to a first groove 38 in the first ring 12.
- the first Recording is further, as can be seen in particular from FIGS. 11 and 12, via an eighth Hydraulic pressure channel 40 connected to a second groove 42 of the first ring 12.
- the second receptacle 15 is, as shown in particular in FIGS. 9, 11, 12 and 13, over a ninth hydraulic pressure passage 44, a tenth hydraulic pressure passage 46, a eleventh hydraulic pressure channel 48 and a twelfth hydraulic pressure channel 50 having a first groove 52 of the second ring 13 connected.
- the second receptacle 15 is further, like in particular from FIGS. 7, 11 and 12, over a thirteenth Hydraulic pressure channel 54, a fourteenth hydraulic pressure channel 56 and a fifteenth hydraulic pressure channel 58 with a second groove 60 of the second ring thirteenth connected.
- the camshaft not shown in FIGS. 1 to 13 points in the of the rings 12th and 13 encompassed portions corresponding annular grooves, which with the grooves 38 and 42 of the first ring 12 and with the grooves 52 and 60 of the second ring 13th aligned. These annular grooves are in turn with hydraulic pressure channels in the camshaft connected, which with appropriate Hydraulik horrkammem one at this Camshaft arranged camshaft adjuster are connected. This leads a Hydraulic pressurization via the respective first grooves 38, 52 of the rings 12, 13 above the respective o.g.
- Hydraulic pressure channels to pivot the corresponding Camshaft with respect to the crankshaft in one direction and a Hydraulic pressurization via the respective second grooves 42, 60 of the rings 12, 13 on the respective o.g. Hydraulic pressure channels to pivot the corresponding camshaft with respect to the crankshaft in a corresponding opposite direction.
- One direction leads to an "early position”, i. the Valve operation takes place earlier or the crankshaft movement leading, and the correspondingly different direction leads to a "late position", i. the valve actuation takes place later or the crankshaft movement below.
- proportional directional valves is also an intermediate position between the two extreme “early position” and “late position” stable adjustable. Conveniently, in the extreme "late position” of Camshaft adjuster locked, so this position even without pressurization Constantly maintained and not from on the camshaft through the Valve actuation acting forces is affected.
- FIG. 14 schematically illustrates one in the separate component 10
- the invention provided hydraulic pressure circuit with the hydraulic pressure connections 20, 22 of hydraulic pressure valves 62 and 64, wherein each hydraulic pressure port 20, 22 a check valve 66, 68 and is connected to a hydraulic pump 70.
- the Hydraulic pressure valves 62, 64 are either 4/2-way valves S / W or 4/2 proportional directional control valves educated.
- Each hydraulic pressure valve 62, 64 is also with a hydraulic tank connection 72 connected.
- Fig. 15 illustrates the function of the hydraulic pressure valves 62, 64 and the functional Cooperation of component 10, the camshaft 74 and the Camshaft adjuster 76.
- This illustration in Fig. 15 is merely schematic to do not understand and give the exact spatial arrangement of the hydraulic pressure valves 62, 64 again; as shown in Figs. 1 to 13 in the receptacles 14, 15 inserted Hydraulic pressure valves would be.
- the arrangement of the hydraulic pressure channels corresponds not completely that of FIG. 1 to 13.
- the hydraulic pressure valve 64 is arranged, which has a piston 78.
- This Piston 78 connects via the receptacle 15 depending on its position one Hydraulic pressure supply via the hydraulic pressure port 22 and the hydraulic pressure channel 26 optionally with the hydraulic pressure channels 44, 46 and 48 or with the Hydraulic pressure channel 56.
- the hydraulic pressure valve 64 has the Hydraulic tank connection 72 on.
- the means of a screw 80 with the component 10 and the camshaft adjuster 76 connected camshaft 74 has two annular grooves 82nd and 84, wherein within the ring 13, a portion of the cam shaft 74th engages around the circumference, the first annular groove 82 with the hydraulic pressure channel 48 and in the second annular groove 84 is in fluid communication with the hydraulic pressure passage 56.
- the Grooves 52 and 60 of the second ring 13 are not shown in Fig. 15.
- the first Ring groove 82 is connected via a hydraulic pressure channel 86 which in the camshaft 74 to the Screw 80 is formed around, with a first hydraulic pressure chamber 88 of the Camshaft adjuster 76 connected.
- the second annular groove 84 is over a Hydraulic pressure channel 90 connected to a second hydraulic pressure chamber 92.
- the camshaft adjuster 76 rotates the camshaft 74 with respect to a wheel 94, which via a drive, not shown (toothed or belt drive) with a not connected crankshaft is connected, in one or the other direction.
- the system is depressurized and the phaser 76 is locked by a bolt 96 in late position.
- the camshaft 74 is pivoted to an early position relative to the crankshaft when the second hydraulic pressure chamber 92 is pressurized via the hydraulic pressure passages 24, 56, 84, and 90.
- the pin 96 is hereby out of engagement with the wheel 94.
- the camshaft 74 is pivoted back into late position when the first hydraulic pressure chamber 88 is pressurized via the hydraulic pressure channels 24, 44, 46, 48, 82 and 86.
- the bolt 96 engages again in the wheel 94 and the system can be made depressurized again.
- FIG. 16 schematically illustrates such a control system.
- a central processing unit (CPU) 98 receives data from a throttle valve 100, an oil temperature sensor 102, which senses the temperature of oil in the region of an engine oil pump 104, from a crankshaft sensor 106 and a camshaft sensor 108 used to determine a position of the camshaft 76 interacts with a signal generator 110. Based on these data, the CPU 98 correspondingly controls the hydraulic pressure valve 64 to set a desired pivot angle of the camshaft 74 between extreme early position and extreme late position.
Description
- Fig. 1
- eine bevorzugte Ausführungsform einer erfindungsgemäßen Zuführungsvorrichtung in Vorderansicht,
- Fig. 2
- in Rückansicht,
- Fig. 3
- in einer Seitenansicht in Richtung Pfeil III von Fig. 1,
- Fig. 4
- in einer Ansicht von unten in Richtung Pfeil IV von Fig. 1,
- Fig. 5
- in einer Seitenansicht in Richtung Pfeil V von Fig. 1,
- Fig. 6
- in einer Ansicht von oben in Richtung Pfeil VI von Fig. 1,
- Fig. 7
- in einer Schnittansicht entlang Linie A-A von Fig. 1,
- Fig. 8
- in einer Schnittansicht entlang Linie B-B von Fig. 1,
- Fig. 9
- in einer Schnittansicht entlang Linie C-C von Fig. 6,
- Fig. 10
- in einer Schnittansicht entlang Linie D-D von Fig. 5,
- Fig. 11
- in einer Schnittansicht entlang Linie E-E von Fig. 6,
- Fig. 12
- in einer Schnittansicht entlang Linie H-H von Fig. 1,
- Fig. 13
- in einer Schnittansicht entlang Linie J-J von Fig. 1,
- Fig. 14
- ein schematisches Blockschaltbild eines Hydraulikkreises der erfindungsgemäßen Zuführungsvorrichtung,
- Fig. 15
- eine schematische Schnittansicht einer montierten Zuführungsvorrichtung im Betrieb und
- Fig. 16
- ein schematisches Schaltbild eines Regelsystems.
Fig. 16 veranschaulicht schematisch ein derartiges Regelsystem. Eine CPU 98 (Central Processing Unit - Zentralrechner) erhält Daten von einer Drosselklappe 100, einem Öltemperatursensor 102, welcher die Temperatur von Öl im Bereich einer Motorölpumpe 104 erfaßt, von einem Kurbelwellensensor 106 und einem Nockenwellensensor 108, welcher zum Bestimmen einer Stellung der Nockenwelle 76 mit einem Signalgeber 110 zusammen wirkt. Auf der Basis dieser Daten steuert die CPU 98 das Hydraulikdruckventil 64 entsprechend an, um einen gewünschten Verschwenkwinkel der Nockenwelle 74 zwischen extremer Früh-Stellung und extremer Spät-Stellung einzustellen.
- 10
- separates Bauteil
- 12
- Ring
- 13
- Ring
- 14
- erste Aufnahme für Hydraulikdruckventile
- 15
- zweite Aufnahme für Hydraulikdruckventile
- 16
- Löcher
- 18
- Halter für eine Gleitschiene
- 20
- erster Hydraulikdruckanschluß
- 22
- zweiter Hydraulikdruckanschluß
- 24
- erster Hydraulikdruckkanal
- 26
- zweiter Hydraulikdruckkanal
- 28
- dritter Hydraulikdruckkanal
- 30
- vierter Hydraulikdruckkanal
- 32
- fünfter Hydraulikdruckkanal
- 34
- sechster Hydraulikdruckkanal
- 36
- siebter Hydraulikdruckkanal
- 38
- erste Nut im ersten Ring
- 40
- achter Hydraulikdruckkanal
- 42
- zweiten Nut des ersten Ringes
- 44
- neunter Hydraulikdruckkanal
- 46
- zehnter Hydraulikdruckkanal
- 48
- elfter Hydraulikdruckkanal
- 50
- zwölfter Hydraulikdruckkanal
- 52
- erste Nut des zweiten Ringes
- 54
- dreizehnter Hydraulikdruckkanal
- 56
- vierzehnter Hydraulikdruckkanal
- 58
- fünfzehnter Hydraulikdruckkanal
- 60
- zweite Nut des zweiten Ringes
- 62
- Hydraulikdruckventil
- 64
- Hydraulikdruckventil
- 66
- Rückschlagventil
- 68
- Rückschlagventil
- 70
- Hydraulikpumpe
- 72
- Hydrauliktankanschluß
- 74
- Nockenwelle
- 76
- Nockenwellenversteller
- 78
- Kolben
- 80
- Schraube
- 82
- erste Ringnut
- 84
- zweite Ringnut
- 86
- Hydraulikdruckkanal
- 88
- erste Hydraulikdruckkammer
- 90
- Hydraulikdruckkanal
- 92
- zweite Hydraulikdruckkammer
- 94
- Rad
- 96
- Bolzen
- 98
- CPU
- 100
- Drosselklappe
- 102
- Öltemperatursensor
- 104
- Motorölpumpe
- 106
- Kurbelwellensensor
- 108
- Nockenwellensensor
- 110
- Signalgeber
- 112
- Kugel
Claims (5)
- Brennkraftmaschine mit einem Zylinderkopf und wenigstens einer an diesem gelagerten Nockenwelle (74), welche angetrieben von einer Kurbelwelle entsprechende Gaswechselventile am Zylinderkopf betätigt, wobei an der Nockenwelle (74) ein Nockenwellenversteller (76) vorgesehen ist, der zum Verändern von Steuerzeiten der Gaswechselventile mittels Hydraulikdruck die Nockenwelle (74) relativ zur Kurbelwelle verdreht, wobei eine Zuführungsvorrichtung für Hydraulikdruck an den Nockenwellenversteller (76) vorgesehen und als vom Zylinderkopf separates Bauteil (10) ausgebildet ist und für jede Nockenwelle (74) einen Ring (12, 13) aufweist, wobei jeder Ring (12, 13) zwei Nuten (38, 42 bzw. 62, 60) aufweist, die über jeweilige Hydraulikdruckkanäle (28, 30, 32, 34, 36 bzw. 40 bzw. 44, 46, 48, 50 bzw. 54, 56, 58) in der Zuführungsvorrichtung (10) mit einem Hydraulikdruckventil (62, 64) verbunden sind, dadurch gekennzeichnet, daß jeder Ring (12, 13) einen Abschnitt der Nockenwelle (74) umgreift und der jeweils umgriffene Abschnitt der Nockenwelle (74) zwei Ringnuten (82, 84) aufweist, welche jeweils mit einer Nut (38, 42 bzw. 62, 60) des entsprechenden Ringes (12, 13) fluchten, wobei jedes Nut/Ringnutpaar (38/82, 42/84) eines Ringes (12, 13) über jeweilige Hydraulikdruckkanäle (86, 90) in der Nockenwelle (74) mit einer Hydraulikdruckkammer (88, 92) des an dieser Nockenwelle (74) angeordneten Nockenwellenverstellers (76) verbunden ist.
- Brennkraftmaschine nach Anspruch 1, dadurch gekennzeichnet, daß die Zuführungsvorrichtung für Hydraulikdruck in dem separaten Bauteil (10) einstückig folgendes aufweist, wenigstens einen Hydraulikdruckanschluß (20, 22), wenigstens einen Hydrauliktankanschluß (72), wenigstens eine Aufnahme (14, 15) für ein Hydraulikdruckventil (62, 64) sowie entsprechende Hydraulikdruckkanäle (24 bzw. 26 bzw. 28, 30, 32, 34, 36 bzw. 40 bzw. 44, 46, 48, 50 bzw. 54, 56, 58), welche derart ausgebildet sind, daß sie jeweils einen Hydraulikdruckanschluß (20, 22) mit der Aufnahme (14, 15) für ein Hydraulikdruckventil (62, 64), jedes Hydraulikdruckventil (62, 64) mit einem Nut/Ringnutpaar (38/82, 42/84) eines Ringes (12, 13) und jede Aufnahme (14, 15) für ein Hydraulikdruckventil (62, 64) mit einem Hydrauliktankanschluß (72) verbinden.
- Brennkraftmaschine nach Anspruch 2, dadurch gekennzeichnet, daß die Aufnahme (14, 15) für ein Hydraulikdruckventil (62, 64) achsparallel oder senkrecht zum Ring (12, 13) angeordnet ist.
- Brennkraftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Hydraulikdruckventil (62, 64) ein 4/2 Proportional-Wegeventil ist.
- Brennkraftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Zuführungsvorrichtung derart ausgebildet ist, daß sie am Zylinderkopf befestigbar ist.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19943833A DE19943833A1 (de) | 1999-09-13 | 1999-09-13 | Brennkraftmaschine mit hydraulischem Nockenwellenversteller zur Nockenwellenverstellung |
DE19943833 | 1999-09-13 | ||
PCT/EP2000/008904 WO2001020135A1 (de) | 1999-09-13 | 2000-09-12 | Brennkraftmaschine mit hydraulischem nockenwellenversteller zur nockenwellenverstellung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1216345A1 EP1216345A1 (de) | 2002-06-26 |
EP1216345B1 true EP1216345B1 (de) | 2005-06-15 |
Family
ID=7921866
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00974375A Revoked EP1216345B1 (de) | 1999-09-13 | 2000-09-12 | Brennkraftmaschine mit hydraulischem nockenwellenversteller zur nockenwellenverstellung |
Country Status (8)
Country | Link |
---|---|
US (1) | US6675752B1 (de) |
EP (1) | EP1216345B1 (de) |
CN (1) | CN1183314C (de) |
AT (1) | ATE298040T1 (de) |
DE (2) | DE19943833A1 (de) |
ES (1) | ES2242646T3 (de) |
PT (1) | PT1216345E (de) |
WO (1) | WO2001020135A1 (de) |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10049494A1 (de) * | 2000-10-06 | 2002-04-11 | Audi Ag | Verstellbare Ventilsteuereinrichtung für eine Brennkraftmaschine |
DE10307624A1 (de) * | 2003-02-22 | 2004-09-02 | Daimlerchrysler Ag | Vorrichtung zur relativen Drehwinkeländerung einer Nockenwelle zu einem Antriebsrad einer Brennkraftmaschine |
EP1618293B1 (de) | 2003-03-29 | 2008-09-24 | Hydraulik-Ring Gmbh | Variable ventilsteuerungseinrichtung in einer brennkraftmaschine |
DE102004001343A1 (de) * | 2004-01-08 | 2005-09-01 | Entec Consulting Gmbh | Variable Ventilsteuerungsvorrichtung mit Nockenwellenverstellung und Ventilhubkonturveränderung |
US7213552B1 (en) | 2003-06-18 | 2007-05-08 | Griffiths Gary L | Variable geometry camshaft |
DE10334690B4 (de) * | 2003-07-30 | 2008-08-21 | Böckmann-Hannibal, Angela, Dipl.-Ing. (FH) | Einrichtung zur Nockenwellenverstellung für Verbrennungskraftmaschinen |
DE102004024222A1 (de) * | 2003-08-15 | 2005-03-10 | Ina Schaeffler Kg | Brennkraftmaschine mit einer hydraulischen Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle |
US6885934B1 (en) * | 2003-10-22 | 2005-04-26 | Robert Bosch Corporation | Method and system for determining camshaft position |
DE102004027636A1 (de) * | 2004-06-05 | 2006-01-05 | Robert Bosch Gmbh | Steuereinrichtung zum Verstellen des Drehwinkels einer Nockenwelle |
DE102005027617A1 (de) * | 2004-07-29 | 2006-03-23 | Ina-Schaeffler Kg | Ringfilter |
DE102005031296A1 (de) * | 2004-07-30 | 2006-03-23 | Ina-Schaeffler Kg | Ringfilter |
JP4276600B2 (ja) * | 2004-09-14 | 2009-06-10 | ヤマハ発動機株式会社 | エンジン |
US7421989B2 (en) * | 2005-09-13 | 2008-09-09 | Delphi Technologies, Inc. | Vane-type cam phaser having increased rotational authority, intermediate position locking, and dedicated oil supply |
US7228831B1 (en) * | 2005-12-14 | 2007-06-12 | Ford Global Technologies, Llc | Camshaft and oil-controlled camshaft phaser for automotive engine |
US7395802B2 (en) * | 2006-06-07 | 2008-07-08 | Ford Global Technologies, Llc | Oil supply for internal combustion engine camshaft |
DE102008030058B4 (de) | 2008-06-27 | 2010-06-17 | Hydraulik-Ring Gmbh | Nockenwellenverstelleinrichtung und geeignetes Ventil dafür |
DE102009016186A1 (de) | 2009-04-03 | 2010-10-14 | Schaeffler Technologies Gmbh & Co. Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH04171205A (ja) * | 1990-10-31 | 1992-06-18 | Atsugi Unisia Corp | 内燃機関のバルブタイミング制御装置 |
DE4229202A1 (de) * | 1992-09-02 | 1994-03-03 | Schaeffler Waelzlager Kg | Vorrichtung für eine stufenlose Winkelverstellung |
DE19502496C2 (de) | 1995-01-27 | 1998-09-24 | Schaeffler Waelzlager Ohg | Vorrichtung zum Verändern der Steuerzeiten einer Brennkraftmaschine |
DE19525836C1 (de) * | 1995-07-15 | 1996-08-01 | Bayerische Motoren Werke Ag | Stellvorrichtung zur relativen Winkelverstellung einer angetriebenen Welle, insbesondere Nockenwelle einer Brennkraftmaschine |
DE19525837A1 (de) | 1995-07-15 | 1997-01-16 | Schaeffler Waelzlager Kg | Vorrichtung zum Verändern der Steuerzeiten einer Brennkraftmaschine |
DE19611606A1 (de) * | 1996-03-23 | 1997-09-25 | Schaeffler Waelzlager Kg | Vorrichtung zum Verändern der Steuerzeiten einer Brennkraftmaschine |
DE19612397A1 (de) * | 1996-03-28 | 1997-10-02 | Bayerische Motoren Werke Ag | Stellvorrichtung zur relativen Winkelverstellung einer angetriebenen Welle, insbesondere Nockenwelle einer Brennkraftmaschine |
JP2924777B2 (ja) * | 1996-04-08 | 1999-07-26 | トヨタ自動車株式会社 | 内燃機関のバルブタイミング可変機構 |
JP3284888B2 (ja) * | 1996-07-03 | 2002-05-20 | トヨタ自動車株式会社 | 内燃機関の油通路構造 |
JPH10184323A (ja) * | 1996-12-26 | 1998-07-14 | Yamaha Motor Co Ltd | 4サイクルエンジン |
DE19708485A1 (de) * | 1997-03-03 | 1998-09-10 | Bayerische Motoren Werke Ag | Drehwinkel-Verstellsystem für gesonderte Einlaß- und Auslaß-Nockenwellen einer Brennkraftmaschine |
DE19726365A1 (de) * | 1997-06-21 | 1998-12-24 | Schaeffler Waelzlager Ohg | Transportsicherung für die Steuerzeiten einer Vorrichtung zum Verändern der Ventilsteuerzeiten einer Brennkraftmaschine |
DE19745670A1 (de) | 1997-10-17 | 1999-04-22 | Schaeffler Waelzlager Ohg | Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE19747244A1 (de) | 1997-10-27 | 1999-04-29 | Schaeffler Waelzlager Kg | Zylinderkopf |
JP4070857B2 (ja) * | 1997-12-17 | 2008-04-02 | トヨタ自動車株式会社 | 内燃機関のバルブ特性制御装置 |
JP3539182B2 (ja) * | 1998-02-20 | 2004-07-07 | トヨタ自動車株式会社 | 可変バルブタイミング装置 |
JPH11303615A (ja) * | 1998-04-24 | 1999-11-02 | Yamaha Motor Co Ltd | 可変バルブタイミング装置付きエンジン |
DE19834843A1 (de) * | 1998-08-01 | 2000-02-03 | Porsche Ag | Einrichtung zur relativen Drehlagenänderung einer Welle zum Antriebsrad |
-
1999
- 1999-09-13 DE DE19943833A patent/DE19943833A1/de not_active Ceased
-
2000
- 2000-09-12 PT PT00974375T patent/PT1216345E/pt unknown
- 2000-09-12 DE DE50010575T patent/DE50010575D1/de not_active Revoked
- 2000-09-12 WO PCT/EP2000/008904 patent/WO2001020135A1/de active IP Right Grant
- 2000-09-12 CN CNB008102635A patent/CN1183314C/zh not_active Expired - Fee Related
- 2000-09-12 ES ES00974375T patent/ES2242646T3/es not_active Expired - Lifetime
- 2000-09-12 AT AT00974375T patent/ATE298040T1/de not_active IP Right Cessation
- 2000-09-12 US US10/088,453 patent/US6675752B1/en not_active Expired - Fee Related
- 2000-09-12 EP EP00974375A patent/EP1216345B1/de not_active Revoked
Also Published As
Publication number | Publication date |
---|---|
DE50010575D1 (de) | 2005-07-21 |
PT1216345E (pt) | 2005-09-30 |
ES2242646T3 (es) | 2005-11-16 |
WO2001020135A1 (de) | 2001-03-22 |
CN1360661A (zh) | 2002-07-24 |
CN1183314C (zh) | 2005-01-05 |
DE19943833A1 (de) | 2001-03-15 |
ATE298040T1 (de) | 2005-07-15 |
US6675752B1 (en) | 2004-01-13 |
EP1216345A1 (de) | 2002-06-26 |
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