WO2018195370A1 - Système d'actionnement de soupape de levée de soupape variable ayant un ou plusieurs anneaux de commande de mouvement - Google Patents

Système d'actionnement de soupape de levée de soupape variable ayant un ou plusieurs anneaux de commande de mouvement Download PDF

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Publication number
WO2018195370A1
WO2018195370A1 PCT/US2018/028467 US2018028467W WO2018195370A1 WO 2018195370 A1 WO2018195370 A1 WO 2018195370A1 US 2018028467 W US2018028467 W US 2018028467W WO 2018195370 A1 WO2018195370 A1 WO 2018195370A1
Authority
WO
WIPO (PCT)
Prior art keywords
cam
operating system
valve operating
motion control
recess
Prior art date
Application number
PCT/US2018/028467
Other languages
English (en)
Inventor
Dale N. SMITH
Mark M. Wigsten
Original Assignee
Borgwarner Inc.
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Borgwarner Inc. filed Critical Borgwarner Inc.
Publication of WO2018195370A1 publication Critical patent/WO2018195370A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/08—Shape of cams
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L2013/0052—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 with cams provided on an axially slidable sleeve

Definitions

  • the present disclosure relates to a variable valve lift valve operating system having one of more motion control rings.
  • a valve operating system having variable valve lift capabilities can include a rotary shaft onto which several sets of cam members are non- rotatably but axially slideably mounted.
  • Each of the cam members can have two or more different sets of cam lobes that can be selectively and alternately employed to control the opening and closing of a set of valves.
  • the cam members can be slid along the cam tube to position a particular set of the cam lobes at a location where they can actively participate in the opening and closing of the set of valves.
  • the present teachings provide a valve operating system that includes a cam tube, a cam member, and a motion control ring.
  • the cam tube is rotatable about an axis.
  • the cam member is axially slidably but non-rotatably mounted on the cam tube and movable along the axis between a first cam position and a second cam position.
  • the cam member has a plurality of distinct and different cam configurations.
  • the cam tube defines a first recess.
  • the cam member defines an internal, circumferentially extending groove into which the motion control ring is received.
  • the motion control ring is received in the first recess and frictionally engages the cam tube to resist movement of the cam member along the axis relative to the cam tube.
  • Figure 1 is a perspective view of a portion of an internal combustion engine having a valve operating system constructed in accordance with the teachings of the present disclosure
  • Figure 2 is an exploded perspective view of the valve operating system of Figure 1 ;
  • Figure 3 is an exploded perspective view of a portion of the valve operating system of Figure 1 illustrating a cam tube and a plurality of cam assemblies in more detail;
  • Figure 4 is an exploded perspective view of a portion of one of the cam assemblies;
  • Figure 5 is a schematic illustration of a portion of a cam member of one of the cam assemblies that depicts a portion of the cam member as having first and second cam configurations;
  • Figure 6 is similar to that of Figure 5, but also depicts a difference in the phasing of the first and second cam configurations;
  • Figure 7 is a longitudinal section view of a portion of the valve operating system of Figure 1 illustrating a motion control ring disposed in a cam member and engaged to an engagement surface formed on the cam tube;
  • Figure 8 is a longitudinal section view similar to that of Figure 7 but depicting a motion control ring disposed in a cam member and engaged to a first alternately configured engagement surface on a cam tube;
  • Figures 9 and 10 are longitudinal section views of the portion of the valve operating system of Figure 1 depicting the cam assemblies in first and second positions, respectively;
  • Figure 1 1 is a longitudinal section view similar to that of Figure 7 but depicting a motion control ring disposed in a cam member and engaged to a second alternately configured engagement surface on a cam tube;
  • Figure 12 is a perspective, partly exploded view of a portion of an exemplary valve operating system that incorporates the second alternately configured engagement surface on the cam tube that is depicted in Figure 1 1 ;
  • Figure 13 is a longitudinal section view similar to that of Figure 7 but depicting a motion control ring disposed in a cam member and engaged to a second alternately configured engagement surface on a cam tube.
  • valve operating system 10 constructed in accordance with the teachings of the present disclosure.
  • valve operating system 10 can be generally similar to that which is described in commonly assigned International Patent Application No. PCT/US2016/060244 filed November 3, 2016, the disclosure of which is incorporated by reference as if fully set forth in detail herein.
  • the internal combustion engine in the particular example illustrated is a four cylinder overhead cam engine with an in-line cylinder configuration, but it will be appreciated that the teachings of the present disclosure have application to other engine configurations and as such, it will be understood that the scope of the present disclosure is not limited to engines with an overhead cam engines or to engines with an in-line cylinder configuration.
  • the engine can include a cylinder head CH and a drive means DM for providing rotary power to drive the valve operating system 10, such as a cam gear, cam sprocket or cam pulley. Except as otherwise noted herein, the cylinder head CH and drive means DM can be configured in a well-known and conventional manner.
  • the valve operating system 10 can include a cam tube 12, a plurality of cam assemblies 14 and an actuator 16.
  • the cam tube 12 can be coupled to the drive means DM to receive rotary power therefrom.
  • the cam tube 12 is fixedly and non-rotatably coupled to the drive means DM, but it will be appreciated that a variable coupling could be employed to couple the cam tube 12 to the drive means DM to selectively alter the rotational position of the cam tube 12 relative to the drive means DM within a predetermined range to provide the valve operating system 10 with variable valve timing capabilities.
  • the cam tube 12 can have a hollow interior 20 and can define a plurality of cam member mounts 22 and a plurality of journals 24.
  • the journals 24 can be received in a cam bore CB that can be formed between the cylinder head CH and a plurality of cam caps CC that are fixedly but removably coupled to the cylinder head CH.
  • a plurality of bearings (not specifically shown) can be disposed between the journals 24 and the cylinder head CH and the cam caps CC so that the cam tube 12 is supported relative to the cylinder head CH for rotation about a rotary axis 28.
  • each of the cam assemblies 14 can include a control link 30, one or more cam members 32 and one or more motion control rings 34.
  • the control links 30 can have a link body 36 and one or more engagement members 38.
  • the link body 36 can form a majority of the control link 30 and can extend within the hollow interior 20 of the cam tube 12 along the rotary axis 28 (i.e., parallel to the rotary axis 28).
  • Each of the engagement members 38 can be coupled to the link body 36 for translation with the link body 36 along the rotary axis 28 and can extend radially outwardly from the link body 36.
  • a first one of the engagement members 38a is formed of a component that is assembled to the link body 36 and secured together with a suitable coupling means, such as a weld and/or fasteners, while a second one of the engagement members 38b is unitarily and integrally formed with the link body 36 (e.g., as a hook or projection that extends perpendicular to the link body 36).
  • a suitable coupling means such as a weld and/or fasteners
  • a second one of the engagement members 38b is unitarily and integrally formed with the link body 36 (e.g., as a hook or projection that extends perpendicular to the link body 36).
  • all of the engagement members 38 could be discrete components that are assembled and secured to the link body 36 or that all of the engagement members 38 could be unitarily and integrally formed with the link body 36, for example through bending, cold heading or forging.
  • Each of the cam members 32 can be axially slidably but non- rotatably coupled to the cam tube 12.
  • each of the cam members 32 has an internally splined or toothed aperture 40 and is received over the cam tube 12 such that the internal teeth of the internally splined aperture 40 meshingly engage corresponding external teeth formed on the cam member mounts 22 on the cam tube 12.
  • Each of the cam members 32 can have a first cam configuration 50 and a second cam configuration 52 that are employed on an alternate basis to open a set of valves (not shown).
  • the set of valves may comprise solely one or more intake valves, or may comprise solely one or more exhaust valves, or may comprise both one or more intake valves and one or more exhaust valves.
  • the first cam configuration 50 can have a first predetermined lift profile
  • the second cam configuration 52 can have a second predetermined lift profile that is different from the first predetermined lift profile.
  • the first predetermined lift profile could include one or more first cam lobes 56 that are configured to provide a first maximum lift value L1 (i.e., the maximum radius of the first cam lobe 56 minus the radius R of the base circle BC of the first cam lobe 56), while the second predetermined lift profile could include one or more second cam lobes 58 that are configured to provide a second maximum lift value L2 that is different from the first maximum lift value L1 .
  • first and second cam configurations 50 and 52 are configured to open a set of valves that comprises both one or more intake valves and one or more exhaust valves, it will be appreciated that the first and second cam lobes 56 and 58 (Fig.
  • first and second cam configurations 50 and 52 will additionally include one or more other cam lobes (not shown) that are configured to open the other type of valves (i.e., exhaust valves or intake valves) that are not opened by the first and second cam lobes 56 and 58 (Fig. 5).
  • first cam lobes 56 of the first predetermined lift profile could be timed (i.e., oriented about the rotary axis) differently from the second cam lobes 58 of the second predetermined lift profile as shown in Figure 6 and as represented by the angle A.
  • each of the cam members 32 of a given one of the cam assemblies 14 can be coupled to the control link 30 of the given one of the cam assemblies 14 for axial movement with the control link 30 along the rotary axis 28.
  • each of the engagement members 38 of the control links 30 are received through respective slotted apertures 60 (best shown in Fig. 3) formed in the cam tube 12 and are received into (and optionally through) respective apertures 62 formed in a respective one of the cam members 32.
  • Each of the cam assemblies 14 is slide-able along the rotary axis 28 between a first position (Fig. 9), in which the first cam configurations 50 are positioned in associated activated locations 70 and each of the second cam configurations 52 is offset along the rotary axis 28 from their associated activated location 70, and a second position (Fig. 10), in which the second cam configurations 52 are positioned in the associated activated locations 70 and each of the first cam configurations 50 is offset along the rotary axis 28 from their associated activated location 70.
  • each of the motion control rings 34 is received between an associated one of the cam members 32 and the cam tube 12 and is configured to generate friction forces that not only resist movement of the associated one of the cam members 32 relative to the cam tube 12, but also which increases as the associated one of the cam assemblies 14 is moved between the first and second positions.
  • Each of the motion control rings 34 is formed of a spring-wire material which can be formed of a wire having a desired cross-sectional shape, such as a round wire, a square wire or a rectangular wire.
  • each motion control ring 34 is received into a circumferentially extending groove 100, which intersects the internally splined aperture 40, that is formed into an associated one of the cam members 32 and slidingly engages a corresponding engagement surface 102 that is formed on the cam tube 12. It will be appreciated, however, that in the alternative, the motion control ring 34 could be received in circumferentially extending groove (not shown) formed in the cam tube 12 and could slidingly engage a corresponding engagement surface (not shown) that is formed on the associated cam member 32.
  • the engagement surface 102 can define a plurality of recesses 104 and a connector 106.
  • Each of the recesses 104 can define a seat 1 10 and one or more transition surfaces 1 12 that can be contoured in an appropriate manner between the seat 1 10 and an adjacent one of the connectors 106.
  • Each of the transition surfaces 1 12 is tapered (i.e., frusto- conical) in the example provided, but it will be appreciated that each of the transition surfaces could be defined by one or more radii or combinations or one or more radii and one or more tapered segments.
  • each of the cam assemblies 14 is movable between first and second positions and as such, each engagement surface 102 has a single connector 106 that spans between a pair of the recesses 104. As such, each of the recesses 104 defines a single transition surface 1 12. It will be appreciated, however, that in situations where the cam assemblies 14 are movable into three or more positions, at least one of the recesses 104 can define a pair of transition surfaces 1 12 as is shown in Figure 8.
  • each of the motion control rings 34 can be received into an associated one of the circumferentially extending grooves 100 formed into the cam members 32 and in an associated one of the seats 1 10 that are formed in the cam tube 12.
  • the motion control rings 34 are formed to a diameter that is somewhat smaller than that of the seats 1 10 so that each of the motion control rings 34 generates a radially-inwardly directed force that is exerted onto the surface of an associated seat 1 10.
  • Axial movement of the motion control rings 34 along the cam tube 12 from an associated seat 1 10 to an associated transition surface 1 12 causes the motion control rings 34 to expand in diameter (so that the axial ends of the wire that forms the motion control rings 34 further separate from one another in a circumferential direction).
  • the actuator 16 can be selectively operated to translate the cam members 32 along the rotary axis 28 to locate a desired one of the cam configurations 50, 52 on each of the cam members 32 at an associated activated location 70 so that the desired cam configurations 50, 52 on each of the cam members 32 is employed to open corresponding sets of valves.
  • the friction forces that are generated by the motion control rings 34 increase as the motion control rings 34 travel from an associated seat 1 10 to an associated connector 106. Further movement of the cam assemblies 14 toward their targeted positions causes the motion control rings 34 to move down the transition surfaces 1 12 that are on opposite side of the connectors 106 and into seats 1 10 that are associated with the placement of the cam assemblies 14 into their targeted positions.
  • the friction forces produced as the motion control rings 34 are moved up one transition surface 1 12, over an associated one of the connectors 106 and down another of the transition surfaces 1 12 can help to decelerate the cam assemblies 14 as they are moved between the first and second positions.
  • the engagement surface 102 has been illustrated and described as including a plurality of recesses 104 that have a seat 1 10 and one or more transition surfaces 1 12 that are disposed adjacent to the seat 1 10, it will be appreciated that the engagement surface 102 can be constructed somewhat differently.
  • the engagement surface 102' can be formed with a pair of recesses 104' and a connector 106'.
  • each of the recesses 104' consists of only a seat 1 10' and the connector 106' directly connects to each of the seats 1 10'.
  • the connector 106' is tangent to the seat 1 10'.
  • a detent mechanism can optionally be employed with each cam assembly 14' and the cam tube 12'.
  • An exemplary detent mechanism is depicted as having a pair of first detent recesses 150 (only one shown), a pair of second detent recesses 152 (only one shown), a pair of detent balls 154 and a band spring 156.
  • the pairs of first and second detent recesses 150 and 152 are formed into the cam tube 12' on opposite sides.
  • each of the first detent recesses 150 is disposed 180 degrees apart from the other first detent recess 150
  • each of the second detent recesses 152 is disposed 180 degrees apart from the other second detent recess 152.
  • Each of the detent balls 154 is disposed in an associated hole 160 (only one shown) that is formed in a cam member 32a'.
  • the band spring 156 is disposed about the cam member 32a' and biases the detent balls 154 radially inwardly toward the cam tube 12'. It will be appreciated that the detent balls 154 can engage one of the detent recesses 150, 152 when one of the cam configurations 50, 52 on the cam member 32a' is disposed in an associated activated location 70 (Fig. 9).
  • Figure 13 is generally similar to that of Figure 1 1 , except that the circumferentially extending groove 100" for holding the motion control ring 34 that is formed into the cam member 32" can include one or more wedging surfaces 170.
  • Each wedging surface 170 is configured to exert a force onto the motion control ring 34 that drives the motion control ring 34 into the seat 1 10' of the recess 104' in the engagement surface 102'. Configuration in this manner may help to prevent the cam member 32" from driving the motion control ring 34 out of the seat 1 10' and over-traveling.
  • the example provided has but a single wedging surface 170 that is configured to drive the motion control ring 34 into a single one of the seats 1 10' (i.e., the seat 1 10' shown in the right side of the figure), but it will be appreciated that a second wedging surface (not shown) could be incorporated into an opposite side of the circumferentially extending groove 100" that would be configured to drive the motion control ring 34 into the other one of the seats 1 10' (i.e., the seat 1 10' shown on the left side of the figure).
  • another one of the cam members could be configured with a circumferentially extending groove having another motion control ring received therein (for engaging a corresponding engagement surface) and the circumferentially extending groove could have a similar wedging surface that is disposed on an opposite side of the circumferentially extending groove than which is shown here. Accordingly, the wedging surface on a first one of the cam members can prevent over-travel of the cam members relative to the cam tube 12 in a first direction, while the wedging surface on a second one of the cam members can prevent over-travel of the cam members relative to the cam tube 12 in a second direction that is opposite the first direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un système d'actionnement de soupape qui comprend un tube de came, un élément de came et un anneau de commande de mouvement. Le tube de came peut tourner autour d'un axe. L'élément de came est monté de manière axialement coulissante mais non rotatif sur le tube de came et mobile le long de l'axe entre une première position de came et une seconde position de came. L'élément de came a une pluralité de configurations de came distinctes et différentes. Le tube à came définit un premier évidement. L'élément de came définit une rainure interne qui s'étend de manière circonférentielle et dans laquelle l'anneau de commande de mouvement est reçu. L'anneau de commande de mouvement est reçu dans le premier évidement et vient en prise par frottement avec le tube de came pour résister au mouvement de l'élément de came le long du tube de came.
PCT/US2018/028467 2017-04-20 2018-04-20 Système d'actionnement de soupape de levée de soupape variable ayant un ou plusieurs anneaux de commande de mouvement WO2018195370A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201762487554P 2017-04-20 2017-04-20
US62/487,554 2017-04-20

Publications (1)

Publication Number Publication Date
WO2018195370A1 true WO2018195370A1 (fr) 2018-10-25

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022034104A1 (fr) * 2020-08-12 2022-02-17 thyssenkrupp Presta Ilsenburg GmbH Système de came coulissant
WO2022034101A1 (fr) * 2020-08-12 2022-02-17 thyssenkrupp Presta Ilsenburg GmbH Système de came coulissant pour un moteur à combustion interne, comprenant un élément de verrouillage intégré

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020094894A1 (en) * 2000-10-13 2002-07-18 Christian Poiret Tensioner for a chain or belt
JP2007262957A (ja) * 2006-03-28 2007-10-11 Toyota Motor Corp 可変動弁仲介機構
US20120073530A1 (en) * 2010-09-24 2012-03-29 Schaeffler Technologies Gmbh & Co. Kg Arrangement for coupling two components of an internal combustion engine arranged movable relative to each other
US20130104824A1 (en) * 2010-06-25 2013-05-02 Neumayer Tekfor Holding Gmbh Adjustable Camshaft
KR20160057768A (ko) * 2014-11-14 2016-05-24 현대자동차주식회사 다단 가변 밸브 리프트 장치

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020094894A1 (en) * 2000-10-13 2002-07-18 Christian Poiret Tensioner for a chain or belt
JP2007262957A (ja) * 2006-03-28 2007-10-11 Toyota Motor Corp 可変動弁仲介機構
US20130104824A1 (en) * 2010-06-25 2013-05-02 Neumayer Tekfor Holding Gmbh Adjustable Camshaft
US20120073530A1 (en) * 2010-09-24 2012-03-29 Schaeffler Technologies Gmbh & Co. Kg Arrangement for coupling two components of an internal combustion engine arranged movable relative to each other
KR20160057768A (ko) * 2014-11-14 2016-05-24 현대자동차주식회사 다단 가변 밸브 리프트 장치

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022034104A1 (fr) * 2020-08-12 2022-02-17 thyssenkrupp Presta Ilsenburg GmbH Système de came coulissant
WO2022034101A1 (fr) * 2020-08-12 2022-02-17 thyssenkrupp Presta Ilsenburg GmbH Système de came coulissant pour un moteur à combustion interne, comprenant un élément de verrouillage intégré

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