EP2050933A1 - Valve operating system comprising a two-step roller finger follower - Google Patents
Valve operating system comprising a two-step roller finger follower Download PDFInfo
- Publication number
- EP2050933A1 EP2050933A1 EP07118713A EP07118713A EP2050933A1 EP 2050933 A1 EP2050933 A1 EP 2050933A1 EP 07118713 A EP07118713 A EP 07118713A EP 07118713 A EP07118713 A EP 07118713A EP 2050933 A1 EP2050933 A1 EP 2050933A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- lock pin
- actuator
- operating system
- valve operating
- arm
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L1/185—Overhead end-pivot rocking arms
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/18—Rocking arms or levers
- F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
- F01L2001/3443—Solenoid driven oil control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2820/00—Details on specific features characterising valve gear arrangements
- F01L2820/03—Auxiliary actuators
- F01L2820/031—Electromagnets
Definitions
- the present invention generally relates to a valve operating system, especially for use in internal combustion engines where valves are operated with a camshaft.
- the present invention relates to a valve operating system, especially for use in internal combustion engines wherein valves are operated with a camshaft, comprising a rocker arm assembly and a locking system
- the rocker arm assembly comprises a primary arm actuation pivotably mounted around a main pivot axis for actuating a valve and a secondary arm pivotably mounted relative to the primary arm around an auxiliary pivot axis located on the primary arm extremity opposite to the main pivot axis, the secondary arm carrying a cam follower element
- the locking system comprises a lock pin movable between a lock position, wherein it ties the primary arm motion with the secondary arm motion, and an unlock position, wherein it frees the secondary arm motion relative to the primary arm motion in order to allow the secondary arm to swivel relative to the primary arm.
- a valve operating system with two step roller finger follower typically comprises a locking system hydraulically operated with oil circulating inside the primary rocker arm pivot device through a hole connected with the cylindrical hole of the lock pin.
- the lock pin is operated in the lock or the unlock position by controlling the oil pressure.
- This hydraulic actuation has several drawbacks. It is difficult to switch individual followers on a multiple cylinder combustion engine which causes invalid switch events and which prevents from using the system for all types of combustion strategies.
- the operation limits of the valve operating system are determined by the engine oil pressure which is not always the same and which requires oversize of the oil pump, leading to parasitic losses.
- the present invention provides a valve operating system as previously described, characterized in that an outside portion of the lock pin extends at least partly outside the primary arm, in that the locking system comprises an electromechanical actuator cooperating with the outside portion of the lock pin in order to control the axial position of the lock pin, and in that the actuator comprises compensating means allowing lock pin control whatever the angular position of the primary arm is.
- the present invention provides also an internal combustion engine comprising a valve operating system according to the preceding features.
- Figure 1 shows a portion of an internal combustion engine 10 equipped with a valve operating system 14 according to a first embodiment of the invention.
- the combustion engine 10 comprises an engine block 12 on which is rotated a camshaft 16 in order to control a valve train 18. As a simplified representation, only one valve 19 is shown on the figures.
- valve operating system 14 As can be seen on FIG 1 , the camshaft 16 controls the valve train 18 through a valve operating system 14.
- the valve operating system 14 is represented in details on FIG 2 , 3 , 4 and 5 . It comprises a rocker arm assembly 21, pivotably mounted relative to the engine block 12, and a locking system 30 the function of which will be described later.
- the rocker arm assembly 21 comprises a primary arm 22 which extends mainly along a longitudinal direction Ox and which is pivoted on its right end, regarding figure 3 , around a main pivot axis Oy.
- the main pivot axis Oy is constituted by an articulation 27 of the ball-and-socket joint type.
- This articulation 27 is constituted of a semi-spherical hollow 29, machined in the pivoted end of the primary arm 22, and of an oil distributor 31 comprising a semi-spherical convex head.
- Such an articulation type is already disclosed, for example in US 2006/0144356 [ ⁇ 0055].
- the primary arm 22 At its left end (as per FIG 3 ), the primary arm 22 comprises an actuation surface 25 which is in contact with the end 33 of the valve stem 23.
- the primary arm 22 swivels around its main pivot axis Oy between a rest position, which is shown on figure 3 , and an actuation position, which is shown on figure 4 .
- the primary arm 22 is hollow in its central portion in order to house a secondary arm 24 which extends generally along the longitudinal direction of the primary arm 22.
- the secondary arm 24 is pivotably mounted by its left end, as per FIG 3 , relative to the primary arm 22, around an auxiliary pivot axis 28 parallel to the transversal axis Oy and located in the left end of the primary arm 22.
- roller cam follower 26 which freely rotates around its transversal axis and which is maintained in permanent contact with an associated cam 37 carried by the camshaft 16.
- a return spring assembly 35 is arranged between the primary arm 22 and the secondary arm 24 in order to maintain the roller cam follower 26 in contact with the cam 37.
- the secondary arm 24 can swivel around its auxiliary pivot axis 28 between an operating position, which is shown on figures 3 and 4 , and a non operating position, which is shown on figure 5 , upon operation of the camshaft 16, depending on the state of the lock system 30 as it will be seen more clearly later on.
- the lock system 30 comprises a cylindrical lock pin 32, a compression spring 42, and an actuator 44, for example an electro-mechanical actuator.
- the lock pin 32 is slidably mounted, along a sliding axis a1, in a generally longitudinal guiding-hole 40 machined in the right end, as per FIG 3 , of the primary arm 22.
- the guiding-hole 40 is opened inside the hollow portion of the primary arm 22 so that the inside extremity 41 of the lock pin 32 may be received in a locking slot 39 arranged in the right end of the secondary arm 24, as it is shown on figure 3 .
- the outside extremity 43 of the lock pin 32 extends outside the guiding-hole 40, towards the right as shown on figure 3 .
- the lock pin 32 has an inside lock position, wherein it is received in the locking slot 39 and an outside unlock position wherein the lock pin end 41 is not engaged in the locking slot 39.
- the lock pin 32 has two portions 45, 47 of distinct diameters connected via a shoulder 46.
- the guiding-hole 40 has a shoulder surface 49, facing the shoulder 46 so that a spring 42 could be compressed between them biasing the lock pin 32 toward the actuator 44, i.e. toward the right considering figure 3 .
- the spring 42 could be arranged reversely such that the lock pin 32 would be biased toward the hollow portion of the primary arm 22, i.e. toward the left considering figure 3 . Then the default position of the lock pin 32 would be reversed.
- the outside extremity 43 of the lock pin 32 has a semi-spherical convex surface generally centred on a point situated on the lock pin axis a1.
- the actuator 44 comprises a body 51 fixed relative to the engine block 14 and a plunger 53, in the shape of a rod, axially movable along an actuating axis a2.
- the plunger 53 has on its free end a concave spherical surface 55 of larger radius compared to the convex surface of the outside extremity 43 of the lock pin 32.
- the concave surface 55 is such that, when the primary arm 22 is oscillating during operation of the primary arm 22, the tip point of the lock pin convex surface 43 draws, in the plane O-x-z, an arc of circle centred on the main pivot axis Oy.
- the concave surface 55 is of a similar radius as this arc of circle.
- the concave surface 55 is arranged on a cap 56 fixed on the free end of the plunger 53.
- the radius of the concave surface 55 is generally centred on the main pivot axis Oy. The aim of this particular arrangement is to allow the lock pin 32 to remain in contact with the concave surface 55 and to remain constantly operable by the actuator 44.
- the concave surface 55 could be of cylindrical shape instead of spherical shape.
- An advantage of such an embodiment would be to allow controlling of several adjacent lock pins 32 with one single actuator 44 in order to activate/deactivate simultaneously several valves 19.
- the actuator 44 is designed to control the plunger 53 along the actuating axis a2 between an unlock position, which is represented on figure 5 , wherein the plunger 53 is stepped back toward the outside, and a lock position, which is represented on figure 4 , wherein the plunger 53 is stepped forward toward the inside of the primary arm 22.
- the lock pin 32 is pushed outside against the concave surface 55 so that, whatever the actuating position of the plunger 53 is, the lock pin 32 remains in contact with the concave surface 55.
- the concave surface 55 together with the compression spring 42 allow compensation of the different angular positions of the lock pin 32 which depends on the swivelling motion of the primary arm 22.
- the actuator 44 is connected to an electronic control unit 57 which controls the actuator 44 depending on engine parameters or any other relevant parameter.
- valve operating system 14 according to the invention works will be explained in details.
- the primary arm 22 is in its rest position and the actuator 44 is controlled in its lock position so that the lock pin 32 is in its lock position wherein its inside extremity 41 is received in the locking slot 39 of the secondary arm 24 to tie the secondary arm motion with the primary arm motion.
- Swivelling of the primary arm 22 drives the lock pin 32 around the main pivot axis so that the outside portion 43 of the lock pin 32 moves along an arcuate path, considering figure 3 and 4 .
- the lock pin 32 remains in permanent contact with the concave surface 55 the shape of which following the motion of the lock pin 32.
- the lock pin 32 remains in a controllable position.
- the control unit 57 controls the actuator 44 so that the plunger 53 moves from its lock to its unlock position, driving the lock pin 32 to its unlock position.
- This unlock position makes the secondary arm 24 free relative to the primary arm 22.
- the cam 37 pushes the cam follower 26, the secondary arm 24 swivels around the auxiliary pivot axis 28, without transferring motion to the primary arm 22.
- the valve 19 stays in its closed state.
- the actuator 44 is an electro-mechanical actuator wherein the axial position of the plunger 53 is controlled by an electromagnetic coil and wherein the plunger 53 comprises two steady positions (lock and unlock positions) in order to prevent the necessity to power on the actuator 44 to maintain the plunger 53, and by the way the lock pin 32, in one of its extreme axial positions.
- the actuator body 51 contains a coil 58 which is powered through a connector device 60.
- the coil 58 comprises an armature 62 having two opposite radial surfaces 64, 66 and forming, between the two radial surfaces 64, 66, a guiding pipe 70 through which the plunger 53 is slidably mounted.
- the plunger 53 carries two permanent magnet plates 72, 74 which are mounted on each side of the coil 58 and which will be called locking plate 72 and unlocking plate 74.
- Each permanent magnet plate 72, 74 is magnetically orientated along the actuating axis a2 in opposite directions so that, depending on the polarity of the supply current for the coil 58, either the locking plate 72 or the unlocking plate 74 is magnetically attracted towards the coil 58 against the corresponding radial surface 64, 66 of the armature 62.
- the distance D between the two permanent magnet plates 72, 74 is bigger than the longitudinal dimension of the armature 62 so that only one plate 72, 74 could be in contact with the armature 62.
- a current of reverse polarity is supplied to the coil 58 when the actuator 44 is controlled in its unlock position, as can be seen on figure 5 .
- the plunger 53 can be maintained magnetically in each one of its lock and unlock positions without requiring electric power. Supply current is required only for transition state between the lock and unlock positions.
- the actuator 44 comprises two coils 76, 78 and only one permanent magnet plate 80 arranged between the two coils 76, 78.
- the permanent magnet plate 80 is attracted towards one of the two coils 76, 78 which corresponds either to the lock or the unlock position of the plunger 53.
- valve operating system 14 A second embodiment of the valve operating system 14 according to the present invention will be described now, referring to figure 8 and focusing on the main differences with the first embodiment.
- the actuator 44 is an electromagnetic contactless actuator in which the heart plunger 53 is constituted by the outside portion 47 of the lock pin 32.
- the coil 82 of the actuator 44 provides an electromagnetic field which controls the displacement of the heart plunger 53 along the actuation axis a1.
- the diameter of the coil 82 is such that, when the lock pin 32 swivels with the primary arm 22, there is no direct contact between the coil 82 and the lock pin outside portion 47.
- the coil 82 compensates the swivelling of the lock pin 32 during primary arm motion.
- the coil 82 could be of oval section in the direction of the swivelling motion in order to allow a larger swivelling motion of the locking pin 32 while making the actuator 44 more compact in width along a transversal direction.
- the outside portion 47 of the lock pin 32 is long enough so that the coil 82 provides enough electromagnetic force to control the lock pin 32.
- the outside portion 47 of the lock pin 32 is tubular in order to minimize the weight in motion without penalizing the actuating power of the actuator 44.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Valve operating system (14) comprising a rocker arm assembly (21) and a locking system (30), wherein the rocker arm assembly (21) comprises a primary arm (22) pivotably mounted around a main pivot axis (Oy) wherein the locking system (30) comprises a movable lock pin (32), characterized in that an outside portion (47) of the lock pin (32) extends at least partly outside the primary arm (22), in that the locking system (30) comprises an electromechanical actuator (44) cooperating with the outside portion (47) of the lock pin (32), and in that the actuator (44) comprises compensating means (42, 43, 55) for lock pin (32) control.
Description
- The present invention generally relates to a valve operating system, especially for use in internal combustion engines where valves are operated with a camshaft.
- More particularly the present invention relates to a valve operating system, especially for use in internal combustion engines wherein valves are operated with a camshaft, comprising a rocker arm assembly and a locking system, wherein the rocker arm assembly comprises a primary arm actuation pivotably mounted around a main pivot axis for actuating a valve and a secondary arm pivotably mounted relative to the primary arm around an auxiliary pivot axis located on the primary arm extremity opposite to the main pivot axis, the secondary arm carrying a cam follower element, wherein the locking system comprises a lock pin movable between a lock position, wherein it ties the primary arm motion with the secondary arm motion, and an unlock position, wherein it frees the secondary arm motion relative to the primary arm motion in order to allow the secondary arm to swivel relative to the primary arm.
- According to prior art, a valve operating system with two step roller finger follower typically comprises a locking system hydraulically operated with oil circulating inside the primary rocker arm pivot device through a hole connected with the cylindrical hole of the lock pin. The lock pin is operated in the lock or the unlock position by controlling the oil pressure. Such a system is disclosed for example in
US 6,966,291 . - This hydraulic actuation has several drawbacks. It is difficult to switch individual followers on a multiple cylinder combustion engine which causes invalid switch events and which prevents from using the system for all types of combustion strategies.
- Moreover, the operation limits of the valve operating system are determined by the engine oil pressure which is not always the same and which requires oversize of the oil pump, leading to parasitic losses.
- In order to overcome the above mentioned drawbacks, the present invention provides a valve operating system as previously described, characterized in that an outside portion of the lock pin extends at least partly outside the primary arm, in that the locking system comprises an electromechanical actuator cooperating with the outside portion of the lock pin in order to control the axial position of the lock pin, and in that the actuator comprises compensating means allowing lock pin control whatever the angular position of the primary arm is.
- According to other features of the invention:
- the compensating means comprise two curved surfaces, one on the actuating part of the actuator and one on the outside portion of the lock pin, at least one of the curved surfaces being centred generally on the main pivot axis;
- a curved concave surface is arranged on the actuating part of the actuator and is centred generally on the main pivot axis and the outside extremity of the lock pin comprises a curved convex surface in contact with the concave surface;
- at least one curved surface is of semi-spherical shape;
- at least one curved surface is of cylindrical shape;
- the actuator is an electro-mechanical actuator comprising at least a coil and a slidably movable plunger carrying at least one permanent magnet plate cooperating with the coil in order to maintain the plunger in one of its lock and unlock positions;
- the compensating means comprise a coil and a heart plunger made of one piece with the outside portion of the lock pin, the plunger being able to freely swivel inside the coil, and the coil and the plunger constitute the actuator.
- The present invention provides also an internal combustion engine comprising a valve operating system according to the preceding features.
- The present invention is now described by way of example with reference to the accompanying drawings in which:
-
Figure 1 is a partial perspective view showing an engine equipped with a valve operating system according to the present invention; -
Figure 2 is a partial perspective view showing a rocker arm assembly and a locking system included in the valve operating system offigure 1 ; -
Figure 3 is a longitudinal section view showing the valve operating system offigure 1 when the locking system is in its lock position and the rocker arm assembly is not operated; -
Figure 4 is a similar view to the one offigure 3 showing the valve operating system when the locking system is in its lock position and the rocker arm assembly is operated; -
Figure 5 is a similar view to the one offigure 3 showing the valve operating system when the locking system is in its unlock position and the rocker arm assembly is operated; -
Figure 6 is an axial section showing a preferred embodiment of an actuator included in the locking system offigure 1 when the actuator is in its lock position; -
Figure 7 is a similar view to the one offigure 6 showing a second preferred embodiment of the actuator comprising two coils; -
Figure 8 is a similar view to the one offigure 3 showing a second embodiment of the valve operating system according to the present invention and comprising an electromagnetic contactless actuator. -
Figure 1 shows a portion of aninternal combustion engine 10 equipped with avalve operating system 14 according to a first embodiment of the invention. - The
combustion engine 10 comprises anengine block 12 on which is rotated acamshaft 16 in order to control avalve train 18. As a simplified representation, only onevalve 19 is shown on the figures. - As can be seen on
FIG 1 , thecamshaft 16 controls thevalve train 18 through avalve operating system 14. Thevalve operating system 14 is represented in details onFIG 2 ,3 ,4 and 5 . It comprises arocker arm assembly 21, pivotably mounted relative to theengine block 12, and alocking system 30 the function of which will be described later. - The
rocker arm assembly 21 comprises aprimary arm 22 which extends mainly along a longitudinal direction Ox and which is pivoted on its right end, regardingfigure 3 , around a main pivot axis Oy. According to the present embodiment, the main pivot axis Oy is constituted by anarticulation 27 of the ball-and-socket joint type. Thisarticulation 27 is constituted of asemi-spherical hollow 29, machined in the pivoted end of theprimary arm 22, and of anoil distributor 31 comprising a semi-spherical convex head. Such an articulation type is already disclosed, for example inUS 2006/0144356 [§0055]. - In the following description we will use, as a non limiting example, an orthogonal normal direct O-x-y-z coordinate system fixed relative to the
engine block 12 wherein Oy is a transversal axis parallel to thecamshaft 16, and Oz is a generally vertical axis parallel to the axis of thevalve stem 23. - At its left end (as per
FIG 3 ), theprimary arm 22 comprises anactuation surface 25 which is in contact with theend 33 of thevalve stem 23. - Upon operation of the
camshaft 16, theprimary arm 22 swivels around its main pivot axis Oy between a rest position, which is shown onfigure 3 , and an actuation position, which is shown onfigure 4 . - The
primary arm 22 is hollow in its central portion in order to house asecondary arm 24 which extends generally along the longitudinal direction of theprimary arm 22. - The
secondary arm 24 is pivotably mounted by its left end, as perFIG 3 , relative to theprimary arm 22, around anauxiliary pivot axis 28 parallel to the transversal axis Oy and located in the left end of theprimary arm 22. - In the central portion of the
secondary arm 24, there is provided aroller cam follower 26 which freely rotates around its transversal axis and which is maintained in permanent contact with an associatedcam 37 carried by thecamshaft 16. - According to the present embodiment, a
return spring assembly 35 is arranged between theprimary arm 22 and thesecondary arm 24 in order to maintain theroller cam follower 26 in contact with thecam 37. - The
secondary arm 24 can swivel around itsauxiliary pivot axis 28 between an operating position, which is shown onfigures 3 and4 , and a non operating position, which is shown onfigure 5 , upon operation of thecamshaft 16, depending on the state of thelock system 30 as it will be seen more clearly later on. - The
lock system 30 comprises acylindrical lock pin 32, acompression spring 42, and anactuator 44, for example an electro-mechanical actuator. Thelock pin 32 is slidably mounted, along a sliding axis a1, in a generally longitudinal guiding-hole 40 machined in the right end, as perFIG 3 , of theprimary arm 22. The guiding-hole 40 is opened inside the hollow portion of theprimary arm 22 so that theinside extremity 41 of thelock pin 32 may be received in alocking slot 39 arranged in the right end of thesecondary arm 24, as it is shown onfigure 3 . - The
outside extremity 43 of thelock pin 32 extends outside the guiding-hole 40, towards the right as shown onfigure 3 . - With reference to the
primary arm 22, thelock pin 32 has an inside lock position, wherein it is received in thelocking slot 39 and an outside unlock position wherein thelock pin end 41 is not engaged in thelocking slot 39. - The
lock pin 32 has twoportions shoulder 46. The guiding-hole 40 has ashoulder surface 49, facing theshoulder 46 so that aspring 42 could be compressed between them biasing thelock pin 32 toward theactuator 44, i.e. toward the right consideringfigure 3 . - According to an alternative embodiment, the
spring 42 could be arranged reversely such that thelock pin 32 would be biased toward the hollow portion of theprimary arm 22, i.e. toward the left consideringfigure 3 . Then the default position of thelock pin 32 would be reversed. - The
outside extremity 43 of thelock pin 32 has a semi-spherical convex surface generally centred on a point situated on the lock pin axis a1. - The
actuator 44 comprises abody 51 fixed relative to theengine block 14 and aplunger 53, in the shape of a rod, axially movable along an actuating axis a2. Theplunger 53 has on its free end a concavespherical surface 55 of larger radius compared to the convex surface of theoutside extremity 43 of thelock pin 32. - The
concave surface 55 is such that, when theprimary arm 22 is oscillating during operation of theprimary arm 22, the tip point of the lockpin convex surface 43 draws, in the plane O-x-z, an arc of circle centred on the main pivot axis Oy. Theconcave surface 55 is of a similar radius as this arc of circle. - According to the present embodiment, the
concave surface 55 is arranged on acap 56 fixed on the free end of theplunger 53. The radius of theconcave surface 55 is generally centred on the main pivot axis Oy. The aim of this particular arrangement is to allow thelock pin 32 to remain in contact with theconcave surface 55 and to remain constantly operable by theactuator 44. - According to an alternative embodiment, the
concave surface 55 could be of cylindrical shape instead of spherical shape. An advantage of such an embodiment would be to allow controlling of several adjacent lock pins 32 with onesingle actuator 44 in order to activate/deactivate simultaneouslyseveral valves 19. - The
actuator 44 is designed to control theplunger 53 along the actuating axis a2 between an unlock position, which is represented onfigure 5 , wherein theplunger 53 is stepped back toward the outside, and a lock position, which is represented onfigure 4 , wherein theplunger 53 is stepped forward toward the inside of theprimary arm 22. - Thanks to the
compression spring 42, thelock pin 32 is pushed outside against theconcave surface 55 so that, whatever the actuating position of theplunger 53 is, thelock pin 32 remains in contact with theconcave surface 55. - The
concave surface 55 together with thecompression spring 42 allow compensation of the different angular positions of thelock pin 32 which depends on the swivelling motion of theprimary arm 22. - Advantageously, the
actuator 44 is connected to anelectronic control unit 57 which controls theactuator 44 depending on engine parameters or any other relevant parameter. - Now the way the
valve operating system 14 according to the invention works will be explained in details. - Starting from a non operated position of the
valve control system 14, which is represented onfigure 3 , theprimary arm 22 is in its rest position and theactuator 44 is controlled in its lock position so that thelock pin 32 is in its lock position wherein itsinside extremity 41 is received in the lockingslot 39 of thesecondary arm 24 to tie the secondary arm motion with the primary arm motion. - When the
cam 37 comes to push down on thecam follower 26, theprimary arm 22 swivels with thesecondary arm 24 around the main pivot axis Oy and theactuating surface 25 pushes down thevalve 19 to open it. - Swivelling of the
primary arm 22 drives thelock pin 32 around the main pivot axis so that theoutside portion 43 of thelock pin 32 moves along an arcuate path, consideringfigure 3 and4 . During the all swivelling motion, thelock pin 32 remains in permanent contact with theconcave surface 55 the shape of which following the motion of thelock pin 32. As a consequence, whatever the position of theprimary arm 22 is, thelock pin 32 remains in a controllable position. - When it is required to deactivate the
valve 19, thecontrol unit 57 controls theactuator 44 so that theplunger 53 moves from its lock to its unlock position, driving thelock pin 32 to its unlock position. This unlock position makes thesecondary arm 24 free relative to theprimary arm 22. Thus, when thecam 37 pushes thecam follower 26, thesecondary arm 24 swivels around theauxiliary pivot axis 28, without transferring motion to theprimary arm 22. Thevalve 19 stays in its closed state. - Advantageously, the
actuator 44 is an electro-mechanical actuator wherein the axial position of theplunger 53 is controlled by an electromagnetic coil and wherein theplunger 53 comprises two steady positions (lock and unlock positions) in order to prevent the necessity to power on theactuator 44 to maintain theplunger 53, and by the way thelock pin 32, in one of its extreme axial positions. - A preferred embodiment of the
actuator 44 is shown onfigure 6 . Theactuator body 51 contains acoil 58 which is powered through aconnector device 60. Thecoil 58 comprises anarmature 62 having two opposite radial surfaces 64, 66 and forming, between the tworadial surfaces pipe 70 through which theplunger 53 is slidably mounted. - The
plunger 53 carries twopermanent magnet plates coil 58 and which will be called lockingplate 72 and unlockingplate 74. Eachpermanent magnet plate coil 58, either the lockingplate 72 or the unlockingplate 74 is magnetically attracted towards thecoil 58 against the correspondingradial surface armature 62. The distance D between the twopermanent magnet plates armature 62 so that only oneplate armature 62. - When the
actuator 44 is controlled in its lock position, as can be seen onfigure 3 and6 , the current supplied to thecoil 58 is such that the south pole of thecoil 58 is on thelock plate 72 side. Then thelock plate 72, for which the north pole is orientated towards thecoil 58, is attracted towards thecoil 58 which provides a motion of theplunger 53 towards its lock position. - Similarly, a current of reverse polarity is supplied to the
coil 58 when theactuator 44 is controlled in its unlock position, as can be seen onfigure 5 . - Thanks to the
permanent magnet plates plunger 53 can be maintained magnetically in each one of its lock and unlock positions without requiring electric power. Supply current is required only for transition state between the lock and unlock positions. - According to a second preferred embodiment, shown on
figure 7 , theactuator 44 comprises twocoils permanent magnet plate 80 arranged between the twocoils permanent magnet plate 80 is attracted towards one of the twocoils plunger 53. - Thanks to the use of electronically controlled
actuator 44, it is possible to operate individually each lockingsystem 30 which means it is possible to choose exactly which one of thevalve 19 should be deactivated. - A second embodiment of the
valve operating system 14 according to the present invention will be described now, referring tofigure 8 and focusing on the main differences with the first embodiment. - In this second embodiment, the
actuator 44 is an electromagnetic contactless actuator in which theheart plunger 53 is constituted by theoutside portion 47 of thelock pin 32. The coil 82 of theactuator 44 provides an electromagnetic field which controls the displacement of theheart plunger 53 along the actuation axis a1. The diameter of the coil 82 is such that, when thelock pin 32 swivels with theprimary arm 22, there is no direct contact between the coil 82 and the lock pin outsideportion 47. Thus the coil 82 compensates the swivelling of thelock pin 32 during primary arm motion. - The coil 82 could be of oval section in the direction of the swivelling motion in order to allow a larger swivelling motion of the locking
pin 32 while making theactuator 44 more compact in width along a transversal direction. - The
outside portion 47 of thelock pin 32 is long enough so that the coil 82 provides enough electromagnetic force to control thelock pin 32. Advantageously, theoutside portion 47 of thelock pin 32 is tubular in order to minimize the weight in motion without penalizing the actuating power of theactuator 44.
Claims (8)
- A valve operating system (14), especially for use in internal combustion engines (10) wherein valves (19) are operated with a camshaft (16), comprising a rocker arm assembly (21) and a locking system (30), wherein the rocker arm assembly (21) comprises a primary arm (22) actuation pivotably mounted around a main pivot axis (Oy) for actuating a valve (19) and a secondary arm (24) pivotably mounted relative to the primary arm (22) around an auxiliary pivot axis (28) located on the primary arm (22) extremity opposite to the main pivot axis (Oy), the secondary arm (24) carrying a cam follower element (26), wherein the locking system (30) comprises a lock pin (32) movable between a lock position, wherein it ties the primary arm motion with the secondary arm motion, and an unlock position, wherein it frees the secondary arm motion relative to the primary arm motion in order to allow the secondary arm (24) to swivel relative to the primary arm (22), characterized in that an outside portion (47) of the lock pin (32) extends at least partly outside the primary arm (22), in that the locking system (30) comprises an electromechanical actuator (44) cooperating with the outside portion (47) of the lock pin (32) in order to control the axial position of the lock pin (32), and in that the actuator (44) comprises compensating means (42, 43, 55, 82) allowing lock pin (32) control whatever the angular position of the primary arm (22) is.
- . The valve operating system (14) according to claim 1, characterized in that the compensating means comprise two curved surfaces (43, 55), one on the actuating part of the actuator (44) and one on the outside portion (47) of the lock pin (32), at least one of the curved surfaces (43, 55) being centred generally on the main pivot axis (Oy).
- . The valve operating system (14) according to claim 2, characterized in that a curved concave surface (55) is arranged on the actuating part of the actuator (44) and is centred generally on the main pivot axis (Oy) and in that the outside extremity (43) of the lock pin (32) comprises a curved convex surface (43) in contact with the concave surface (55).
- . The valve operating system (14) according to claim 2 or 3, characterized in that at least one curved surface (43, 55) is of semi-spherical shape.
- . The valve operating system (14) according to anyone of claims 1 to 4, characterized in that at least one curved surface (43, 55) is of cylindrical shape.
- . The valve operating system (14) according to anyone of claims 1 to 5, characterized in that the actuator (44) is an electro-mechanical actuator comprising at least a coil (58, 76, 78) and a slidably movable plunger (53) carrying at least one permanent magnet plate (72, 74, 80) cooperating with the coil (58, 76, 78) in order to maintain the plunger (53) in one of its lock and unlock positions.
- . The valve operating system (14) according to claim 1, characterized in that the compensating means comprise a coil (82) and a heart plunger (53) made of one piece with the outside portion (47) of the lock pin (32), the plunger (53) being able to freely swivel inside the coil (82), and in that the coil (82) and the plunger (53) constitute the actuator (44).
- . Internal combustion engine (10) comprising a valve operating system (14) according to anyone of the preceding claims.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07118713A EP2050933A1 (en) | 2007-10-17 | 2007-10-17 | Valve operating system comprising a two-step roller finger follower |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07118713A EP2050933A1 (en) | 2007-10-17 | 2007-10-17 | Valve operating system comprising a two-step roller finger follower |
Publications (1)
Publication Number | Publication Date |
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EP2050933A1 true EP2050933A1 (en) | 2009-04-22 |
Family
ID=39161088
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP07118713A Withdrawn EP2050933A1 (en) | 2007-10-17 | 2007-10-17 | Valve operating system comprising a two-step roller finger follower |
Country Status (1)
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EP (1) | EP2050933A1 (en) |
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