EP1216345B1 - Internal combustion engine with hydraulic camshaft adjuster for adjusting the camshaft - Google Patents

Abstract

An internal combustion engine including a cylinder head having gas-exchange valves, at least one camshaft supported on the cylinder head, which camshaft is driven by a crankshaft to actuate corresponding gas-exchange vales on the cylinder head, and a camshaft adjuster arranged on the camshaft. The adjuster has a hydraulic pressure chamber and is configured to use hydraulic pressure to rotate position of the camshaft relative to the crankshaft to change control times of the gas-exchange valves. A feed device for hydraulic pressure is provided on the camshaft adjuster and is configured as a component separate from the cylinder head. The feed device has a ring for each camshaft, each ring having two grooves, each of the grooves being connected via associated hydraulic pressure channels in the feed device to a hydraulic pressure valve. Each ring is arranged to surround a section of the camshaft. Each surrounded section of the camshaft has two ring-shaped grooves, each of which is aligned with one of the grooves of the corresponding ring to form a pair. Each groove/ring-shaped groove pair of a ring is connected via associated hydraulic pressure channels in the camshaft to the hydraulic pressure chamber of the camshaft adjuster mounted on the camshaft.

Description

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. By means provided in a housing cover 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.

From DE 197 47 244 A1 it is known at one end of a camshaft in provide a storage area thereof in the cylinder head annular grooves and over These annular grooves hydraulic means arranged on the camshaft Nokkenwellenversteller supply. To losses in hydraulic fluid tap in the area To avoid the bearing of the camshaft is in a half shell of the bearing a this overlapping sleeve bearing ring inserted. This integration of the hydraulic fluid supply in the cylinder head itself, however, makes this consuming and costly to manufacture. Further, by the supply of the hydraulic fluid via a bearing shell of a bearing of the camshaft in the cylinder head weakened this camp accordingly.

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 Hydarulikdruckkanäle 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.

This object is achieved by an internal combustion engine o.g. kind solved with the features characterized in claim 1. Advantageous embodiments The invention are set forth in the dependent claims.

In an internal combustion engine o.g. Art it is provided according to the invention, that 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 / Ringnutpaar 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.

This has the advantage that a simple in production and assembly hydraulic fluid supply for camshaft adjuster of a camshaft available stands.

In a preferred embodiment, 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 / Ringnutpaar a ring and each receptacle for a Connect hydraulic pressure valve to a hydraulic tank connection. Here is the Recording for a hydraulic pressure valve, for example, axially parallel or perpendicular arranged to the ring.

A pivoting of the camshaft with arbitrary intermediate positions of the Position of the camshaft between corresponding end positions at the same time large pivoting with swivel angles of example larger sixty degrees is achieved by the hydraulic pressure valve being a 4/2 proportional directional control valve is.

Conveniently, the feeding device is designed such that it Cylinder head is fastened.

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.

Further features, advantages and advantageous embodiments of the invention will become apparent from the dependent claims, and from the following description of the invention with reference to the accompanying drawings. These show in

Fig. 1

A preferred embodiment of a feeding device according to the invention in front view,

Fig. 2

in rear view,

Fig. 3

in a side view in the direction of arrow III of Fig. 1,

Fig. 4

in a view from below in the direction of arrow IV of Fig. 1,

Fig. 5

in a side view in the direction of arrow V of Fig. 1,

Fig. 6

in a view from above in the direction of arrow VI of FIG. 1,

Fig. 7

in a sectional view along line AA of Fig. 1,

Fig. 8

in a sectional view taken along line BB of Fig. 1,

Fig. 9

in a sectional view taken along line CC of Fig. 6,

Fig. 10

in a sectional view taken along line DD of Fig. 5,

Fig. 11

in a sectional view taken along line EE of Fig. 6,

Fig. 12

in a sectional view taken along line HH of Fig. 1,

Fig. 13

in a sectional view taken along line JJ of Fig. 1,

Fig. 14

a schematic block diagram of a hydraulic circuit of the feeding device according to the invention,

Fig. 15

a schematic sectional view of a mounted feeder in operation and

Fig. 16

a schematic diagram of a control system.

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 illustrated in Figs. 1 to 13 preferred Embodiment of a supply device according to the invention for hydraulic means a camshaft adjuster, not shown, is a separate component 10 with two Rings 12 and receptacles 14 formed for hydraulic pressure valves, not shown. 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. Here, the form in Fig. 2 hatched or dashed areas shown corresponding contact surfaces on Cylinder head. On the component 10 is 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.

According to the invention, 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. By way of example, balls 112 are indicated in FIG. 15.

As can be seen in particular from FIG. 2, 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. Of 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 Hydraulikdruckkammem 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.

By provided in the receptacles 14, 15 4/2 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.

For pivoting the rotating in the rings 12 and 13 camshafts apply the arranged in the receptacles 14, 15 hydraulic pressure valves controlled by a controller, not shown, which below Referring to Fig. 16, corresponding ones of the receptacles 14 and 15 will be explained away running hydraulic pressure channels. If, for example, in the first ring 12th rotating camshaft pivoted in one direction (for example, early position) be, so sets the arranged in the receptacle 14 hydraulic pressure valve the Hydraulic pressure channels 28, 30, 32, 34 and 36 (see Fig. 8 and 9 in this order) under pressure, which then via the first groove 38 in the first ring 12 in the camshaft and thus to a corresponding hydraulic pressure chamber of the camshaft adjuster is passed on. If the rotating in the first ring 12 camshaft in the other Direction (for example, late position) are pivoted, so that is in the 14 arranged hydraulic pressure valve, the hydraulic pressure channel 40 (see Fig. 11 and 12) under pressure, which then via the second groove 42 in the first ring 12 in the Camshaft and thus to a corresponding hydraulic pressure chamber of the Camshaft adjuster is passed on. Should an intermediate position between Frühund Set late position, so sets the arranged in the receptacle 14 Hydraulic pressure valve, both the hydraulic pressure channels 28, 30, 32, 34 and 36 and the Hydraulic pressure channel 40 under pressure and regulates both pressures such that a desired pivoting or adjustment of the camshaft results.

If the rotating in the second ring 13 camshaft in one direction (for example Early position) are pivoted, so it is in the receptacle 15 arranged Hydraulic pressure valve, the hydraulic pressure channels 44, 46, 48 and 50 (see Fig. 13 and 9 in this order) under pressure, which then via the first groove 52 in the second ring 13th in the camshaft and thus to a corresponding hydraulic pressure chamber of Camshaft adjuster is passed on. If the rotating in the second ring 13 Camshaft in the other direction (for example, late position) to be pivoted so sets the arranged in the receptacle 15 hydraulic pressure valve the Hydraulic pressure channels 54, 56 and 58 (see Fig. 7 and 11 in this order) under Pressure, which then via the second groove 60 in the second ring 13 in the camshaft and thus further to a corresponding hydraulic pressure chamber of the camshaft adjuster is directed. If an intermediate position between early and late position set be, so sets the arranged in the receptacle 15 hydraulic pressure valve both the Hydraulic pressure channels 44, 46, 48 and 50 and the hydraulic pressure channels 54, 56 and 58th under pressure and regulates both pressures such that there is a desired pivoting or adjustment of the camshaft results.

FIG. 14 schematically illustrates one in the separate component 10 According to 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. In the receptacle 15 of the component 10th 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. Femer, 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. Depending on which of the two hydraulic pressure chambers 88, 90 is pressurized, 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. In the As shown in FIG. 15, 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. In contrast, 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. If both the hydraulic pressure channels 24, 56, 84 and 90, the second hydraulic pressure chamber 92 and the hydraulic pressure channels 24, 44, 46, 48, 82 and 86, the first hydraulic pressure chamber 88 are pressurized, the system is in control position and it will an intermediate position between the extreme early and late position regulated according to the specification of a regulation.
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.

LIST OF REFERENCE NUMBERS

10

separate component

12

ring

13

ring

14

first intake for hydraulic pressure valves

15

second intake for hydraulic pressure valves

16

holes

18

Holder for a slide rail

20

first hydraulic pressure connection

22

second hydraulic pressure connection

24

first hydraulic pressure channel

26

second hydraulic pressure channel

28

third hydraulic pressure channel

30

fourth hydraulic pressure channel

32

fifth hydraulic pressure channel

34

sixth hydraulic pressure channel

36

seventh hydraulic pressure channel

38

first groove in the first ring

40

eighth hydraulic pressure channel

42

second groove of the first ring

44

ninth hydraulic pressure channel

46

tenth hydraulic pressure channel

48

eleventh hydraulic pressure channel

50

twelfth hydraulic pressure channel

52

first groove of the second ring

54

thirteenth hydraulic pressure channel

56

fourteenth hydraulic pressure channel

58

fifteenth hydraulic pressure channel

60

second groove of the second ring

62

Hydraulic pressure valve

64

Hydraulic pressure valve

66

check valve

68

check valve

70

hydraulic pump

72

Hydraulic tank connection

74

camshaft

76

Phaser

78

piston

80

screw

82

first ring groove

84

second annular groove

86

Hydraulic pressure passage

88

first hydraulic pressure chamber

90

Hydraulic pressure passage

92

second hydraulic pressure chamber

94

wheel

96

bolt

98

CPU

100

throttle

102

Oil temperature sensor

104

Engine oil pump

106

crankshaft sensor

108

camshaft position sensor

110

signaler

112

Bullet

Claims (5)

1. Internal combustion engine having a cylinder head and at least one camshaft (74) which is mounted on the latter and actuates corresponding gas exchange valves on the cylinder head in a manner driven by a crankshaft, a camshaft adjuster (76) being provided on the camshaft (74), which camshaft adjuster (76) rotates the camshaft (74) relative to the crankshaft by means of hydraulic pressure in order to change control times of the gas exchange valves, a feed apparatus for feeding hydraulic pressure to the camshaft adjuster (76) being provided and being configured as a separate component (10) from the cylinder head and having a ring (12, 13) for each camshaft (74), each ring (12, 13) having two grooves (38, 42 or 62, 60) which are connected to a hydraulic pressure valve (62, 64) via respective hydraulic pressure ducts (28, 30, 32, 34, 36 or 40 or 44, 46, 48, 50 or 54, 56, 58) in the feed apparatus (10), characterized in that each ring (12, 13) surrounds a section of the camshaft (74) and the respectively surrounded section of the camshaft (74) has two annular grooves (82, 84) which are each aligned with a groove (38, 42 or 62, 60) of the corresponding ring (12, 13), each groove/annular groove pair (38/82, 42/84) of a ring (12, 13) being connected via respective hydraulic pressure ducts (86, 90) in the camshaft (74) to a hydraulic pressure chamber (88, 92) of the camshaft adjuster (76) which is arranged on this camshaft (74).
2. Internal combustion engine according to Claim 1, characterized in that the feed apparatus for hydraulic pressure has the following component parts integrally in the separate component (10): at least one hydraulic pressure connection (20, 22), at least one hydraulic tank connection (72), at least one receptacle (14, 15) for a hydraulic pressure valve (62, 64), and appropriate hydraulic pressure ducts (24 or 26 or 28, 30, 32, 34, 36 or 40 or 44, 46, 48, 50 or 54, 56, 58) which are configured in such a way that they connect in each case one hydraulic pressure connection (20, 22) to the receptacle (14, 15) for a hydraulic pressure valve (62, 64), each hydraulic pressure valve (62, 64) to a groove/annular groove pair (38/82, 42/84) of a ring (12, 13), and each receptacle (14, 15) for a hydraulic pressure valve (62, 64) to a hydraulic tank connection (72).
3. Internal combustion engine according to Claim 2, characterized in that the receptacle (14, 15) for a hydraulic pressure valve (62, 64) is arranged axially parallel or perpendicular with respect to the ring (12, 13).
4. Internal combustion engine according to one of the preceding claims, characterized in that the hydraulic pressure valve (62, 64) is a proportional 4/2-way valve.
5. Internal combustion engine according to one of the preceding claims, characterized in that the feed apparatus is configured in such a way that it can be fastened to the cylinder head.

Images