EP0797726B1 - Valve gear mechanism for an internal combustion engine - Google Patents

Abstract

PCT No. PCT/DE95/01783 Sec. 371 Date Aug. 22, 1997 Sec. 102(e) Date Aug. 22, 1997 PCT Filed Dec. 12, 1995 PCT Pub. No. WO96/18807 PCT Pub. Date Jun. 20, 1996A valve gear mechanism for an internal combustion engine includes a variable valve control mechanism comprising a shaft (1) having an axis of rotation (D) and serving to transmit the rotary motion to the valve gear mechanism; a rotating body (10) being rotatably supported on said shaft (1); and an intermediate member (20) surrounding said shaft (1) and being disposed adjacent to said rotatable rotating body (10) in an axial direction and being rotatable with respect to said shaft (1) and having a drive connection to said shaft (1) via a first sliding guide (15) and a first transmission element (40, 50) and to said rotating body (10) via a second sliding guide (16) and a second transmission element (70), wherein said first transmission element (40, 50) comprises a radial pin (40) being inserted in said shaft (1) in a direction substantially vertical to said axis of rotation (D). The radial pin (40) is preferably held so as to be displaceable in a recess (51) of a sliding block (50) which is pivotably mounted in a bearing seat (22) in said intermediate member (20).

Description

The invention relates to a valve train Internal combustion engine and in particular a valve train an internal combustion engine in which a rotating body, preferably a cam, on a shaft, preferably the Camshaft, during the rotation of the shaft cyclically is rotatable, thereby variable valve control to provide.

Such a valve train is for example in WO-A-96/23963 described. One disclosed in this patent application Adjustment mechanism is shown in Fig. 23 and includes a camshaft 100 with an axis of rotation 500 on which a Cam 200 is stored. Also on camshaft 100 is mounted an inner eccentric 300, on the Axis of rotation 500 eccentric outer surface 320 External eccentric 400 is mounted. The internal eccentric 300 and the outer eccentric 400 are over one Internal eccentric ring gear 340 or one External eccentric ring gear 440 rotatable, making one on one eccentric outer surface of the outer eccentric 400 mounted intermediate link 490 in a plane perpendicular to The axis of rotation 500 is displaceable relative to the camshaft 100 is. The intermediate member 490 is with the cam 200 and Drive shaft 100 coupled. This intervenes as the first transmission element 800 rotatable in the Camshaft 100 bearing axial pin 800 with a the axial pin 800 formed of the same material Sliding stone flag 810 in a slide guide a first groove 600 formed in the link 490 is trained. One of the first groove 600 diametrically opposite second groove 700 of the intermediate member 490 is in engagement with a sliding stone flag 910, the same material with a second axial pin 900 is formed, which is rotatable in a bore 110 of the Cam 200 is stored.

The rotation of the camshaft 1 is over the first Axial pin 100 through its tab 110 and the first groove 600 transferred to the intermediate link 490 and from there on the second groove 700 and the flag 910 of the second Axial pin 900 on cam 200. Is that Intermediate member 490 in a concentric position Camshaft 100, the cam 200 rotates synchronously the camshaft 100. In contrast, becomes the intermediate link 490 shifted in a plane perpendicular to the axis of rotation 500, so there is one with each revolution of the camshaft 100 cyclical increase and subsequent lowering of the Speed of rotation of the cam 200 compared to the Camshaft 100 instead, which is used to effective opening time of a not shown To influence the gas inlet valve of an internal combustion engine, which is operated via a tappet 205.

In the movement described above, in addition to the Torque forces a tipping moment on the intermediate member 490 exercised on the storage of the pontic 490 is supported on the external eccentric 400. Do this relatively high forces in this area Are particularly critical since it is a high-speed warehouse that the Relative speed of the practically stationary External eccentric 400 and the practical with Camshaft speed rotating link 490 is exposed. Under unfavorable conditions, it can Intermediate link 490 tend to tilt.

Another disadvantage of this arrangement arises in that the tilting moment of the intermediate link 490 its parallelism to the cam 200 is not guaranteed is. This can mean that between the Sliding stone flags 810 and 910 of the axial pins 800 or 900 and the grooves 600 or 700 of the intermediate link 490 not always touching the surface, but there may be edge contact. This significantly increases wear in this area.

A generic valve train is still from FR-A-2305589 or known from JP-A-05 118208.

The object of the invention is that described above Develop the state of the art in such a way that minimal construction volume the friction between themselves components moving towards each other and thus wear of these components is reduced.

The solution to this problem is in claim 1 specified.

According to the invention, a valve train has one Internal combustion engine with an adjustment mechanism a shaft having an axis of rotation, over which the Rotary movement for the valve train initiated in this is, with a rotatably mounted relative to the shaft Rotating body and with a surrounding the shaft Intermediate link, which in the axial direction next to the rotatable rotating body arranged and opposite the shaft is rotatable and with the shaft over a first Slideway and a first transmission element and with the rotating body via a second sliding guide and a second transmission element is drivingly connected. At least one of the transmission elements comprises a radial pin that is substantially perpendicular to the Axis of rotation of the shaft is arranged.

The use of a radial pin as a transmission element has the advantage that when force is applied Tipping moment can be reduced, which makes the overall occurring tilting moment is reduced. Preferably the first transmission element is a radial pin.

So that the intermediate link the cyclical rotation of the Rotary body can cause against the shaft, must Relative displacement between the shaft and the Intermediate link in the longitudinal direction of the radial pin and one Pivotal movement of the radial pin relative to the Intermediate link may be possible. For example caused by the radial pin at the end, with which he engages with the pontic has a kind of ball head, which in the Intermediate link is stored. This will make the necessary Allows swivel movement. The radial displacement must be in in this case take place in that the radial pin in can shift its longitudinal direction with respect to the shaft.

In another preferred embodiment, the Radial pin in a recess in a sliding block slidably received in a bearing seat of the Intermediate link is pivotally mounted. At this Embodiment takes the pivotal movement between the Sliding block and the bearing seat of the intermediate link instead, while the longitudinal displacement between the radial pin and the sliding block takes place. This allows the radial pin be firmly fixed in the shaft.

In this embodiment, the radial pin can be one cylindrical section and essentially one have rectangular section, the cylindrical Section is inserted into a radial bore of the shaft and the substantially rectangular section in sliding engagement with the recess of the sliding block stands. Between the cylindrical section and the im essential rectangular section of the radial pin can a paragraph may be provided with one on the shaft a positive locking element against migration of the radial pin from the Radial bore forms.

The diameter of the cylindrical section is preferably smaller than the larger of the two Cross-sectional edges of the substantially rectangular Section.

The sliding block preferably has the outer contour of a cylinder segment flattened on two sides, whereby the two rounded sides of the jacket segments Cylinders are joined together by an end face are connected. The recess is preferably that of the Face opposite side of the sliding block open. The sliding block has two sliding surfaces Sliding contact with two opposite one another Faces of the rectangular section of the radial pin and two shoulders to rest on a third surface of the rectangular section of the radial pin. Between A depression can be formed around the shoulders To facilitate assembly of the radial pin. If the Diameter of the cylindrical section of the radial pin is smaller than at least the larger of the two Cross-sectional edges of the substantially rectangular Section, the cylindrical section of the Radial pin through the recess into the Radial bore of the shaft are introduced.

The bearing seat is preferably on the rotating body facing side of the intermediate link open and has two concave side walls, the radius of curvature of which the Side faces of the sliding block correspond, as well as one End face for contact with the end face of the radial pin on. This allows the sliding block in the side Bearing seat can be used.

The axial fixation of the rotating body and the Intermediate link on the shaft can be via the radial pin respectively.

The second transmission element can be parallel to Axis of rotation mounted in a bore of the rotating body Grip axial pin. A particularly compact arrangement to realize the washer Have interruption that gives free access to the Axial pin guaranteed, the washer on the side opposite the interruption Has flat, which rests on the sliding block and as Anti-rotation lock of the washer acts.

The side surfaces of the sliding stone flag can become one or both sides of the axial pin over the circumference of its extend cylindrical shaft so that the Axial pin together with the sliding stone flag an L-shape or has a T-shape. This will make an enlarged one Contact surface of the sliding stone flag and thus one Reduction of the surface pressure to the groove of the Pontic and in the case of a T-shape one symmetrical application of force achieved.

The bore of the rotating body in which the axial pin can be stored on the side of the The pontic is turned away, closed and the Shaft can have a longitudinal bore as well as one or more of the longitudinal bore to the outer surface of the shaft have running shaft oil holes. By doing Rotary body can be arranged a rotary body oil hole be that oil from the longitudinal bore of the shaft over the Shaft oil hole and the rotating body oil hole in the Bore for storing the axial pin between these and the closed end of this hole passes through the axial pin by the oil pressure in firm contact with the End wall is pressed in the groove of the intermediate link.

As a result, the sliding behavior of the sliding stone flag in the groove improved.

In a further advantageous embodiment, a third sliding guide between the rotating body and the Intermediate member provided which is a support between the Rotating body and the intermediate member represents and at the same time a relative movement between the rotating body and the intermediate link in a direction perpendicular to Allows axis of rotation.

This third sliding guide is used by the Transfer of the rotational movement generated tilting moment on the Include pontic. Through this The support provided will be the fastest Bearing point between the intermediate link and the External eccentric relieved. Instead, the support is found against this tilting moment between the rotating body and the Intermediate link instead, which is only a minor Have relative speed to each other. The free Tipping moment is about in the valve train according to the invention the large bearing between the rotating body and supported on the shaft, on which also only slight Relative speeds occur and therefore only is lightly loaded. This will make the Total system friction losses significantly reduced. In addition, the holding torque of the external eccentric becomes clear decreased.

The third sliding guide can be designed so that in a groove is provided in the rotary body, in which a Intermediate link trained web engages. In a special advantageous embodiment, the groove runs in Circumferential direction of the rotating body, wherein by a Opening is interrupted, through which the Intermediate link with the web can be inserted in the radial direction is.

To increase the contact area for the pontic, can have an intermediate washer in the groove next to the web be included. This creates an attachment to the Pontic also take place in the area where the groove is interrupted.

Since in the embodiment described above, the free Tipping moment at the bearing between the rotating body and Shaft is supported, it is advantageous to use this Bearing point to be executed particularly wide. For this reason the rotating body can move in the direction of the bearing surface the axis of rotation be widened and have dimensions, which are wider than at least a section of the Outer contour of the rotating body.

The shaft is preferably a camshaft and the Rotating body a cam for actuating a Gas exchange valve. This makes it extremely compact Device for variable valve control provided. The intermediate link can be designed so that its outer contour in no operating position over the Outer contour of the cam protrudes. This enables the Use of this embodiment in bucket tappet motors.

Fig. 1

einen Axialschnitt durch eine erste Ausführungsform der erfindungsgemäßen Anordnung zeigt,

Fig. 1A

eine auseinandergezogene perspektivische Darstellung wesentlicher Bauteile der Anordnung nach Fig. 1 unter Weglassung der Nockenwelle,

Fig. 1B

eine Fig. 1A entsprechende auseinandergezogene perspektivische Darstellung unter einem anderen Blickwinkel,

Fig. 2

ein Radialschnitt längs der Linie E-E in Fig. 1 ist,

Fig. 3

eine Frontalansicht eines als Nocken ausgebildeten Drehkörpers ist,

Fig. 4

eine Seitenansicht des Nockens gemäß Fig. 3 ist,

Fig. 5

eine Schnittansicht des Nockens längs der Linie C-C in Fig. 3 ist,

Fig. 6

eine perspektivische Darstellung des Nockens nach Fig. 3 ist,

Fig. 7

eine Frontalansicht einer Ausführungsform eines Zwischenglieds ist,

Fig. 8

eine Seitenansicht des Zwischenglieds nach Fig. 7 ist,

Fig. 9

eine Schnittansicht des Zwischenglieds längs der Linie H-H in Fig. 7 ist,

Fig. 10

eine Schnittansicht des Zwischenglieds längs der Linie I-I in Fig. 8 ist,

Fig. 11

eine perspektivische Darstellung des Zwischenglieds gemäß Fig. 7 ist,

Fig. 12

eine erste Seitenansicht einer Ausführungsform eines Radialstifts ist,

Fig. 13

eine perspektivische Darstellung des Radialstifts nach Fig. 12 ist,

Fig. 14

eine Ansicht des Radialstifts nach Fig. 12 von oben ist,

Fig. 15

eine erste Seitenansicht einer Ausführungsform eines Gleitsteins ist,

Fig. 16

eine perspektivische Darstellung des Gleitsteins nach Fig. 15 ist,

Fig 17

eine Draufsicht des Gleitsteins nach Fig. 15 in Richtung des Pfeils X in Fig. 15 ist,

Fig. 18

ein Axialschnitt durch eine zweite Ausführungsform einer erfindungsgemäßen Anordnung ist,

Fig. 19

ein Radialschnitt längs der Linie G-G in Fig. 18 ist,

Fig. 20

eine Darstellung einer Zwischenscheibe ist,

Fig. 21

ein Radialschnitt durch eine dritte Ausführungsform der erfindungsgemäßen Anordnung ist,

Fig. 22

einen Radialschnitt längs der Linie L-L in Fig. 21 ist und

Fig. 23

einen Axialschnitt durch einen Verstellmechanismus gemäß einem nicht vorveröffentlichten Stand der Technik zeigt.

Further features and advantages of the invention are illustrated by the following description of advantageous exemplary embodiments with reference to the accompanying drawing, in which

Fig. 1

3 shows an axial section through a first embodiment of the arrangement according to the invention,

Fig. 1A

2 shows an exploded perspective view of essential components of the arrangement according to FIG. 1 with the camshaft omitted,

Figure 1B

1A corresponding exploded perspective view from a different angle,

Fig. 2

is a radial section along the line EE in Fig. 1,

Fig. 3

2 is a front view of a rotating body designed as a cam,

Fig. 4

3 is a side view of the cam,

Fig. 5

FIG. 3 is a sectional view of the cam along line CC in FIG. 3,

Fig. 6

3 is a perspective view of the cam according to FIG. 3,

Fig. 7

FIG. 2 is a front view of an embodiment of an intermediate link,

Fig. 8

7 is a side view of the intermediate link according to FIG. 7,

Fig. 9

FIG. 7 is a sectional view of the intermediate link along the line HH in FIG. 7,

Fig. 10

FIG. 8 is a sectional view of the intermediate link along the line II in FIG. 8,

Fig. 11

7 is a perspective view of the intermediate link according to FIG. 7,

Fig. 12

FIG. 1 is a first side view of an embodiment of a radial pin,

Fig. 13

12 is a perspective view of the radial pin according to FIG. 12,

Fig. 14

12 is a top view of the radial pin of FIG. 12,

Fig. 15

FIG. 1 is a first side view of an embodiment of a sliding block,

Fig. 16

15 is a perspective view of the sliding block according to FIG. 15,

Fig. 17

15 is a plan view of the sliding block according to FIG. 15 in the direction of arrow X in FIG. 15,

Fig. 18

3 is an axial section through a second embodiment of an arrangement according to the invention,

Fig. 19

18 is a radial section along the line GG in FIG. 18,

Fig. 20

is a representation of a washer,

Fig. 21

3 is a radial section through a third embodiment of the arrangement according to the invention,

Fig. 22

is a radial section along the line LL in Fig. 21 and

Fig. 23

shows an axial section through an adjustment mechanism according to a not previously published prior art.

With reference to Figures 1-17, one is described below first embodiment of a valve train with a Adjustment mechanism to provide a variable Valve control for internal combustion engines explained. A as Cam-formed rotating body 10 is rotatable on a trained as a camshaft shaft 1, which at Operation of the internal combustion engine, preferably by the Crankshaft of the internal combustion engine (not shown), with half crankshaft speed is rotated. In axial In the direction next to the cam 10 is an inner eccentric 91 provided, which is rotatable by a bearing block 92 to a cylinder head 93, which is only shown in a hint is fixed. On an eccentric to the axis of rotation D. The outer surface of the inner eccentric 91 is an outer eccentric 90 rotatably mounted. The inner eccentric 91 is over one Internal eccentric ring gear 91A rotatable during the External eccentric 90 through a coaxial to the axis of rotation D. the external eccentric ring gear 90A is rotatable, which with a nose 90B in a groove 90C of the External eccentric engages.

Is located between the cam 10 and the eccentric arrangement an intermediate member 20, which is on an eccentric Outer surface of the outer eccentric 90 is rotatably mounted. Each after the position of the outer eccentric 90 and the inner eccentric 91 takes the intermediate member 20 to the axis of rotation D. coaxial position or a position in which its Axis of rotation relative to the axis of rotation D of the camshaft 1 is offset.

The intermediate member 20 is with the camshaft 1 and Cam 10 drivingly connected, so that a rotation of the Camshaft 1 via intermediate member 20 on cam 10 is transmitted. If depending on the position of the External eccentric 90 and the inner eccentric 91 the rotation of the intermediate member 20 concentric with the rotation of the Camshaft 1 runs, the cam 10 rotates synchronously with the camshaft 1. Is by appropriate Displacement of the external eccentric 90 and / or Inner eccentric 91 the intermediate member 20 from his concentric position radially to the camshaft 1 shifted, there is a cyclic one with every revolution Speed increase or speed reduction the speed of rotation of the cam 10 compared to that of the camshaft 1 instead.

The drive connection of the camshaft 1 to Intermediate member 20 takes place via a radial pin 40, which in a corresponding radial bore 4 of the camshaft 1 is introduced. The camshaft 1 has a Longitudinal bore 2 and the radial bore 4 has a depth that is greater than the sum of the camshaft radius and the radius of the longitudinal bore 2.

The radial pin 40 has a cylindrical section 42 which is fully inserted into the camshaft 1 and a generally rectangular section 43 which protrudes from the camshaft 1. Between the cylindrical portion 42 and the rectangular portion 43 a shoulder 41 is formed. By selection suitable fit dimensions between the cylindrical part 42 of the radial pin 40 and the radial bore 4 and one corresponding stop at the closed end of the Radial bore 4, the radial pin 40 is fixed in the Camshaft 1 fixed. As an additional positive The inner eccentric 91 partially covers the fuse Radial bore 4, which due to the shoulder 41 a additional protection against migration of the Radial pin 40 is reached from the bore 4.

To more advantageous friction between the Bore 4 partially overlapping section of the Inner eccentric 91 and shoulder 41 between the cylindrical portion 42 and the rectangular portion To receive 43 of the radial pin 40 is the shoulder 41 with a radius corresponding to the curvature of the surface the camshaft 1 (see Fig. 12). Hereby surface contact is ensured and the Formation of a lubricating film enables.

The rectangular section 43 is covered by a recess 51 a sliding block 50 slidably includes. The sliding block 50 has the shape of a flattened on two sides Cylinder segment, with the two rounded Side surfaces 52, 53 are jacket segments of a cylinder, which are connected to one another by an end face 54. The recess 51 is that of the end face 54 opposite side open and has two Sliding surfaces 55, 56 for sliding contact with two each other opposite faces of the rectangular portion 43 the radial pin 40 and two shoulders 57, 58 to the system to a third surface of the rectangular section 43 of the Radial pin 40 on.

There is a depression 59 between the shoulders 57, 58 trained to assemble the radial pin 40 facilitate. If the diameter of the cylindrical portion 42 of the radial pin 40 smaller than at least the larger of the two Cross-sectional edges 44, 45 of its substantially rectangular section 43, the radial pin 40 due to the recess 59 by the overlap with of the radial bore 4 lying recess 51 in the shaft 1 be inserted.

The rectangular section 43 of the radial pin 40 and the Recess 51 of the sliding block 50 are in terms of their Dimensions matched so that the sliding block 50 can slide over the rectangular section 43.

The intermediate member 20 has a bearing seat 22 which the side facing the cam 10 is open. The to the open side adjacent concave side walls 25, 26 of the Bearing seat 22 are the radius of the side surfaces 52, 53 of the sliding block 50 formed accordingly, so that the through the open side of the bearing seat 22 into the bearing seat 22 insertable sliding block 50 opposite the intermediate link 20 can be pivoted. An end face 27 of the Bearing seat 22 serves to abut the sliding block 50 recess 27A provided in the end face 27 allows the insertion of the radial pin 40 in the Assembly.

On the side of the bearing seat 22 opposite Intermediate member 20 has a groove 23 into which one Sliding stone flag 71 engages with the same material an axial pin 70 is formed. The axial pin 70 is rotatable in a closed at one end and parallel to the axis of rotation D extending bore 13 in the cam 10 stored. A rotating body oil hole provided in the cam 10 19 is at least temporarily in overlap with a shaft oil bore 3 of the camshaft 1 and opens with its opposite end in the bore 13 in one Area between that of the sliding stone flag 71st opposite end of the axial pin 70 and the closed End of the bore 13. Through an appropriate groove (not shown) of the cam 10 in the area of the bearing surface Camshaft 1 can be ensured that the Rotary body oil bore 19 over the entire range of rotation Cam 10 opposite the camshaft 1 in connection with the shaft oil hole 3 is located. That way ensures that a in the longitudinal bore 2 Camshaft 1 prevailing oil pressure on the front side of the axial pin 70 is applied and the Sliding flag 71 against the end wall 24 of the groove 23 of the Intermediate member 20 presses to the game between the Sliding stone flag 71 and the groove 23 when changing the system dampen. The diameter of the pin of the axial pin 70 is preferably smaller than the width of the Sliding stone flag 21 or the groove 23. The length the pin of the axial pin 70 is preferably larger than half the width of the cam 1.

The intermediate member 20 has that end the open side of the groove 23 and the open side of the Bearing seat 22 has, via a web 21 which in runs essentially in the circumferential direction and through the groove 23 and the open side of the bearing seat 22 interrupted becomes. The web 21 can be inserted radially into a Groove 11 are introduced, which on the intermediate member 20th facing side of the cam 10 is formed. The groove 11 runs essentially in the circumferential direction and will interrupted by an opening 12 which the radial Inserting the web 21 allows. The depth of the groove 11 and the strength of the web 21 are so on top of each other matched that a tilting moment of the intermediate member 20th can be caught and at the same time over one radial displacement and a certain extent Rotation of the intermediate member 20 relative to the cam 10 is possible.

The groove 11 of the cam 10 is on the intermediate member 20 facing side by an essentially in Limited circumferential web 17, the is also interrupted by the opening 12. To the Enlarge the contact surface to absorb the tilting moment, this web 17 gives way in a central region 18 in the region the line D-D in Fig. 3 from the circumferential direction. In this area is the web 17 with respect to the bottom of the Groove 11 increased, for example, in that in the Middle region 18 the upper edges of the web 17 on both Sides of the bore for the camshaft 1 parallel to each other.

Accordingly, the bottom is that on the intermediate member 20 groove 28 formed by the web 21 in one corresponding central region 29 opposite the upper edge of the web 21 lowered, for example in that this central region 29 the bottom portions of the groove 28 have a changed radius of curvature.

Taking into account the fact that at multi-cylinder engines multiple adjustment mechanisms of the previously described in a continuous Camshaft 1 are mounted, the Assembly process of these mechanisms as follows.

The axial pin 70 is in with its cylindrical shaft the bore 13 of the cam 10 is inserted. The sliding block 50 is in from the open side of the bearing seat 22 inserted this. The intermediate member 20 is of the Bore 13 and thus the cam tip opposite Side of the cam 10 forth with its web 21 in the groove 11 introduced. Here, the sliding stone flag 71 enters Groove 23. The intermediate member 20 is in this position and the cam 10 axially fixed to each other. The thus manufactured unit from intermediate link and cam is on the camshaft is pushed on and the recess of the Sliding block 50 with the radial bore 4 in the camshaft 1 overlapped. The radial pin 40 is through the recess 51 is inserted into the radial bore 4. The pre-assembled eccentric unit with the external eccentric 90, the Inner eccentric 91 and the eccentric gear rings 90A, 91A pushed onto the camshaft and the outer eccentric 90 inserted into the bearing seat of the intermediate member 20. In the inner eccentric 91 covers this end position Part of the radial bore 4 and thus secures the radial pin 40 against emigration.

With reference to Figures 18-20, one will be described below second embodiment explained, which differs from the first embodiment described above only differs in that the groove 11 of the cam 10 in addition an intermediate disk 60 to the web 21 of the intermediate member 20 records that serves the investment area for the Intermediate member 20 in particular in the region of the opening 12 on Enlarge cams 10. The washer 60 is in the essentially ring-shaped and points to the cam tip a flattened area 62, which gives access to the Axial pin 70 provides and acts as an anti-rotation. On the opposite side of the interruption 61 Intermediate disk 60 is provided with an interruption 61, which provides clearance for the sliding block 50.

Fig. 21 shows a third embodiment in which for two cams 10A, 10B, a common inner eccentric 91 is provided. This is on both sides of the An adjusting unit is provided for the camshaft bearing, so that Subsequent insertion of the eccentric is not possible is. For this reason are local to the eccentrics Recesses (not shown) provided around the Radial pin with complete pre-assembly unit made of cams 10A, 10B, the two intermediate links 20 and the eccentrics through the recesses 51 in the respective sliding blocks 50 in the corresponding radial bores 4 of the camshaft 1 to be able to introduce.

Reference list

1

Shaft, camshaft

2nd

Longitudinal bore

3rd

Oil shaft drilling

4th

Radial bore

10, 10A, 10B

Rotating body, cams

11

Groove

12th

opening

13

drilling

14

storage area

15

first sliding guide

16

second sliding guide

17th

web

18th

Middle range

19th

Rotary body oil hole

20th

Pontic

21

web

22

Camp seat

23

Groove

24th

Front wall

25th

concave side wall

26

concave side wall

27

Face

28

Groove

29

Middle range

30th

third sliding guide

40

first transmission element, radial pin

41

paragraph

42

cylindrical section

43

rectangular section

44

Cross-sectional edge

45

Cross-sectional edge

50

Sliding block

51

Recess

52

Side surface

53

Side surface

54

Face

55

Sliding surface

56

Sliding surface

57

shoulder

58

shoulder

59

deepening

60

Washer

61

Interruption

62

Flattening

70

second transmission element, axial pin

71

Sliding flag

90

External eccentric

90A

External eccentric ring gear

90B

nose

90C

Groove

91

Internal eccentric

91A

Internal eccentric ring gear

92

Bearing block

93

Cylinder head

Claims (18)

1. A valve gear mechanism for an internal combustion engine comprising

   a shaft having an axis of rotation (D) and serving to transmit the necessary rotary motion to the valve gear mechanism;

   a rotating body (10) mounted in such a way that it can turn about said shaft (1); and

   an intermediate member (20) surrounding said shaft (1) and being located adjacent to the rotatable rotating body (10) in an axial direction and having a drive connection to said shaft (1) via a first sliding guide (15) and a first transmission element (40, 50) and to said rotating body (10) via a second sliding guide (16) and a second transmission element (70),

   characterized in that at least one transmission element (40, 50) comprises a radial pin (40) disposed substantially vertically with respect to the axis of rotation (D) of said shaft (1).
2. The valve gear mechanism as claimed in claim 1, characterized in that said first transmission element (14) is a radial pin (40) and is slidably received in a recess (51) of said sliding block (50) being pivotably supported in a bearing seat (22) of said intermediate member (20).
3. The valve gear mechanism as claimed in claim 2, characterized in that said radial pin (40) has a cylindrical portion (42) and a substantially rectangular portion (43), said cylindrical portion (42) being inserted in a radial bore (4) of said shaft (1) and said substantially rectangular portion (43) being in sliding engagement with said recess (51) of said sliding block (50).
4. The valve gear mechanism as claimed in claim 3, characterized in that a step (41) is provided between said cylindrical portion (42) and said substantially rectangular portion (43) of said radial pin (40), said step forming together with an element (91) to be shifted onto said shaft (1) a positive locking means against said radial pin (40) creeping out of said radial bore (4).
5. The valve gear mechanism as claimed in claim 3 or 4, characterized in that the diameter of said cylindrical portion (42) is smaller than the larger of both sides (44, 45) of the cross sectional area of said substantially rectangular portion (43).
6. The valve gear mechanism as claimed in any of the proceeding claims, characterized in that said sliding block (50) has the outer conture of a cylinder segment flattened on two sides, wherein both curved side surfaces (52, 53) are outer segments of a cylinder which are connected by a front surface (54).
7. The valve gear mechanism as claimed in claim 6, characterized in that said recess (51) is open at the side of the sliding block (50) opposite to said front surface (54).
8. The valve gear mechanism as claimed in claim 7, characterized in that said sliding block (50) has two sliding surfaces (55, 56) for sliding contact with two opposing surfaces of said rectangular portion (43) of said radial pin (40) and two shoulders (57, 58) for contacting a third surface of said rectangular portion (43) of said radial pin (40).
9. The valve gear mechanism as claimed in claim 8, characterized in that a dimple (59) is formed between said shoulders (57, 58) in order to facilitate mounting of said radial pin (40).
10. The valve gear mechanism as claimed in any of the proceeding claims, characterized in that said bearing seat (22) is open at that side of said intermediate member (20) facing said rotating body (10) and includes two concave side walls (25, 26) having radii of curvature corresponding to those of said side surfaces (52, 53) of said sliding block (50) and an end surface (27) for contacting said front surface (54) of said radial pin (40).
11. The valve gear mechanism according to any of the proceeding claims, characterized in that the axial fixing of said rotating body (10) and said intermediate member (20) on said shaft (1) is effected by said radial pin (40).
12. The valve gear mechanism as claimed in any of the proceeding claims, characterized in that said second transmission element (70) comprises an axial pin (70) parallel to said axis of rotation (D) and rotatably supported in a bore (13) of said rotating body (10).
13. The valve gear mechanism as claimed in claim 12, characterized in that one end of said axial pin (70) is provided with a sliding block lug (71) having two parallel side surfaces which engages a groove (23) of said intermediate member (20), said side surfaces extending in the direction of said groove (23) on one or both sides of said axial pin (70) beyond the circumference thereof so that said axial pin (70) together with said sliding block lug (71) has an L-form or a T-form.
14. The valve gear mechanism as claimed in claims 12 or 13, characterized in that said bore (13) in said rotating body (10) is closed at the end thereof opposite to said intermediate member (20), said shaft (1) has a longitudinal bore (2) and at least one shaft oil bore (3) extending from said longitudinal bore (2) to the outer surface of said shaft (1) and said rotating body (10) has a rotating body oil bore (19) through which oil from said longitudinal bore (2) via said shaft oil bore (3) can reach said bore (13) in a region between the closed end thereof and said axial pin (70), whereby said axial pin (70) is forced into close contact to the end wall (24) of said groove (23).
15. The valve gear mechanism as claimed in any of the proceeding claims, characterized in that said intermediate member (20) is rotatably supported on an outer excenter (90) which is rotatably supported on an excentric circumferential surface of an inner excenter (91) rotatably supported on said shaft (1).
16. The valve gear mechanism as claimed in claim 15, characterized in that two adjacent rotating bodies (10A, 10B) are provided on a common inner excenter (91).
17. The valve gear mechanism as claimed in any of the proceeding claims, characterized in that between said rotating body (10) and said intermediate member (20) there is provided a third sliding guide (30) constituting a support between said rotating body (10) and said intermediate member (20) and, at the same time, allowing a relative movement between said rotating body (10) and said intermediate member (20) in a direction perpendicular to said axis of rotation (D).
18. The valve gear mechanism as claimed in any of the proceeding claims, characterized in that said shaft (1) is a cam shaft and said rotating body (10) is a cam for operating a gas exchange valve.

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