DE102015009010A1 - Nockenmitnehmersystem - Google Patents

Abstract

One embodiment of the invention provides a cam follower system (500) comprising: - a body (130) having a cam follower receiving opening (132) defining a sliding axis (A), and - a cam follower (505) supporting a ram (50) 510), wherein an axial portion (550) of the plunger (510) is axially slidably inserted into an axial portion (1320) of the cam follower receiving aperture (132), the axial portion (550) of the plunger and the axial portion (1320 ) of the receiving opening have a mating non-circular cross section, so that they form a sliding joint.

Description

TECHNICAL AREA

The present disclosure relates generally to an internal combustion engine, such as an internal combustion engine of a motor vehicle. In particular, the present disclosure relates to a cam follower system that is used in an internal combustion engine such. As a diesel engine or a gasoline engine is used in a fuel injection pump.

BACKGROUND

It is known that an internal combustion engine, such as. As a diesel engine or a gasoline engine, generally having a cylinder block defining at least one cylinder which receives a piston having a coupling, with which the crankshaft is rotated. The cylinder is closed by a cylinder head which cooperates with the piston to define a combustion chamber into which an air / fuel mixture is periodically introduced and ignited, resulting in hot expanding combustion gases whose expansion causes reciprocation of the combustion engine Pistons and thus leads to the rotation of the crankshaft of the engine.

The fuel is provided by at least one fuel injector, which may be located directly in the combustion chamber and receives the fuel from a fuel pipe communicating through a fuel pump with a fuel tank.

The piston of the fuel pump is conventionally actuated by a cam, for example a cam of a camshaft synchronized with the crankshaft of the engine, which is rotatably connected to at least one element selected from the engine block and the cylinder head.

In particular, the free end of the piston of the fuel pump is coupled to a Nockenmitnehmer having a cylindrical plunger and a roller which is rotatably mounted on the plunger and adapted to be pressed by a spring against the cam of the camshaft, so that the Rotation of the camshaft leads to a periodic displacement of the piston of the fuel pump.

The plunger slides into a cylindrical plunger receiving opening provided in at least one member selected from the engine block and the cylinder head.

In order to prevent a rotational or tilting movement of the Nockenmitnehmers and in particular of the plunger in the plunger receiving opening, the motor is provided with a rotation.

The anti-rotation device generally comprises a pin or nose which is attached to the plunger receiving opening, projects radially into the cavity in the interior of the receiving opening and is adapted to slide positively in an axial seat provided on the plunger shirt.

Alternatively, the pin or nose may protrude radially from the plunger shirt and positively slide in an axial seat provided in the plunger receiving opening.

However, the pin or nose is generally a component that is small and therefore difficult to mount in the plunger receiving opening and is also difficult to handle and store before and during the assembly phase of the internal combustion engine.

Moreover, during operation of the internal combustion engine, the pin or nose is subject to wear, resulting in an increase in the radial clearance between the pin or nose and the plunger seat.

As a result, during operation of the internal combustion engine due to the relative rotational movements between the plunger seat and the pin or the nose and due to the collisions between these components to a noise by tilting.

Another disadvantage of the known anti-rotation device is that during operation of the internal combustion engine, an unforeseeable, accidental breakage of the pin or the nose can occur, whereby the broken components (the pin or the nose or parts thereof) no longer rotate the ram stop and beyond that may cause the cam profile is damaged by pitting.

SUMMARY

In view of the above, one purpose of an embodiment of the present invention is to obviate or at least significantly mitigate the above disadvantages. Another purpose is to achieve this goal with a simple, rational and relatively inexpensive solution. These and other objects are achieved by the embodiments of the invention as defined in the independent claims. The dependent claims define preferred or particularly advantageous aspects of embodiments of the invention.

• – einen Körper, der eine Nockenmitnehmer-Aufnahmeöffnung aufweist, die eine Gleitachse definiert, und
• – einen Nockenmitnehmer, der einen Stößel umfasst, wobei ein axialer Abschnitt des Stößels in einen axialen Abschnitt der Nockenmitnehmer-Aufnahmeöffnung axial gleitend eingefügt wird, wobei der axiale Abschnitt des Stößels und der axiale Abschnitt der Aufnahmeöffnung einen zusammenpassenden nicht kreisförmigen Querschnitt aufweisen, so dass sie ein Schubgelenk bilden.

An embodiment of the invention provides, in particular, a cam follower system comprising:

• A body having a cam follower receiving opening defining a sliding axis, and
• A cam follower comprising a plunger, wherein an axial portion of the plunger is axially slidably inserted into an axial portion of the cam follower receiving aperture, wherein the axial portion of the plunger and the axial portion of the receiving aperture have a mating non-circular cross-section such that they form a sliding joint.

Thanks to this solution, the cam follower can self-align when inserted into the cam follower receiving opening provided in the cylinder head or engine block, allowing a correct and rapid connection between the cam follower and the cam, with the follower and cam follower receiving opening simultaneously a non-rotating configuration, which allows efficient sliding translational movement of the plunger of the cam follower along the sliding axis of the cam follower receiving opening.

In practice, the mutual translation connection between the cam follower plunger and the cam follower receiving aperture, which is possible only in a single translational movement degree of freedom, prevents the occurrence of noise by tilting during operation of the internal combustion engine, and at the same time, the cam is prevented from damage. d. H. Pitting corrosion, protected.

According to one embodiment of the invention, the axial portion of the plunger has at least two outer opposed curved sliding surfaces.

According to one aspect of this embodiment, the curved sliding surfaces comprise symmetrical semi-cylindrical surfaces.

This aspect of the invention provides a reciprocal translational connection between the plunger and the cam follower receiving opening that is quieter and more robust than known connections between the cam follower and the cam follower receiving aperture, thereby reducing overall noise and increasing the life of the internal combustion engine with the cam follower system ,

According to another aspect of the invention, the distance between the centers of the semi-cylindrical surfaces is between 0.5 mm and 2 mm.

This aspect of the invention provides a very simple, reliable and cost-effective solution for providing a non-circular outer contour of the cross-section of the axial portion of the plunger, while maintaining the same sliding properties as in a known cylindrical cam follower plunger.

According to a further aspect of the invention, the axial portion of the plunger has an elongated outer cross-section.

Thanks to this solution, the non-circular outer contour of the cross-section of the axial portion of the plunger on a very simple, reliable and cost-effective construction, which allows a non-rotatable and self-centering connection with a corresponding Nockenmitnehmer-receiving opening.

According to a first alternative of the invention, the axial portion of the plunger has an oval outer cross-section.

This aspect of the invention provides a simpler method of manufacturing the cam follower tappet.

In this case, the axial portion of the plunger also has two mutually facing opposite planar surfaces which connect the mutually facing ends of the two opposite semi-cylindrical surfaces with each other.

Thanks to this solution, the non-circular outer contour of the cross section of the axial portion of the plunger on a symmetrical, non-rotating and self-centering structure, which causes good sliding of the cam follower plunger when inserted into a corresponding cam follower receiving opening.

According to a second alternative of the invention, the axial portion of the plunger has an octagonal outer cross-section.

In other words, the axial portion of the plunger also has two opposing opposed "V" shaped surfaces connecting respective facing ends of two opposed semi-cylindrical surfaces.

This solution reduces the abutting surfaces of the plunger and the receiving opening when the cam follower plunger is slidably inserted into an oval cam follower receiving opening, which reduces the mutual friction.

Moreover, in the aft-shaped structure, only a reduced total contact surface of the plunger, ie, only the portion of the extended distal curved surfaces intended to come into contact with the opposed surfaces of the bore of the cam follower receiving opening, must be subjected to fine grinding.

According to another aspect of the invention, the cam follower comprises a roller which is rotatably mounted on the plunger and is intended to press against the cam.

In other words, the cam follower is a driver element with a roller.

Thanks to this solution, the wear and noise of the connection between cam and cam follower are further reduced.

In the example, the roller has an axis of rotation with a predefined fixed orientation with respect to the longitudinal axis of the elongated outer cross section, in which example the axis of rotation of the roller is parallel to the longitudinal axis of the elongated outer cross section.

In other words, therefore, the fixed orientation imparted to the cam follower ram by the sliding joint with respect to the cam follower receiving aperture fixes the orientation of the axis of rotation of the roller so that it is parallel to the axis of rotation of the cam.

According to another aspect of the invention, the axial portion of the receiving opening has at least two inner opposing curved sliding surfaces.

This aspect of the invention, as disclosed above, provides a reciprocal translational connection between the plunger and the cam follower receiving opening that is quieter and more robust than known connections between the cam follower and the cam follower receiving opening, thereby reducing overall noise and engine life is increased with the cam follower system.

According to one aspect of the invention, the curved sliding surfaces comprise facing semi-cylindrical surfaces, and the axial portion of the receiving opening comprises two opposing opposing planar surfaces connecting each other to the facing ends of the two opposed semi-cylindrical surfaces.

This aspect of the invention provides a simpler method of manufacturing the cam follower receiving aperture; In addition, the non-circular inner bore of the axial portion of the receiving opening has a symmetrical structure, which cooperates with the non-rotating and self-centering structure of the plunger, in particular both with the oval structure of the plunger and with the aft-shaped structure of the plunger, resulting in good lubricity the cam follower tappet when inserted into a bisymmetrical oval cam follower receiving opening result.

According to a further aspect of the invention, the axial portion of the receiving opening comprises an elongated inner cross-section.

Thanks to this solution, the non-circular inner contour of the cross-section of the axial portion of the receiving opening to a very simple, reliable and cost-effective structure, which is adapted to be coupled with a correspondingly constructed anti-rotation and self-centering plunger

In the example, the longitudinal axis of the elongate inner cross section of the cam follower receiving aperture has a predefined fixed orientation with respect to the axis of rotation of the cam, in the example the longitudinal axis of the elongated cross section of the receiving aperture being parallel to the axis of rotation of the cam.

In other words, the fixed alignment between the cam follower tappet and the cam follower receiving opening provided by the thrust joint sequentially fixes the orientation of the axis of rotation of the roller with respect to the axis of rotation of the cam so that they are parallel to each other.

According to one aspect of the invention, the axial portion of the receiving opening has an oval inner cross-section.

This aspect of the invention provides a simpler method of manufacturing the cam follower receiving aperture; In addition, the non-circular inner bore of the axial portion of the receiving opening has a symmetrical structure, which cooperates with the non-rotating and self-centering structure of the plunger, in particular both with the oval structure of the plunger and with the aft-shaped structure of the plunger, resulting in good lubricity of the cam follower tappet when inserted into the bisymmetrical oval cam follower receiving opening result.

According to another aspect of the invention, at least the two inner opposed curved sliding surfaces of the cam follower receiving opening are ground.

Thanks to this solution, the ground distal curved surfaces, which are intended to come into contact with the sliding surfaces of the cam follower, ensure a good sliding ability, which reduces the mutual friction and the wear of the sliding components.

According to another aspect of the invention, the body comprising the cam follower receiving opening is selected from the following components: the cylinder head and the engine block.

The invention may also be embodied as an internal combustion engine provided with the cam follower system described above.

BRIEF DESCRIPTION OF THE DRAWINGS

Now, the present invention will be described by way of example with reference to the accompanying drawings.

1 schematically shows a motor vehicle system.

2 is the cross section AA of 1 ,

3 Fig. 10 is a partially sectioned schematic view of an internal combustion engine showing the fuel pump, the cam follower and the cam follower receiving port.

4 is an enlarged detail view of 3 ,

5 is a partially sectioned schematic view of a first embodiment of the cam follower, seen from the direction shown in FIG 3 with the arrow B is displayed.

6 is a schematic plan view of the positive connection between the cam follower and the cam follower receiving opening of 5 ,

7 FIG. 15 is a perspective and exploded schematic view of the cam follower and the cam follower receiving opening according to the first embodiment. FIG.

8th is a partially sectioned schematic view of a second embodiment of the cam follower, seen from the direction shown in FIG 3 with the arrow B is displayed.

9 is a schematic plan view of the positive connection between the cam follower and the cam follower receiving opening of 8th ,

10 FIG. 15 is a perspective and exploded schematic view of the cam follower and the cam follower receiving opening according to the second embodiment. FIG.

PRECISE DESCRIPTION

Some embodiments may be a motor vehicle system 100 include that in the 1 and 2 is shown and that an internal combustion engine (ICE) 110 , For example, a diesel engine or a gasoline engine has.

The ICE 110 includes a crankshaft 145 in a crankcase 118 is housed and rotatably supported by this. Above the crankcase 118 includes the ICE 110 also a cylinder block 119 , the at least one cylinder 125 with a piston 140 defined, which has a coupling with which the crankshaft 145 is turned. In the present example, the cylinder block 119 and the crankcase 118 formed as separate bodies, which are fastened to each other by suitable means. In other embodiments, however, it may be provided that the cylinder block 119 and the crankcase 118 are formed as a single body, which is commonly referred to as an engine block and by the reference numeral 120 can be marked. The ICE 110 further comprises a cylinder head 130 that is above the cylinder block 119 is arranged and with the piston 140 works together to create a combustion chamber 150 define. An air / fuel mixture (not shown) is introduced into the combustion chamber 150 introduced and ignited, resulting in hot expanding combustion gases, leading to a reciprocation of the piston 140 to lead.

The fuel is from at least one fuel injector 160 provided the fuel under high pressure from a fuel pipe 170 receives. The fuel pipe 170 is fluid supply with a high pressure fuel pump 180 connected to the pressure of a fuel source or a tank 190 increased fuel.

Each of the cylinders 125 has at least one inlet 210 and an outlet 220 on, in the cylinder head 130 are formed. The inlet (inlets) 210 is (are) provided to air in the combustion chamber 150 to carry while the outlets 220 are provided to the exhaust gases from the combustion chamber 150 eject. In other embodiments, each cylinder 125 more than an inlet 210 and / or more than one outlet 220 exhibit.

The air can be the air inlets 210 via an intake manifold 200 be supplied. An air inlet pipe 205 leads the intake manifold 200 Ambient air too. In other embodiments, a throttle 330 be selected to control the air flow to the intake manifold 200 to regulate. In other embodiments, a compressed air system such as a turbocharger is used 230 with a compressor 240 that is together with a turbine 250 turns, used. The rotation of the compressor 240 increases the pressure and the temperature of the air in the pipe 205 and the intake manifold 200 , One in the lead 205 containing intercooler 260 can reduce the temperature of the air. The turbine 250 turns when flowing from an exhaust manifold 225 coming exhaust gases, the exhaust gas from the outlet 220 passes through a series of vanes before passing through the turbine 250 is expanded. The exhaust gases leave the turbine 250 and become an exhaust system 270 guided. This example shows a variable geometry turbine (VGT) with a VGT actuator 290 configured to move the vanes to cause the vanes to flow the exhaust gas through the turbine 250 to change. In other embodiments, the turbocharger 230 have a fixed geometry and / or have a wastegate.

The exhaust system 270 can be an exhaust pipe 275 comprising one or more exhaust aftertreatment devices 280 Has. Aftertreatment devices can be any devices with which the composition of the exhaust gases can be changed. Some examples of aftertreatment devices 280 include, but are not limited to, catalytic (two- and three-way) converters, oxidation catalysts, lean NOx traps, hydrocarbon adsorbers, selective catalytic reduction (SCR) systems, and particulate filters. Other embodiments include an exhaust gas recirculation (EGR) system. 300 that with the exhaust manifold 225 and the intake manifold 200 connected is. The EGR system 300 can be an EGR cooler 310 exhibit the temperature of the exhaust gases in the EGR system 300 to reduce. An EGR valve 320 regulates the flow of exhaust gases in the EGR system 300 ,

The motor vehicle system 100 can still use an electronic control unit (ECM) 450 configured to receive signals from or to various, with the ICE 110 connected sensors and / or devices to send or receive. The ECM 450 It can receive input signals from various sensors designed to generate the signals proportional to various physical parameters associated with the ICE 110 are. The sensors include, but are not limited to, an air mass flow and temperature sensor 340 , a pressure and temperature sensor 350 for the manifold, a sensor 360 for the pressure in the combustion chamber, sensors 380 for the coolant and oil temperature and / or the associated fill level, a pressure sensor 400 for the fuel, a camshaft position sensor 410 , a crankshaft position sensor 420 , Sensors 430 for the pressure and the temperature of the exhaust gases, an EGR temperature sensor 440 as well as a position sensor 445 for the gas pedal. Furthermore, the ECU 450 to output various signals to control the operation of the ICE 110 to control, for example, but not exclusively, to the fuel injectors 160 , to the throttle 330 , to the EGR valve 320 , to the VGT actuator 290 and to the camshaft adjusting system. It should be noted that dashed lines are used to indicate various connections between the various sensors, devices and the ECM 450 but others have been omitted for purposes of clarity.

What the ICE 110 concerns, so is in each inlet 210 an inlet valve 215 containing, selectively, air from the inlet 210 in the combustion chamber 150 lets in ( 2 ). Similarly, in every outlet 220 an outlet valve 222 containing, alternately, the outlet of the exhaust gases through the outlet 220 allowed. The intake valves 215 and the exhaust valve 222 be through one or more camshafts 135 operated, coinciding with the crankshaft 145 rotates. Each of these camshafts 135 is located above the cylinder head 130 so they are commonly referred to as overhead camshafts. In particular, the camshaft (s) may (may) 135 directly in the cylinder head 130 be arranged and rotatably supported by this. In other embodiments, the camshaft (s) may (may) be 135 alternatively, in one above the cylinder head 130 arranged ladder frame or cam carrier be arranged and rotatably supported by this. In some examples, the camshaft (s) may directly in the engine block 120 , in particular in the cylinder block 119 be arranged and rotatably supported by this.

The fuel pump 180 is provided by a cam follower system 500 one of which is a cam follower 505 included in a cam follower receiving opening 132 can slide.

The fuel pump 180 includes a pump housing 181 and is with a reciprocating piston 182 provided from the pump housing 181 projects.

The pump housing 181 is at least one element selected from the cylinder head 130 and the engine block 120 , attached.

In the present example, the pump housing 181 on the cylinder head 130 attached.

The piston 182 is in an opening 131 arranged in the cylinder head 130 (or in the engine block 120 ), wherein it is oriented to be operative with a cam follower 505 of the cam follower system 500 communicated.

The camshaft 135 includes a cam 136 that by the cam follower 505 in operative contact with the fuel pump 180 is.

At least one element selected from the cylinder head 130 and the engine block 120 (In the present example, the cylinder head 130 ) includes the cam follower receiving opening 132 between the opening 131 and the cam 136 is arranged so that the cam follower 505 when in the cam follower receiving opening 132 is arranged between the cam 136 and the piston 182 the fuel pump is arranged.

The cam follower receiving opening 132 is in the direction of the cam 136 axially on the opening 131 aligned.

A feather 183 is between the pump housing 181 and a collar 184 arranged on the piston 182 is formed or attached thereto, and normally pushes the piston 182 outwards into an advanced position.

The cam follower 505 is in the cam follower receiving opening 132 inserted and includes one of the fuel pump 180 facing end and a cam 136 facing opposite end.

The collar 184 is at the pump end of the cam follower 505 formed or is pressed against it anyway.

When a force on the cam follower 505 is exercised, whether by the cam 136 located at the cam end of the cam follower 505 turns, or by the spring 183 applying a force to the pump end of the cam follower 505 exerts, the cam follower slides 505 into the cam follower receiving opening 132 ,

The cam follower 505 is a driver element with a roller, wherein the cam follower 505 in particular a plunger 510 and a role 515 includes that rotatable on the plunger 510 is arranged and intended to be against the cam 136 to press.

The pestle 510 has the shape of a dome with the axis A. In particular, the plunger points 510 a peripheral wall 520 on which limits a housing in which the roll 515 partially housed. The role 515 protrudes axially from the open end of the plunger and defines the cam end of the cam follower 505 ,

The peripheral wall 520 is at an upper end by an upper radial wall 525 closed, which is a top 530 which has an axially upward concave shape in this example.

The top 530 defines the pump end of the cam follower 505 , The piston 182 the fuel pump 180 is against the top 530 of the plunger 510 pressed.

A wave 535 with the geometric axis C is used to the role 515 at the lower open end of the plunger 510 to fix. The geometric axis C is perpendicular to the axis A of the plunger 510 , The ends of the shaft 535 are for example by frictional insertion in holes or through holes 540 fastened in the peripheral wall 520 are formed opposite each other. The wave 535 Of course, by any other suitable means on the plunger 510 be attached. In the illustrated exemplary embodiment, the through-holes are 540 overall of cylindrical shape.

The peripheral surface of the roll 515 Remains from the bore of the plunger 510 spaced, so that contact between these two elements is prevented.

To the friction torque and the wear between the shaft 535 and the role 515 Limit is a variety of cylindrical needles 545 next to each other between the outer surface of the shaft 535 and the hole of the roll 515 arranged. Alternatively, it would also be feasible to drill the roller 515 with the outer surface of the shaft 535 got in contact.

An axial section 550 of the plunger 510 , in particular the radially widest axial section 550 the peripheral wall 520 of the plunger 510 , Has a cross section (according to a plane perpendicular to the axis A of the plunger 510 ), which has a continuous, non-circular outer contour.

In particular, the axial section 550 of the plunger on an elongated outer cross section.

In all examples shown, the plunger 510 an axially constant elongate outer cross section. Alternatively, it is possible that the plunger 510 an axially variable elongated outer cross section, wherein the axial portion 550 of the plunger from the portion of the peripheral wall 520 is defined, which has the radially largest outer cross-section.

The elongated outer cross section of the axial section 550 of the plunger has a longitudinal axis which is parallel to the geometric axis C, ie the axis of rotation of the roller 515 is.

In the examples, the axial section comprises 550 the plunger at least two outer opposite curved and convex surfaces, which are designed in the cam follower receiving opening 132 to glide.

In particular, the surfaces are semi-cylindrical surfaces 555 ,

In the examples, the distance between the centers of the semi-cylindrical surfaces 555 of the plunger between 0.5 mm and 2 mm, preferably 1 mm.

In a first embodiment of the invention, which in 5 - 7 is shown, the axial section 550 of the plunger on an oval outer cross section.

In this embodiment, the outer peripheral wall 520 of the plunger 510 that the axial section 550 of the plunger defined by the two facing symmetrical semi-cylindrical surfaces 555 of the plunger and by two opposite plane surfaces 560 of the plunger, each of which defines the facing ends of the two opposed semi-cylindrical surfaces 555 connect the plunger together.

In a second and alternative embodiment of the invention, which in 8th - 10 is shown, the axial section 550 of the plunger on a figure-eight-shaped outer cross-section.

In this embodiment, the outer peripheral wall 520 of the plunger 510 that the axial section 550 of the plunger defined by the two facing symmetrical semi-cylindrical surfaces 555 of the plunger and by two opposite concave "V" shaped surfaces 565 defining, respectively, the facing ends of the two opposed semi-cylindrical surfaces 555 connect the plunger together.

The cam follower receiving opening 132 is a through hole and defines a linear sliding axis which coincides with the axis A when the cam follower 505 in the cam follower receiving opening 132 is arranged.

At least the axial section 550 the ram is designed to be positive and sliding in at least one positive axial section 1320 the cam follower receiving opening 132 to be inserted.

The axial section 1320 the receiving opening, in the example of the radially narrowest axial portion of the bore of the cam follower receiving opening 132 that the (axial section 550 the plunger of the) cam follower (s) 505 includes, has a cross section (according to a plane perpendicular to the axis of the cam follower receiving opening 132 ), which has a continuous non-circular inner contour.

In particular, the bore of the axial section 1320 the receiving opening has an elongated inner cross-section.

In all examples shown, the cam follower receiving opening 1320 an axially constant elongated inner cross section. Alternatively, it is possible for the cam follower receiving opening 132 an axially variable elongated inner cross section, wherein the axial section 1320 the receiving opening from the portion of the bore of the cam follower receiving opening 132 is defined with the radially narrowest inner cross section of the axial section 550 of the ram during operation of the ICE 110 includes. In the examples, the elongate inner cross section of the axial section 1320 the receiving opening has a longitudinal axis which is parallel to the axis of rotation D of the cam 136 , in particular parallel to the axis of rotation of the camshaft 135 , is.

According to these examples, the axial section 550 of the plunger in only a few possible orientations (in the examples, in two orientations angularly spaced 180 degrees apart) in the axial section 1320 the receiving opening are arranged, but with a correct orientation of the role 515 of the Nockenmitnehmers is possible, in which the geometric axis C parallel to the axis of rotation D of the cam 136 is.

From the above, it is apparent that the plunger 510 of the cam follower 505 only in the cam follower receiving opening 132 can be inserted when the axial section 550 the plunger axially on the axial portion 1320 aligned with the receiving opening and radially has the same orientation as this. The positive connection between the axial section 550 the plunger and the axial section 1320 the receiving opening defines a thrust joint, which is the reciprocal rotation between the plunger 510 and the cam follower receiving opening 132 prevented and therefore the plunger 510 only one degree of freedom in the translational movement in the cam follower receiving opening 132 leaves.

Due to the positive, non-rotating connection between the shaped, non-circular outer cross section of the axial section 550 the plunger with the correspondingly shaped, non-circular inner cross section of the axial section 1320 the receiving opening is the plunger 510 Able to insert itself into the cam follower receiving opening 132 to align yourself.

In the examples, the axial section 1320 at least two inner opposing curved and concave surfaces adapted to slide with the outer opposed curved and convex surfaces of the axial section 550 to connect the plunger. In particular, the curved surfaces are semi-cylindrical surfaces 1321 ,

In the examples, the distance between the centers of the semi-cylindrical surfaces 1321 the receiving opening between 0.5 mm and 2 mm, preferably 1 mm.

In the two embodiments of the invention, which in 5 - 7 respectively. 8th - 10 are shown, the axial section 1320 the receiving opening on an oval inner cross section.

The oval inner cross section of the bore of the axial section 1320 the receiving opening preferably has the same shape as the entire outer cross section of the axial section 550 of the plunger and is sized so that the axial section 550 of the plunger with reduced clearance in the axial section 1320 the receiving opening can be inserted.

In this embodiment, the inner bore of the axial section 1320 the receiving opening through the two symmetrical semi-cylindrical surfaces 1321 the receiving opening and by two opposite flat surfaces 1322 formed the receiving opening, each of the facing ends of the two opposite semi-cylindrical surfaces 1321 connect the receiving opening with each other.

In the first embodiment of the invention, which in 5 - 7 is shown, the entire bore of the axial section 1320 the receiving opening are ground to the kinetic friction between the in contact, moving surfaces (which are the semi-cylindrical surfaces 1321 the receiving opening and the flat surfaces 1322 the receiving opening is in sliding contact with the semi-cylindrical surfaces 555 the plunger or the flat surfaces 560 of the plunger).

In the example, also the entire peripheral wall 520 of the axial section 550 the plunger be ground

In the second embodiment of the invention, which in 8th - 10 is shown, it is possible that only the semi-cylindrical receiving opening surfaces 1321 the bore of the axial section 1320 the receiving opening are ground to the kinetic friction between the contacting, moving surfaces (which are the semi-cylindrical surfaces 1321 the receiving opening is in sliding contact with the semi-cylindrical surfaces 555 the plunger are located), the plan surfaces 1322 the receiving opening is not in contact with the "V" shaped surfaces 565 of the axial section 550 of the plunger are.

In the example, also the semi-cylindrical surfaces 555 the plunger be ground.

The cam follower 505 in the context of its use in a fuel injection pump 180 for an ICE 110 can be used in other applications, for example in a rocker arm system, which is intended to actuate the valves of a combustion piston engine. When the cam follower is used in a rocker arm system for operating the valves of an internal combustion engine, a push rod cooperating with a rocker pushes against the top 530 of the plunger 510 ,

From the above, it is apparent that the plunger 510 of the cam follower 505 when inserted into the cam follower receiving opening 132 aligns itself, whereby a noiseless, robust sliding connection of the two elements with a low coefficient of friction is possible.

This makes it possible to simplify the assembly of the engine components.

In the foregoing summary and detailed description, at least one exemplary embodiment has been presented; however, it should be noted that there are a large number of modification options. It should also be noted that the exemplary embodiment or exemplary embodiments are only examples and are not intended to limit the scope, applicability, or construction in any way whatsoever. Rather, the foregoing summary and detailed description will provide those skilled in the art with a practical guide to implementing at least one example embodiment, it being understood that various changes may be made in the functions and arrangements of the elements described with reference to an exemplary embodiment without departing from the spirit of the invention Scope of protection as defined in the appended claims and their legal equivalents.

LIST OF REFERENCE NUMBERS

100

Automotive system

110

internal combustion engine

118

crankcase

119

cylinder block

120

block

125

cylinder

130

cylinder head

131

opening

132

Cam-receiving opening

1320

axial portion of the receiving opening

1321

semi-cylindrical surfaces of the receiving opening

1322

plane surfaces of the receiving opening

135

camshaft

136

cam

140

piston

145

crankshaft

150

combustion chamber

160

fuel injector

170

Fuel pipe

180

Fuel pump

181

pump housing

182

piston

183

feather

184

collar

190

Fuel source

200

intake manifold

205

Air inlet line

210

inlet

215

intake valves

220

outlet

222

outlet valve

225

exhaust manifold

230

turbocharger

240

compressor

250

turbine

260

Intercooler

270

exhaust system

275

exhaust pipe

280

aftertreatment devices

290

VGT actuator

300

Exhaust gas recirculation system (EGR)

310

EGR cooler

320

EGR valve

330

throttle

340

Mass flow and temperature sensor for the air

350

Sensor for manifold pressure and temperature

360

Combustion pressure sensor

380

Sensors for coolant and oil temperature and the associated level

400

Fuel rail pressure sensor

410

Camshaft position sensor

420

Crankshaft position sensor

430

Sensors for pressure and temperature of the exhaust gases

440

EGR temperature sensor

445

Accelerator position sensor

450

electronic control unit (ECM)

500

Nockenmitnehmersystem

505

cam

510

tappet

515

role

520

peripheral wall

525

radial wall

530

top

535

wave

540

Through openings

545

needles

550

axial portion of the plunger

555

semi-cylindrical surfaces of the plunger

560

plane surfaces of the plunger

565

"V" shaped surfaces

A

Axis of the plunger

C

geometric axis

D

Rotary axis of the cam

Claims (15)

Cam follower system ( 500 ), comprising: - a body ( 130 ) having a cam follower receiving opening ( 132 ), which defines a sliding axis (A), and - a cam follower ( 505 ), which has a pestle ( 510 ), wherein an axial section ( 550 ) of the plunger ( 510 ) in an axial section ( 1320 ) of the cam follower receiving opening ( 132 ) is slidably inserted axially, wherein the axial section ( 550 ) of the plunger and the axial section ( 1320 ) of the receiving opening have a mating non-circular cross-section, so that they form a sliding joint. Cam follower system ( 500 ) according to claim 1, wherein the axial section ( 550 ) of the plunger at least two outer opposing curved sliding surfaces ( 555 ) having. Cam follower system ( 500 ) according to claim 2, wherein the sliding surfaces symmetrical semi-cylindrical surfaces ( 555 ) are. Cam follower system ( 500 ) according to one of the preceding claims, wherein the axial section ( 550 ) of the plunger has an elongate outer cross-section. Cam follower system ( 500 ) according to one of the preceding claims, wherein the axial section ( 550 ) of the plunger has an oval outer cross-section. Cam follower system ( 500 ) according to claim 5, wherein the axial portion of the plunger has two facing opposite planar surfaces ( 560 ), each having the mutually facing ends of the two opposite semi-cylindrical surfaces ( 555 ) connect with each other. Cam follower system ( 500 ) according to claim 4, wherein the axial section ( 550 ) of the plunger has an octagonal outer cross-section. Cam follower system ( 500 ) according to any one of the preceding claims, wherein the cam follower ( 505 ) a role ( 515 ) rotatably mounted on the plunger ( 510 ) and is intended to bear against a cam ( 136 ). Cam follower system ( 500 ) according to claim 1, wherein the axial section ( 1320 ) of the receiving opening at least two inner opposing curved sliding surfaces ( 1321 ) having. Cam follower system ( 500 ) according to claim 9, wherein the sliding surfaces facing each other semi-cylindrical surfaces ( 1321 ) and wherein the axial section ( 1320 ) of the receiving opening two mutually facing opposite flat surfaces ( 1322 ), each having the mutually facing ends of the two opposite semi-cylindrical surfaces ( 1321 ) connect with each other. Cam follower system ( 500 ) according to one of the preceding claims 9 to 10, wherein the axial section ( 1320 ) of the receiving opening has an elongate inner cross-section. Cam follower system ( 500 ) according to claim 11, wherein the axial section ( 1320 ) of the receiving opening has an oval inner cross-section. Cam follower system ( 500 ) according to one of the preceding claims 9 to 12, wherein at least the two inner opposing curved sliding surfaces ( 1321 ) are ground. Cam follower system ( 500 ) according to one of the preceding claims, wherein the body is selected from the following components: from the cylinder head ( 130 ) and the engine block ( 120 ). Internal combustion engine ( 110 ) equipped with a cam follower system ( 500 ) is equipped according to one of the preceding claims.

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