WO2006095532A1 - 弁開閉時期制御装置 - Google Patents
弁開閉時期制御装置 Download PDFInfo
- Publication number
- WO2006095532A1 WO2006095532A1 PCT/JP2006/302325 JP2006302325W WO2006095532A1 WO 2006095532 A1 WO2006095532 A1 WO 2006095532A1 JP 2006302325 W JP2006302325 W JP 2006302325W WO 2006095532 A1 WO2006095532 A1 WO 2006095532A1
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- WO
- WIPO (PCT)
- Prior art keywords
- driven
- axial
- axial direction
- camshaft
- end side
- Prior art date
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
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
-
- 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
- F01L1/022—Chain drive
-
- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
-
- 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
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34473—Lock movement perpendicular to camshaft axis
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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
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34483—Phaser return springs
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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
- F01L2303/00—Manufacturing of components used in valve arrangements
- F01L2303/01—Tools for producing, mounting or adjusting, e.g. some part of the distribution
Definitions
- the present invention relates to a drive-side rotation member that rotates in synchronization with a crankshaft of an internal combustion engine, a driven-side rotation member coaxially disposed on the drive-side rotation member, and one end side of the driven-side rotation member in the axial direction. And an interference member which penetrates from the other end side in the axial direction and is fastened to the camshaft of the internal combustion engine at the other axial end side of the driven side rotating member to fix the driven side rotating member to the camshaft.
- the present invention relates to a valve timing control device.
- An internal combustion engine such as an automobile engine may be provided with a valve timing control device for controlling the timing of opening and closing of the intake valve and the exhaust valve in accordance with the operating state.
- the valve opening / closing timing control device is generally attached to one end of a camshaft.
- auxiliary equipment such as a vacuum pump and a fuel pump can also be attached as a driven device driven by an internal combustion engine. These may be attached to one end of a camshaft to reduce the overall height of the internal combustion engine. .
- Patent Document 1 discloses a structure for connecting a drive shaft of a driven device such as a fuel pump to one end of a camshaft of an internal combustion engine.
- a substantially cylindrical pump-side coupling is attached by nut to the end of the drive shaft located substantially at the center of the fuel pump.
- a coupling member constituting an Oldham coupling is interposed as an intermediate member between the flange portion at one end of the cam shaft and the pump side coupling, and the cam shaft disposed substantially in series is connected to the drive shaft Power transmission to the vehicle.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2001-263025 (page 3, FIG. 1-3)
- an outer rotor 105 has a sprocket 154 formed on its outer periphery, and rotates in synchronization with a crankshaft (not shown) via a timing chain 121 wound around the sprocket 154.
- the inner rotor 104 is coaxially installed on the outer rotor 105 and fixed to the end of the camshaft 103 by the bolt 107, and the outer rotor 105 is on the side opposite to the side on which the camshaft 103 is disposed.
- an engagement groove 181 engageable with the joint member 191 on the driven device 109 side is formed on the surface of the cover plate 152
- the driven device 109 may be rotationally driven by the rotation of the external rotor 105 of the open / close timing control device 101.
- the entire cover plate 152 needs to be formed of a material with high wear resistance such as iron or sintered metal. Therefore, there is a problem that the weight of the valve timing control device 101 becomes heavy and the inertia becomes large.
- the cover plate 152 is exclusively designed for connecting the driven device 109. Therefore, it can not be used for the valve timing control device 101 to which the driven device 109 is not attached, and there is a problem that the versatility is low and the cost is high.
- the present invention has been made in view of the above problems, and an object thereof is to provide a driven device at one end of a camshaft while suppressing an increase in the overall length of the internal combustion engine in the axial direction of the camshaft. It is an object of the present invention to provide a valve timing control device capable of mounting both of the valve timing control devices and capable of being versatile and capable of suppressing an increase in weight.
- the characterizing feature of the valve timing control device is a drive side rotation member that rotates in synchronization with a crankshaft of an internal combustion engine, and a coaxial arrangement of the drive side rotation member.
- the driven side rotation member and the axial direction one end side of the driven side rotation member are penetrated from the one end side to the other side in the axial direction, and the other side of the driven side rotation member in the axial direction
- An engagement means having a mating groove is integrally provided at one axial end of the fastening member.
- the driven device can be attached to one end side in the axial direction of the valve timing control device via the engagement means. Therefore, it is possible to attach both the valve timing control device and the driven device to one end of the camshaft while suppressing an increase in the overall length of the internal combustion engine in the axial direction of the camshaft.
- the engaging means having the engaging groove is integrally provided at one axial end portion of the fastening member, if only the fastening member is made of a material having high wear resistance, the material is made of a material. It is enough. Therefore, since a lightweight material can be used for the driving side rotation member, the valve opening / closing timing control device can be made lightweight, and the inertia can be reduced.
- valve timing control device for mounting the driven device uses a fastening member provided with the above-mentioned engaging means, and the valve timing control device for mounting the driven device does not have a usual fastening member. By using it, most parts of the valve timing control device except the fastening member can be made common. Therefore, the versatility can be enhanced and the cost can be reduced.
- the engagement means is a base formed at one axial end of the fastening member and arranged at one axial end side with respect to the drive side rotation member, and one axial end side of the base It is preferable to have a configuration having an engaging groove formed along a straight line intersecting with the rotation axis.
- the engagement means having the engagement groove can be integrally provided at one axial end of the fastening member.
- valve opening / closing timing control device includes a drive side rotation member that rotates in synchronization with a clamper shaft of an internal combustion engine, and a driven side rotation member coaxially arranged on the drive side rotation member. And penetrating from one end side in the axial direction of the driven side rotation member to the other end side in the axial direction, and fastening the driven side rotation member to the camshaft of the internal combustion engine at the other end side in the axial direction of the driven side rotation member.
- An engagement means disposed on one end side in the axial direction with respect to the rolling member and having an engagement groove for attaching the driven device is nipped between the axial one end portion of the fastening member and the driven side rotation means. The point is.
- the driven device can be attached to one end side in the axial direction of the valve timing control device via the engagement means. Therefore, it is possible to attach both the valve timing control device and the driven device to one end of the camshaft while suppressing an increase in the overall length of the internal combustion engine in the axial direction of the camshaft.
- the engaging means having the engaging groove is held between the one end in the axial direction of the fastening member and the driven side rotating means, only the members constituting the engaging means are made wear resistant. It is sufficient if it is made of high-grade material. Therefore, since the drive side rotation member can be made of a lightweight material, the valve timing control device can be made lightweight, and the inertia can be reduced.
- valve opening / closing timing control device to which the driven device is attached is attached with the above-mentioned engagement means, and the valve opening / closing timing control device without the driven device attachment is not attached with the above-mentioned engagement means.
- Most parts of the timing control device can be made common. Therefore, the versatility can be enhanced and the cost can be reduced.
- the engagement means may be a base disposed on one end side in the axial direction with respect to the drive side rotation member, and a straight line intersecting the rotation axis at the axial one end side face of the base.
- the engaging groove formed, the fitting portion fitted on the inner periphery of the through hole of the fastening member formed on the driven side rotating member, and the radially formed inner side of the fitting portion It is preferable to have a configuration having a through hole of a fastening member.
- the engagement means may constitute a part of an Oldham joint provided between the engagement device and the driven device.
- FIG. 1 is a longitudinal sectional view of a valve timing control device 1 according to the present embodiment.
- FIG. 2 is a front view of the valve timing control device 1 according to the present embodiment.
- FIG. 3 is a sectional view taken along the line A-A of FIG.
- the valve timing control device 1 includes an external rotor 5 as a drive side rotation member that rotates in synchronization with a crank shaft (not shown) of the engine 2 as an internal combustion engine. And an inner rotor 4 as a driven side rotation member disposed coaxially and fixed to the camshaft 3.
- the internal rotor 4 is integrally fixed to an end of a camshaft 3 which constitutes a rotary shaft of a cam that controls the opening and closing of an intake valve or an exhaust valve of the engine 2.
- a camshaft 3 which constitutes a rotary shaft of a cam that controls the opening and closing of an intake valve or an exhaust valve of the engine 2.
- a fitting recess 41 as a fitting portion formed on the other end side in the axial direction of the inner rotor 4 and a fitting portion formed on an end portion of the cam shaft 3
- a fastening member 7 described later.
- a fitting recess 41 as a fitting portion is formed on the other axial end side of the inner rotor 4, and on the axial one end side of the inner rotor 4, a fixing member 7 can be penetrated for fixation. Holes 42 are formed.
- a fitting convex portion 31 as a fitting portion to be fitted to the fitting concave portion 41 of the inner rotor 4 and a step shape with respect to the fitting convex portion 31.
- a contact surface 33 formed on the rear surface.
- an internal thread portion 34 to which the fastening member 7 can be screwed is formed at an axial center portion of the camshaft 3. Then, the surface 43 on the other axial end side of the inner rotor 4 is brought into contact with the contact surface 33 of the cam shaft 3, and the fastening member 41 is fitted with the fitting recess 41 on the fitting protrusion 31.
- the male screw portion 71 of 7 is screwed into the female screw portion 34 of the camshaft 3. By this, the inner rotor 4 is fixed to the end of the camshaft 3.
- the outer rotor 5 is mounted so as to be rotatable relative to the inner rotor 4 within a predetermined relative rotational phase range. Then, the cam shaft 3 is connected to the surface on the other end side in the axial direction. A plate 51 is attached, and a cover plate 52 is attached to the surface at one end in the axial direction opposite to the other end in the axial direction to which the camshaft 3 is connected.
- the cover plate 52 is provided with a female screw portion into which a bolt 53 as a fastening member is screwed.
- the cover plate 52 and the rear plate 51 are integrated with the outer rotor 5 by screwing through the bolt 53 force and the outer rotor 5 and screwing to the female screw portion provided on the cover plate 52.
- the rear plate 51 and the force bar plate 52 are formed between the inner rotor 4 and the outer rotor 5 and close the opening of the fluid pressure chamber 61 which will be described later.
- a timing sprocket 54 is physically provided on the outer periphery of the outer rotor 5.
- a timing chain 21 is bridged between the timing sprocket 54 of the external rotor 5 and a crank sprocket attached to the crankshaft of the engine 2.
- the external rotor 5 is connected to the crankshaft of the engine 2 so as to rotate in synchronization. That is, when the crankshaft of the engine 2 is rotationally driven, rotational power is transmitted to the timing sprocket 54 through the timing chain 21.
- the outer rotor 5 is rotationally driven along the rotational direction S shown in FIG. 3, and further, the inner rotor 4 is rotationally driven along the rotational direction S to rotate the camshaft 3.
- a cam provided on the camshaft 3 pushes down the intake valve or exhaust valve of the engine 2 to open it.
- a torsion spring 64 is provided between the inner rotor 4 and the cover plate 52 fixed to the outer rotor 5. Both end portions of the torsion spring 64 are a rotor side spring holding portion formed as a circular recessed groove on the surface 45 on one end side in the axial direction of the inner rotor 4, and a side of the cover plate 52 facing the inner rotor 4. It is each fixed to the cover side spring holding
- the torque spring 64 applies a torque to normally bias the inner rotor 4 and the outer rotor 5 in the direction in which the relative rotational phase is displaced in the advance direction S1.
- the outer rotor 5 is provided with a plurality of projections 55 functioning as a radially inwardly projecting shoe, spaced apart from one another along the rotational direction.
- a fluid pressure chamber 61 defined by the outer rotor 5 and the inner rotor 4 is formed between the adjacent projections 55 of the outer rotor 5. In the illustrated example, five fluid pressure chambers 61 are provided.
- Vane grooves 44 a are formed in the outer peripheral portion of the inner rotor 4 at locations facing the fluid pressure chambers 61.
- vanes 44 which divide the fluid pressure chamber 61 into an advancing chamber 61a and a retarding chamber 61b in the relative rotational direction (directions of arrows S1 and S2 in FIG. 3), extend in the radial direction. It is slidably inserted along.
- the vane 44 is biased radially outward by a spring 44b provided on the inner diameter side thereof.
- the advancing chamber 61 a of the fluid pressure chamber 61 is in communication with the advancing passage 62 a formed in the inner rotor 4, and the retarding chamber 61 b is connected in communication with the retarding passage 62 b formed in the inner rotor 4.
- the advance passage 62a and the retard passage 62b are connected to a hydraulic circuit (not shown). Then, the hydraulic oil pumped up by the oil pump driven by the engine 2 or the like is supplied or discharged to one or both of the advancing chamber 61a and the retarding chamber 61b through the control valve.
- the relative rotational phase (hereinafter, also simply referred to as “relative rotational phase”) between the inner rotor 4 and the outer rotor 5 is set to the advance direction S1 (the direction in which the vane 44 changes to the arrow S1 side in FIG. 3) or A retarding direction S2 (a direction in which the vanes 44 change to the arrow S2 side in FIG. 3) is displaced or an urging force is generated which holds the phase at an arbitrary phase.
- the lock mechanism 63 includes a lock member 63 a provided so as to be able to project radially inward from the outer rotor 5 and a concave lock chamber 63 b provided on the outer periphery of the inner rotor 4. There is.
- the lock chamber 63b communicates with a lock passage 62c formed in the inner rotor 4, and the lock passage 62c is connected to a hydraulic circuit (not shown).
- the lock member 63a is guided by a guide groove 56 provided in the outer rotor 5 and It is provided slidably in the radial direction of 5.
- the lock member 63a is urged radially inward by a spring 63c. Then, the lock member 63a protrudes into the lock chamber 63b formed on the outer periphery of the inner rotor 4, whereby the displacement of the relative rotational phase is prevented and the lock phase is restrained.
- the lock phase is usually set to such a phase that smooth startability of the engine can be obtained.
- the lock phase is set such that the most retarded phase of the relative rotational phase is the lock phase.
- detachment of the lock member 63a from the lock chamber 63b is performed by supplying hydraulic fluid (not shown) to the lock chamber 63b via the lock passage 62c. That is, when the hydraulic oil is supplied into the lock chamber 63b and filled up, and the pressure of the hydraulic oil biases the lock member 63a outward in the radial direction of the outer rotor 5 becomes larger than the biasing force of the spring 63c, The lock member 63a disengages from the lock chamber 63b. Thereby, the displacement of the relative rotational phase between the inner rotor 4 and the outer rotor 5 is allowed.
- the fastening member 7 penetrates from one end side in the axial direction of the inner rotor 4 to the other end side in the axial direction.
- the inner rotor 4 is fixed to the camshaft 3 by being fastened to the camshaft 3 at the end side.
- the fastening member 7 has an externally threaded portion 71 which can be screwed to the internally threaded portion 34 of the camshaft 3 on the other axial end side.
- the fastening member 7 also has a head 72 formed on one end side in the axial direction, and an intermediate portion 73 connecting the head 72 and the male screw portion 71.
- the head portion 72 of the fastening member 7 is formed to have a large diameter with respect to the male screw portion 71 and the middle portion 73, and a fastening tool (not shown) can be engaged with the axial center of one end of the axial direction Tooling holes 74 (see Figure 2) are provided.
- the head 72 corresponds to the “axial direction one end of the fastening member” in the present invention.
- the fastening member 7 causes the male screw portion 71 and the intermediate portion 73 to pass through the fixing holes 42 of the inner rotor 4 and causes the male screw portion 71 to be screwed on the female screw portion 34 of the camshaft 3.
- the inner rotor 4 is held between the head 72 of the fastening member 7 and the contact surface 33 of the camshaft 3, and the inner rotor 4 is fixed to the camshaft 3.
- an engaging portion 8A as the engaging means 8 is physically provided on one end side in the axial direction of the head portion 72 of the fastening member 7. .
- the engaging portion 8A is disposed on one end side in the axial direction with respect to the cover plate 52, and has an engaging groove 81 for mounting the driven device.
- the engagement portion 8A is formed at one end of the fastening member 7 in the axial direction and is disposed at one end side in the axial direction with respect to the cover plate 52, and the disc-like base And an engaging groove 81 formed along the diametrical direction.
- the disc-like base portion 82 is integrally formed by radially expanding a part of one axial end side of the head portion 72 of the fastening member 7 in the radial direction.
- the surface 82a on the other axial end side of the disc-like base 82 is disposed substantially in parallel with a predetermined distance not to abut the cover plate 52.
- the engaging groove 81 is a groove having a substantially square cross section which is open on the end face 82b side of the disc-like base 82 at one end side in the axial direction, and a straight line of a constant width w along the diameter direction of the disc-like base 82 It is formed in a shape.
- the width w of the engagement groove 81 is a width that fits the engagement convex portion 92 of the joint member 91 of the driven device 9 described later.
- a cylindrical recess 82c is formed around the tool engagement hole 74 in the axial center portion of the disc-like base 82, and is open on the end face 82b side at one axial end side for inserting the fastening tool. Ru.
- the engagement groove 81 of the engagement portion 8A is engaged with a joint member 91 provided on a drive shaft (not shown) of the driven device 9.
- a driven device 9 driven by the engine 2 includes, for example, accessories such as a vacuum pump and a fuel pump.
- the coupling member 91 of the driven device 9 is formed with an engagement convex portion 92 engaged with the engagement groove 81 of the engagement portion 8A.
- the engaging convex portion 92 is fitted into the engaging groove 81 of the engaging portion 8A, whereby the engaging portion 8A and the joint member 91 are engaged. Therefore, here, the engagement convex portion 92 is a convex stripe having a square cross section that fits into the engagement groove 81, and is formed in a linear shape with a constant width along the diametrical direction of the joint member 91.
- the engagement portion 8A constitutes a part of an old dam joint provided between the driven device 9 and the old dam joint by engaging with the joint member 91.
- the engagement convex portion 92 is formed on the other end side in the axial direction opposite to the engagement portion 8A of the fastening member 7, and the other end in the axial direction is opposite to that.
- An intermediate member 94 in which the convex portion 93 is formed to be protruded, and a second concave groove 9 engaged with the second convex portion 93.
- a driven-device-side member 96 in which 5 is formed.
- the second convex portion 93 formed on the intermediate member 94 is formed to project in the direction opposite to the engaging convex portion 92.
- the second convex portion 93 is formed in a linear shape having a constant width along the diameter direction of the joint member 91 in the direction orthogonal to the engagement convex portion 92.
- the second recessed groove 95 is formed at one axial end side of the driven device side member 96 facing the second convex portion 93 so as to be engageable with the second convex portion 93.
- FIG. 4 is a longitudinal sectional view of the valve timing control device 1 according to the present embodiment.
- FIG. 5 is a front view of the valve timing control device 1 according to the present embodiment.
- the valve opening / closing timing control device 1 according to the present embodiment includes an engagement member 8B force fastening member 7 having an engagement groove 81 disposed on one end side in the axial direction with respect to the cover plate 52. It differs from the first embodiment described above in which the engaging portion 8A is provided integrally with the fastening member 7 in that it is sandwiched between the head portion 72 and the inner rotor 4.
- differences from the first embodiment will be described in detail.
- the fastening member 7 has the same shape as a normal bolt, since the engaging portion 8A is formed. That is, the fastening member 7 is formed on the other end side in the axial direction, and has an external thread portion 71 which can be screwed to the internal thread portion 34 of the camshaft 3, a head 72 formed on one end side in the axial direction, and the head An intermediate portion 73 connecting the portion 72 and the male screw portion 71 is provided.
- the head portion 72 of the fastening member 7 is formed to have a large diameter with respect to the male screw portion 71 and the middle portion 73, and a fastening tool (not shown) can be engaged with the axial center of the end on one axial end side thereof.
- a tool engagement hole 74 (see Figure 5) is provided.
- the fastening member 7 penetrates from one axial end of the inner rotor 4 to the other axial end, and is fastened to the camshaft 3 at the other axial end of the inner rotor 4.
- the internal rotor 4 is held between the head 72 and the contact surface 33 of the camshaft 3 via the engaging member 8B described later, and the internal rotor 4 is fixed to the camshaft 3. There is.
- the engaging member 8 B includes a disc-like base portion 82 disposed on one end side in the axial direction with respect to the cover plate 52, and an engaging groove 81 formed along the diameter direction of the disc-like base portion 82.
- a fitting portion 83 fitted to the inner periphery of the fixing hole 42 through which the formed fastening member 7 can be penetrated, and a through hole 84 of the fastening member 7 formed radially inward of the fitting portion 83 have.
- the disk-like base 82 is disposed on one end side in the axial direction with respect to the cover plate 52, and the surface 82a on the other axial end side is not in contact with the cover plate 52 for a predetermined period of time. They are arranged approximately parallel with a gap.
- the engaging groove 81 is a groove having a substantially rectangular cross-section that opens on the end face 82b side of the disc-like base 82 at one axial end side, and has a constant width w along the diameter direction of the disc-like base 82. It is formed in a straight line.
- the width w of the engagement groove 81 is a width that fits the engagement convex portion 92 of the joint member 91 of the driven device 9 described later.
- an abutting portion 85 having an abutting surface 85a that abuts the surface 45 on the one axial end side of the internal rotor 4;
- a fitting portion which is formed to project from the other end side in the axial direction and is inserted from one end side in the axial direction into the fixing hole 42 formed in the inner rotor 4 and fitted on the inner periphery of the fixing hole 42 And are provided.
- the contact portion 85 and the disc-like base portion 82 are connected by a connecting portion 86.
- a cylindrical recess 87 having a size capable of inserting the head 72 of the fastening member 7 is formed in the axial center portion of the disc-like base 82 and the connecting portion 86.
- a through hole 84 having a size that allows the male screw portion 71 and the intermediate portion 73 of the fastening member 7 to pass therethrough is formed in the axial center portion of the contact portion 85 and the fitting portion 83.
- the fastening member 7 causes the male screw portion 71 and the intermediate portion 73 to pass through the through hole 84 to the fixing hole 42 of the inner rotor 4 and causes the male screw portion 71 to be screwed on the female screw portion 34 of the camshaft 3.
- the contact portion 85 of the engaging member 8B is held between the head 72 of the fastening member 7 and the surface 45 on the one axial end side of the inner rotor 4, and the engaging member 8B is fixed to the inner rotor 4. Be done.
- the engagement groove 81 is a groove having a substantially square cross section and is formed linearly in a constant width w along the diameter direction of the disc-like base 82 .
- the shape of the engagement groove 81 is not limited to such a shape. That is, the shape of the engagement groove 81 should be a shape that conforms to the shape of the engagement projection 92 provided on the driven device 9 side. Therefore, various shapes can be provided according to the shape of the engagement convex portion 92.
- the engaging portion 8A or the engaging member 8B as the engaging means 8 is formed along the disc-like base 82 and the diameter direction thereof.
- the configuration of the engagement means 8 according to the present invention is not limited to such an embodiment. That is, instead of the disk-like base 82, a base having various front shapes such as a polygon having a substantially rectangular shape or a substantially octagonal shape or an oval shape is used. It is also one of the preferred embodiments that the engaging groove 81 is formed along a straight line.
- the cover plate 52 is provided on one end side of the outer rotor 5 in the axial direction, and the rear plate 51 is provided on the other end side in the axial direction.
- the drive side rotation member 52 and the rear plate 51 are configured to rotate.
- the cover plate 52 and the rear plate 51 may be integrally formed with the external rotor 5 which is not necessarily provided. Therefore, in such a case, the engagement groove 81 of the engagement means 8 is disposed on one axial end side of the outer rotor 5.
- FIG. 1 is a longitudinal sectional view of a valve timing control apparatus according to a first embodiment of the present invention.
- FIG. 2 A front view of a valve timing control device according to the first embodiment of the present invention
- FIG. 3 A-A sectional view of Fig. 1
- FIG. 5 A front view of a valve timing control device according to a second embodiment of the present invention
- FIG. 6 A longitudinal sectional view of a valve timing control device according to the background art
- FIG. 7 Front view of the valve timing control device according to the background art
- Fixing hole (Through hole of fastening member formed on driven side rotating member) 1: Rya plate (Drive side rotating member)
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/815,262 US7765967B2 (en) | 2005-03-11 | 2006-02-10 | Valve timing control apparatus |
EP06713468A EP1857644B1 (en) | 2005-03-11 | 2006-02-10 | Valve opening/closing timing controller |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005069001A JP4161277B2 (ja) | 2005-03-11 | 2005-03-11 | 弁開閉時期制御装置 |
JP2005-069001 | 2005-03-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006095532A1 true WO2006095532A1 (ja) | 2006-09-14 |
Family
ID=36953134
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/302325 WO2006095532A1 (ja) | 2005-03-11 | 2006-02-10 | 弁開閉時期制御装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US7765967B2 (ja) |
EP (1) | EP1857644B1 (ja) |
JP (1) | JP4161277B2 (ja) |
CN (1) | CN100510326C (ja) |
WO (1) | WO2006095532A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170254232A1 (en) * | 2014-08-28 | 2017-09-07 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster having two ball joints |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006007671A1 (de) | 2006-02-18 | 2007-09-06 | Schaeffler Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE102008007561B4 (de) * | 2008-02-05 | 2019-08-22 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Nockenwellensteller mit einem Mitnehmerflansch, mit dem zumindest ein Nebenaggregat einer Brennkraftmaschine drehend antreibbar ist |
DE102008017688A1 (de) * | 2008-04-08 | 2009-10-15 | Schaeffler Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
JP5321925B2 (ja) * | 2011-02-18 | 2013-10-23 | アイシン精機株式会社 | 弁開閉時期制御装置 |
DE102011119285A1 (de) | 2011-11-24 | 2013-05-29 | Magna Powertrain Ag & Co. Kg | Verstellantrieb |
DE102012223811A1 (de) * | 2012-12-19 | 2014-06-26 | Mahle International Gmbh | Nockenwelle |
DE102013204659A1 (de) * | 2013-03-18 | 2014-09-18 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenversteller |
JP6128025B2 (ja) * | 2014-03-17 | 2017-05-17 | 株式会社デンソー | バルブタイミング調整装置 |
JP2017020434A (ja) * | 2015-07-13 | 2017-01-26 | 本田技研工業株式会社 | 内燃機関のオイルポンプ |
DE102016208248B3 (de) | 2016-05-13 | 2017-06-14 | Bayerische Motoren Werke Aktiengesellschaft | Ölabscheider zur Abscheidung von Öl aus Aerosol in einem Verbrennungsmotor |
CN110195624B (zh) | 2018-02-27 | 2022-05-17 | 博格华纳公司 | 凸轮轴承间的凸轮相位器 |
US10947870B2 (en) * | 2018-05-25 | 2021-03-16 | Schaeffler Technologies AG & Co. KG | Coupling for a camshaft phaser arrangement for a concentric camshaft assembly |
CN111140305B (zh) | 2018-11-01 | 2024-02-02 | 博格华纳公司 | 凸轮相位器凸轮轴联接 |
JP2020193583A (ja) * | 2019-05-28 | 2020-12-03 | 日立オートモティブシステムズ株式会社 | 内燃機関のバルブタイミング制御装置 |
Citations (4)
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JP2001263025A (ja) * | 2000-03-16 | 2001-09-26 | Nissan Motor Co Ltd | 内燃機関の補機駆動用カップリング装置 |
JP2004052708A (ja) * | 2002-07-23 | 2004-02-19 | Honda Motor Co Ltd | 多気筒エンジン |
JP2005030310A (ja) * | 2003-07-14 | 2005-02-03 | Honda Motor Co Ltd | カムホルダを備える内燃機関 |
JP2005076482A (ja) * | 2003-08-29 | 2005-03-24 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
Family Cites Families (6)
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---|---|---|---|---|
JPS5970828A (ja) * | 1982-10-18 | 1984-04-21 | Honda Motor Co Ltd | エアポンプ搭載内燃エンジン |
US5715780A (en) * | 1996-10-21 | 1998-02-10 | General Motors Corporation | Cam phaser position detection |
US6718921B2 (en) * | 2002-07-15 | 2004-04-13 | Delphi Technologies, Inc. | Method and apparatus for cleaning an oil control valve for an internal combustion engine |
US6953015B2 (en) | 2002-07-23 | 2005-10-11 | Honda Giken Hogyo Kabushiki Kaisha | Engine |
DE20221858U1 (de) * | 2002-12-21 | 2008-09-04 | Schaeffler Kg | Brennkraftmaschine mit einer Vorrichtung zur hydraulischen Drehwinkelverstellung ihrer Nockenwelle gegenüber ihrer Kurbelwelle sowie mit einer Vakuumpumpe für einen Servoverbraucher, insbesondere für einen Bremskraftverstärker |
JP2005002952A (ja) | 2003-06-13 | 2005-01-06 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
-
2005
- 2005-03-11 JP JP2005069001A patent/JP4161277B2/ja not_active Expired - Fee Related
-
2006
- 2006-02-10 CN CNB2006800078809A patent/CN100510326C/zh not_active Expired - Fee Related
- 2006-02-10 WO PCT/JP2006/302325 patent/WO2006095532A1/ja not_active Application Discontinuation
- 2006-02-10 EP EP06713468A patent/EP1857644B1/en not_active Expired - Fee Related
- 2006-02-10 US US11/815,262 patent/US7765967B2/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2001263025A (ja) * | 2000-03-16 | 2001-09-26 | Nissan Motor Co Ltd | 内燃機関の補機駆動用カップリング装置 |
JP2004052708A (ja) * | 2002-07-23 | 2004-02-19 | Honda Motor Co Ltd | 多気筒エンジン |
JP2005030310A (ja) * | 2003-07-14 | 2005-02-03 | Honda Motor Co Ltd | カムホルダを備える内燃機関 |
JP2005076482A (ja) * | 2003-08-29 | 2005-03-24 | Aisin Seiki Co Ltd | 弁開閉時期制御装置 |
Non-Patent Citations (1)
Title |
---|
See also references of EP1857644A4 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20170254232A1 (en) * | 2014-08-28 | 2017-09-07 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster having two ball joints |
US10329965B2 (en) * | 2014-08-28 | 2019-06-25 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster having two ball joints |
Also Published As
Publication number | Publication date |
---|---|
JP2006250063A (ja) | 2006-09-21 |
JP4161277B2 (ja) | 2008-10-08 |
EP1857644A4 (en) | 2009-08-19 |
CN101137821A (zh) | 2008-03-05 |
EP1857644B1 (en) | 2012-01-11 |
US20090038568A1 (en) | 2009-02-12 |
US7765967B2 (en) | 2010-08-03 |
CN100510326C (zh) | 2009-07-08 |
EP1857644A1 (en) | 2007-11-21 |
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