EP2843201A1 - Variable Ventilsteuerzeit-Steuervorrichtung - Google Patents

Variable Ventilsteuerzeit-Steuervorrichtung Download PDF

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Publication number
EP2843201A1
EP2843201A1 EP14182160.3A EP14182160A EP2843201A1 EP 2843201 A1 EP2843201 A1 EP 2843201A1 EP 14182160 A EP14182160 A EP 14182160A EP 2843201 A1 EP2843201 A1 EP 2843201A1
Authority
EP
European Patent Office
Prior art keywords
rotation member
side rotation
driven side
camshaft
flow path
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.)
Withdrawn
Application number
EP14182160.3A
Other languages
English (en)
French (fr)
Inventor
Yoshihiro Kawai
Masaki Kobayashi
Yoshiaki Yamakawa
Atsushi OTSUKI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Aisin Corp
Original Assignee
Aisin Seiki Co Ltd
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 Aisin Seiki Co Ltd filed Critical Aisin Seiki Co Ltd
Publication of EP2843201A1 publication Critical patent/EP2843201A1/de
Withdrawn legal-status Critical Current

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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
    • F01L1/34—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
    • 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
    • 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
    • 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
    • F01L2001/34433—Location oil control valves
    • 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
    • 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
    • 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
    • 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

Definitions

  • This disclosure generally relates to a variable valve timing control device.
  • a known variable valve timing control device favorably includes a driven side rotation member which is formed with a lightweight material which has small rotation inertia in order to easily change a relative rotational phase of the driven side rotation member relative to a driving side rotation member. Therefore, the driven side rotation member is generally made from a low strength material, for example, an aluminum material.
  • a camshaft connected to the driven side rotation member is generally made from a high-strength material, for example, an iron material.
  • a gap is easily formed at an interface between the driven side rotation member and the camshaft due to a difference between a coefficient of linear expansion of the driven side rotation member and a coefficient of linear expansion of the camshaft.
  • the driven side rotation member may be easily damaged because the high-strength camshaft is directly in contact with the low-strength driven side rotation member.
  • a known variable valve timing control device is disclosed in JP2012-57578A (hereinafter referred to as Patent reference 1).
  • the variable valve timing control device disclosed in Patent reference 1 is provided with a driving side rotation member (housing), a driven side rotation member (inner rotor), and a fluid pressure chamber defined between the driving side rotation member and the driven side rotation member, and a first flow path and a second flow path allowing an operation fluid to flow in or flow out of the fluid pressure chamber.
  • the variable valve timing control device further includes an intermediate member between an inner circumferential surface of the driven side rotation member and an outer circumferential surface of the camshaft and connects the driven side rotation member and the camshaft.
  • a space configuring a part of the first flow path is defined between the driven side rotation member and the camshaft, whereas a part of the second flow path is placed at the intermediate member.
  • a contact portion where the intermediate member is in contact with the driven side rotation member is provided between the first flow path and the second flow path.
  • the driven side rotation member is made from an aluminum material, whereas the intermediate member is made from an iron material.
  • variable valve timing control device because the variable valve timing control device includes the intermediate member which is positioned between the inner circumferential surface of the driven side rotation member and the outer circumferential surface of the camshaft, to connect the driven side rotation member and the camshaft, the driven side rotation member made from the aluminum material does not come in contact with the camshaft.
  • the driven side rotation member made from the aluminum material may be prevented from being damaged.
  • the intermediate member is made from the iron material which includes a coefficient of linear expansion that is close to a coefficient of linear expansion of the camshaft which is made from the high-strength material, the gap is not generated at the interface of the intermediate member and the camshaft. Accordingly, in a case where the flow path of the operation fluid extends over the intermediate member and the camshaft, the operation fluid does not leak easily.
  • the space formed between the driven side rotation member and the camshaft corresponds to the part of the first flow path, whereas the part of the second flow path is provided at the intermediate member.
  • the first flow path and the second flow path communicate with each other via the gap, and the operation fluid leaks out of and flows into the first and second flow paths. Accordingly, the relative rotational phase of the driven side rotation member relative to the driving side rotation member may not be changed precisely at the right time, or proper timing.
  • the contact portion where the intermediate member and the driven side rotation member come in contact with each other in the entire circumference between the first and second flow paths is provided to prevent the operation fluid from leaking out of and flowing into the first and second flow paths.
  • the intermediate member is inserted from an end of the driven side rotation member to be positioned between the inner circumference of the driven side rotation member and an outer circumference of the camshaft.
  • the intermediate member may easily come out of the driven side rotation member when the camshaft is mounted to the variable valve timing control device. Accordingly, the mounting process of the variable valve timing control device may be complicated.
  • a gap may be generated between the intermediate member and the driven side rotation member because of a resistance force applied when the intermediate member is press-fitted into the driven side rotation member.
  • the first and second flow paths communicate with each other via the gap, leading to the inferior operation.
  • variable valve timing control device that prevents a driven side rotation member from being damaged by a camshaft which is made from a high-strength material, that restrains an operation fluid from leaking out of and flowing into the first and second flow paths while simplifying the mounting process of the variable valve timing control device.
  • a variable valve timing control device includes a driving side rotation member configured to synchronously rotate with a driving shaft of an internal combustion engine, a driven side rotation member provided inwardly of the driving side rotation member to be coaxial with the driving side rotation member, the driven side rotation member integrally rotating with a camshaft for opening and closing a valve of the internal combustion engine, a fluid pressure chamber defined between the driving side rotation member and the driven side rotation member, a first flow path and a second flow path allowing a flow of an operation fluid into and out of the fluid pressure chamber to change a relative rotational phase of the driven side rotation member relative to the driving side rotation member between a most advanced angle phase and a most retarded angle phase, an intermediate member being provided between an inner circumferential surface of the driven side rotation member and an outer circumferential surface of the camshaft, the intermediate member connecting the driven side rotation member and the camshaft, and a contact portion where the intermediate member and the driven side rotation member come in contact with each other at a position between the first flow path and
  • the intermediate member comes in contact with the driven side rotation member between the first flow path and the second flow path when the intermediate member is mounted to the camshaft after the intermediate member and the driven side rotation member are mounted to the driving side rotation member after the intermediate member is press-fitted into the driven side rotation member.
  • the intermediate member and the driven side rotation member are mounted to the driving side rotation member, the intermediate member is positioned inside the driven side rotation member by press-fitting. Accordingly, without having to be glued by an adhesive material or attracted by a magnetic force of a magnet, the intermediate member is prevented from being coming out of the driven side rotation member by a friction force applied between the driven side rotation member and the intermediate member before mounting the driven side rotation member and the intermediate member to the camshaft.
  • the intermediate member is prevented from coming out of the driven side rotation member before mounting the camshaft to the intermediate member.
  • the driven side rotation member is prevented from being damaged by the camshaft which is made from a high-strength material.
  • the mounting process is simplified while adopting the construction where the operation fluid is prevented from leaking out of and flowing into the first and second flow paths.
  • variable valve timing control device further includes a control valve being positioned inwardly of the intermediate member in a radial direction, the control valve controlling the operation fluid to flow into and out of the fluid pressure chamber.
  • control valve of this disclosure may be mounted to a reduced space while reducing the process for configuring the flow path.
  • the intermediate member is press-fitted to a portion of an inner wall of the driven side rotation member.
  • the intermediate member may be processed with a reduced man-hour and a reduced size of the portion to be processed.
  • the intermediate member is press-fitted to the inner wall of the driven side rotation member at plural positions being equally spaced apart along a circumferential direction relative to an axis.
  • the intermediate member may be processed with a reduced man-hour and a further reduced size of the portion to be processed.
  • the intermediate member is fitted only to a portion positioned between a portion where the second flow path is formed and the contact portion of the inner wall.
  • the intermediate member may be processed with a reduced man-hour and a reduced size of the portion to be processed.
  • the driven side rotation member includes plural press-fitting portions which are irregularly positioned along the circumferential direction of the driven side rotation member, and come in contact with the intermediate member when press-fitting to the intermediate member, and a length from the press-fitting portion to a center of the driven side rotation member is shorter than a length from the inner wall to a center of the driven side rotation member.
  • the intermediate member may be processed with a reduced man-hour and a further reduced size of the portion to be processed.
  • variable valve timing control device for controlling, or regulating the timing for opening and closing an intake valve of an engine for a vehicle will be explained hereunder with reference to the drawings.
  • variable valve timing control device of this disclosure A first embodiment of the variable valve timing control device of this disclosure will be explained with reference to Figs. 1 to 5 .
  • the variable valve timing control device includes a driving side rotation member 1 (a housing) and a driven side rotation member 2 (an inner rotor).
  • the aluminum-alloy-made driving side rotation member 1 synchronously rotates with a crankshaft of an engine for a vehicle.
  • the aluminum-alloy-made driven side rotation member 2 is positioned inwardly of the driving side rotation member 1 to be coaxial with the driving side rotation member 1.
  • the driven side rotation member 2 integrally rotates with a camshaft 10 which opens and closes an intake valve of the engine.
  • the driven side rotation member 2 is relatively rotatably supported by the driving side rotation member 1.
  • the camshaft 10 is coaxially configured with a camshaft body 10a and a steel-made oil control valve bolt 10b, or a steel-made OCV bolt 10b.
  • the steel-made OCV bolt 10b is coaxially positioned within the driven side rotation member 2 and is screwed and fixed to the camshaft body 10a.
  • the engine for the vehicle corresponds to an internal combustion engine
  • the crankshaft corresponds to a driving shaft of the internal combustion engine.
  • a steel-made intermediate rotation member 6 serving as an intermediate member is provided between an inner circumference of the driven side rotation member 2 and an outer circumferential surface of the OCV bolt 10b.
  • the intermediate rotation member 6 is coaxially inserted and press-fitted into the driven side rotation member 2 to be positioned therein from a direction of a camshaft body 10a.
  • the cylindrical rotation member 6 transmits the rotation of the driven side rotation member 2 to the OCV bolt 10b.
  • the OCV bolt 10b is positioned between the driven side rotation member 2 and the intermediate rotation member 6 and screwed and fixed to an end portion of the camshaft body 10a.
  • the intermediate rotation member 6 connects the driven side rotation member 2 and the camshaft 10.
  • the camshaft body 10a serves as a rotation shaft of a cam which controls, or regulates the opening and closing of the intake valve of the engine.
  • the camshaft body 10a integrally rotates with the driven side rotation member 2, the intermediate rotation member 6, and the OCV bolt 10b.
  • the camshaft body 10a is rotatably mounted to a cylinder head of the engine.
  • the driving side rotation member 1 is integrally configured with a front plate 11, an outer rotor 12 and a rear plate 13.
  • the front plate 11 is positioned on the opposite side of the camshaft body 10a relative to the intermediate rotation member 6.
  • the driven side rotation member 2 is covered by the outer rotor 12.
  • the rear plate 13 is integrally provided with a timing sprocket 15.
  • the driven side rotation member 2 is accommodated in the driving side rotation member 1 and a fluid pressure chamber 4 is defined between the driving side rotation member 1 and the driven side rotation member 2.
  • plural projections 14 is positioned inwardly of the outer rotor 12 and protrudes inwardly in a radial direction and being spaced apart along the rotation direction S.
  • the fluid pressure chamber 4 is provided between the driven side rotation member 2 and the outer rotor 12.
  • the projection 14 functions as a shoe relative to an outer circumferential surface of the driven side rotation member 2.
  • Projections 21 are provided on the outer circumferential surface of the driven side rotation member 2 to be positioned at portions which face the fluid pressure chambers 4, respectively.
  • the fluid pressure chamber 4 is divided into an advanced angle chamber 41 serving as a fluid pressure chamber and a retarded angle chamber 42 serving as a fluid pressure chamber by the projection 21 along the rotation direction S. According to the embodiment, four fluid pressure chambers 4 are provided, however, the construction is not limited to the foregoing.
  • the oil serving as the operation fluid is supplied to and drained from the advanced angle chamber 41 and the retarded angle chamber 42, or is blocked to be supplied to and drained from the advanced angle chamber 41 and the retarded angle chamber 42, to apply the oil pressure to the projection 21. Accordingly, the relative rotational phase of the driven side rotation member 2 relative to the driving side rotation member 1 is displaced in either the advanced angle direction or the retarded angle direction, or the relative rotational phase is maintained at a predetermined phase.
  • the advanced angle direction is defined as a direction where the volume of the advanced angle chamber 41 increases and is indicated with an advanced angle direction S1 (serving as a first rotation direction) in Fig. 2 .
  • the retarded angle direction is defined as a direction where the volume of the retarded angle chamber 42 increases and is indicated with a retarded angle direction S2 (serving as a second rotation direction) in Fig. 2 .
  • the relative rotational phase when the volume of the advanced angle chamber 41 is maximized is defined as a most advanced angle phase.
  • the relative rotational phase when the volume of the advanced angle chamber 42 is maximized is defined as a most retarded angle phase.
  • the variable valve timing control apparatus includes a lock mechanism 8 which locks, or retains the relative rotational phase of the driven side rotation member 2 relative to the driving side rotation member 1 at a predetermined lock phase which is positioned between the most advanced angle phase and the most retarded angle phase.
  • a lock mechanism 8 which locks, or retains the relative rotational phase of the driven side rotation member 2 relative to the driving side rotation member 1 at a predetermined lock phase which is positioned between the most advanced angle phase and the most retarded angle phase.
  • a lock member 81 is movably configured along an axial direction.
  • the lock member 81 is maintained in a locked state, or a retained state by being held in an engaged state with a lock groove provided at either the front plate 11 or the rear plate 13 by using a biasing member.
  • a lock passage 82 is provided at the driven side rotation member 2 and connects the lock mechanism 8 and an advanced angle oil passage 43 (serving as a first flow path).
  • the advanced angle control is operated to displace the relative rotational phase of the driven side rotation member 2 relative to the driving side rotation member 1 to the advanced angle direction S1
  • the oil pressure is applied to the lock mechanism 8.
  • the lock member 81 comes out of the lock groove against the biasing force applied by the biasing member to release the locked state.
  • the OCV 51 serves as a control valve and controls, or regulates a supply and draining of the oil to and from the fluid pressure chamber 4.
  • the OCV 51 is coaxially provided with the camshaft 10 and positioned inwardly of the intermediate rotation member 6 in the radial direction.
  • the OCV 51 includes a spool 52, a spring 53 which biases the spool 52, and an electromagnetic solenoid 54 which activates the spool 52.
  • the spool 52 is accommodated in an accommodation space 5a which is provided at an end portion of the OCV bolt 10b and is slidable along an axis X inside the accommodation space 5a.
  • the electromagnetic solenoid 54 adopts a known structure.
  • a spring 53 is provided inside the accommodation space 5a at a position which is axially inward of the accommodation space 5a and constantly biases the spool 52 in a direction opposite to the camshaft body 10a.
  • a push pin 54a provided at the electromagnetic solenoid 54 pushes a rod portion 52a which is provided at the spool 52.
  • the spool 52 slides towards the camshaft body 10a against the biasing force of the spring 53.
  • the OCV 51 is configured to regulate, or control the position of the spool 52 by regulating, or controlling a duty ratio of the electric power supplied to the electromagnetic solenoid 54. Further, the feeding amount by the OCV 51 to the electromagnetic solenoid 54 is controlled by an electric control unit, or an ECU.
  • the cylindrical intermediate rotation member 6 is positioned inwardly of the driven side rotation member 2, specifically, positioned at a portion closer to the cam shaft body 10a (the right in Fig. 5 ).
  • a washer member 7 is positioned inwardly of the driving side rotation member 1 and the driven side rotation member 2 and positioned opposite from the camshaft body 10a (the left in Fig. 5 ) relative to the intermediate rotation member 6.
  • the intermediate rotation member 6 and the washer member 7 are positioned inwardly of the driven side rotation member 2. As shown in Figs.
  • the OCV bolt 10b is placed inwardly of each center hole of the washer member 7, the driven side rotation member 2 and the intermediate rotation member 6 and screwed and fixed to the camshaft body 10a.
  • the intermediate rotation member 6 and the driven side rotation member 2 are in contact with each other along the entire circumference in the axial direction between the advanced angle oil passage 43 and a retarded angle oil passage 44 (serving as a second flow path) and include a contact portion A.
  • the intermediate rotation member 6 comes in contact with the driven side rotation member 2 at a position between the advanced angle oil passage 43 and the retarded angle oil passage 44 when mounting the intermediate rotation member 6 to the camshaft 10 after mounting the intermediate rotation member 6 and the driven side rotation member 2 to the driving side rotation member 1.
  • the washer member 7 increases a tightening force of the OCV bolt 10 relative to the camshaft body 10a.
  • a torsion spring 9 is mounted to position between the washer member 7 and the front plate 11 and biases the washer member 7 and the front plate 11 to rotate the driven side rotation member 2 relative to the driving side rotation member 1 in the advanced angle direction S1.
  • An outer diameter of the intermediate rotation member 6 is set to be slightly greater than an inner diameter of a cylindrical inner wall 2a (serving as an inner wall) of the driven side rotation member 2.
  • a fitting portion 20 fits the entire outer circumferential surface of the intermediate rotation member 6 into the entire inner circumferential surface of the cylindrical inner wall 2a. Accordingly, the intermediate rotation member 6 is integrally mounted to the driven side rotation member 2 by press-fitting into the driven side rotation member 2 at the fitting portion 20.
  • a fitting pressure level of the fitting portion 20 to the driven side rotation member 2 is set to be a pressure level that allows the intermediate rotation member 6 to forcibly move to come in contact with the driven side rotation member 2 when the OCV bolt 10 which is inserted into and extends through the washer member 7, the driven side rotation member 2, and the intermediate rotation member 6 from a direction of the front plate 11 is screwed and fixed to the camshaft body 10a. Accordingly, the intermediate rotation member 6 reliably comes in contact with the driven side rotation member 2 throughout the circumference between the advanced angle oil passage 43 and the retarded angle oil passage 44 to prevent the oil from leaking out of and flowing into the advanced angle oil passage 43 and the retarded angle oil passage 44.
  • the oil reserved in the oil pan 61 is sucked by a mechanical oil pump 62 that is actuated in response to the transmission of the rotational drive force of the crankshaft, and is supplied to an oil supply passage 45.
  • the OCV 51 controls the supplying and draining, or the blocking operation to supply and drain the oil to and from the advanced angle oil passage 43 and the retarded angle oil passage 44.
  • the advanced angle oil passage 43 serves as an oil passage for changing the relative rotational phase of the driving side rotation member 1 and the driven side rotation member 2 in the advanced angle direction S1.
  • the retarded angle oil passage 44 serves as an oil passage for changing the relative rotational phase of the driving side rotation member 1 and the driven side rotation member 2 in the retarded angle direction S2.
  • the advanced angle oil passage 43, the retarded angle oil passage 44 and a supply oil passage 45 correspond to flow paths which selectively supply and drain the oil to and from the fluid pressure chamber 4 in order to change the relative rotational phase of the driven side rotation member 2 relative to the driving side rotation member 1 between a most advanced angle phase and a most retarded angle phase.
  • the advanced angle oil passage 43 corresponds to a first flow path and the retarded angle oil passage 44 corresponds to a second flow path.
  • the advanced angle oil passage 43 which communicates with the advanced angle chamber 41 is configured with a first through hole 43a, a first annular oil passage 43b, and a second through hole 43c.
  • the first through hole 43a is provided at the OCV bolt 5b.
  • the first annular oil passage 43b is positioned between the OCV bolt 5b and the driven side rotation member 2.
  • the second through hole 43c is provided at the driven side rotation member 2.
  • the retarded angle oil passage 44 which communicates with the retarded angle chamber 42 is configured with a third through hole 44a, a second annular oil passage 44b, a fourth through hole 44c, and a fifth through hole 44d.
  • the third through hole 44a is provided at the OCV bolt 5b.
  • the second annular oil passage 44b is provided at an inner circumferential surface of the intermediate rotation member 6 between the OCV bolt 10b and the intermediate rotation member 6.
  • the fourth through hole 44c is provided at the intermediate rotation member 6.
  • the fifth through hole 44d is provided at the driven side rotation member 2.
  • the second annular oil passage 44b and the fourth through hole 44c which configure parts of the retarded angle oil passage 44 are provided at the intermediate rotation member 6.
  • the oil supply passage 45 selectively supplying the oil to the advanced angle oil passage 43 and the retarded angle oil passage 44 is configured with a first passage 45a, a second passage 45b, a third annular passage 45c, and a sixth through hole 45d.
  • the first passage 45a is provided at the camshaft body 10a.
  • the second passage 45b is provided at the intermediate rotation member 6.
  • the third annular passage 45c is provided at the intermediate rotation member 6 between the intermediate rotation member 6 and the OCV bolt 10b.
  • the sixth through hole 45d is provided at the OCV bolt 10b.
  • the intermediate rotation member 6 includes the second annular oil passage 44b, the fourth though hole 44c, the second passage 45b and the third annular oil passage 45c which are the parts of the advanced angle oil passage 43, the retarded angle oil passage 44, and the supply oil passage 45 which supply and drain the oil to and from the fluid pressure chamber 4.
  • the oil which flows inside the supply oil passage 45 flows into an annular groove 52b which is provided at an outer circumferential surface of the spool 52.
  • the annular groove 52b communicates with neither the first through hole 43a nor the third through hole 44a which are provided at the OCV bolt 10b
  • the oil is not supplied to the advanced angle chamber 41 and the retarded angle chamber 42.
  • the first through hole 43a is configured so as not to communicate with the seventh through hole 52c which is provided at the spool 52, the oil in the advanced angle chamber 41 is not drained to the outside of the variable valve timing control device via the advanced angle oil passage 43, the seventh through hole 52c, the accommodation space 5a and a drain hole 52d.
  • the third through hole 44a is configured so as not to communicate with the accommodation space 5a, the oil in the retarded angle chamber 42 is not drained to the outside of the variable valve timing control device via the retarded angle oil passage 44, the accommodation space 5a and a drain hole 52d. That is, upon supplying a predetermined amount of electricity to the electromagnetic solenoid 54 to control the OCV 51 to hold the spool 52 at the position shown in Fig. 1 , the relative rotational phase of the driven side rotation member 2 relative to the driving side rotation member 1 is maintained because the oil is blocked so as not to be supplied and drained to and from the advanced angle chamber 41 and the retarded angle chamber 42.
  • the spool 52 When the electromagnetic solenoid 54 is not energized, the spool 52 is held at the position shown in Fig. 3 by the biasing force of the spring 53. In those circumstances, the annular groove 52b of the spool 52 communicates with the first through hole 43a of the OCV bolt 10b and does not communicate with the third through hole 44a. Simultaneously, the third through hole 44a communicates with the accommodation space 5a.
  • the oil supplied to the supply oil passage 45 is supplied to the advanced angle chamber 41 via the advanced angle oil passage 43, whereas the oil in the retarded angle chamber 42 is drained to the outside of the variable valve timing control device via the retarded angle oil passage 44, the accommodation space 5a, and the drain hole 52d. In those circumstances, the relative rotational phase is displaced in the advanced angle direction S1 by the oil pressure applied to the advanced angle chamber 41.
  • the spool 52 When the electromagnetic solenoid 54 is energized maximally, the spool 52 is held at the position shown in Fig. 4 against the biasing force of the spring 53. In those circumstances, the annular groove 52b of the spool 52 communicates with the third through hole 44a of the OCV bolt 10b and does not communicate with the first through hole 43a. Simultaneously, the first through hole 43a communicates with the seventh through hole 52c of the spool 52.
  • the oil supplied to the supply oil passage 45 is supplied to the retarded angle chamber 42 via the retarded angle oil passage 44, whereas the oil in advanced angle chamber 41 is drained to the outside of the variable valve timing control device via the advanced angle oil passage 43, the seventh through hole 52c, the accommodation space 5a, and the drain hole 52d.
  • the relative rotational phase is displaced in the retarded angle direction S2 by the oil pressure applied to the retarded angle chamber 42.
  • the fitting portion 20 of the intermediate rotation member 6 is press-fitted to a portion of the cylindrical inner wall 2a along the direction of the axis X, specifically, only the portion positioned between a portion where the retarded angle oil passage 44 is formed and the contact portion A.
  • the outer circumferential surface of the intermediate rotation member 6 protruding towards the rear plate 13 relative to the driven side rotation member 2 is relatively rotationally in close contact with the rear plate 13.
  • the intermediate rotation member 6 is in close contact with the driven side rotation member 2 at the fitting portion 20 and at the contact portion A. Accordingly, the advanced angle oil passage 43 and the retarded angle oil passage 44 are prevented from communicating with each other via the interface between the intermediate rotation member 6 and the driven side rotation member 2.
  • the outer circumferential surface of the intermediate rotation member 6 is configured so as to be relatively rotationally in close contact with the rear plate 13 to prevent the oil from leaking out via the retarded angle oil passage 44. Constructions other than the aforementioned configuration are similar to the constructions of first embodiment.
  • FIG. 7 A third embodiment of this disclosure will be explained referring to Fig. 7 .
  • the outer circumferential surface of the intermediate rotation member 6, specifically, the part protruding towards the rear plate 13 relative to the driven side rotation member 2 is relatively rotationally in close contact with the rear plate 13 to prevent the oil from leaking to the outside via the retarded angle oil passage 44.
  • plural fitting portions 200 which are formed on the outer circumferential surface of the intermediate rotation member 6 in order to be fitted to the cylindrical inner wall 2a of the driven side rotation member 2 are press-fitted to plural portions of the cylindrical inner wall 2a, the plural portions which are equally spaced apart along the circumferential surface of the cylindrical inner wall 2a.
  • press-fitting portions 20a include the same width and are equally spaced apart on the cylindrical inner wall 2a of the driven side rotation member 2 in a circumferential direction at, for example, three portions. A length from an inner surface of the press-fitting portions 20a to a center of the driven side rotation member 2 is shorter than a length from the cylindrical inner wall 2a to a center of the intermediate rotation member 6.
  • the intermediate rotation member 6 includes the fitting portions 200 which are equally spaced apart and press-fitted to the press-fitting portions 20a.
  • the intermediate rotation member 6 is coaxially positioned with the driven side rotation member 2 precisely while reducing the size of the portion of the intermediate rotation member 6 to be processed for press-fitting.
  • the fitting portions 200 may include the plural press-fitting portions 20a which are unequally spaced apart on the cylindrical inner wall 2a in the circumferential direction. That is, according to the third embodiment, the driven side rotation member 2 includes the plural press-fitting portions 20a which are irregularly positioned along the circumferential direction of the driven side rotation member 2 and come in contact with the intermediate rotation member 6 when press-fitting to the intermediate rotation member 6. A length from the press-fitting portion to a center of the driven side rotation member 2 is shorter than a length from the cylindrical inner wall 2a to a center of the driven side rotation member 2.
  • variable valve timing control device of the disclosure controls an opening and closing timing of an exhaust valve.
  • variable valve timing control device of the disclosure is applicable to an internal combustion engine for an automobile and for other purposes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP14182160.3A 2013-08-28 2014-08-25 Variable Ventilsteuerzeit-Steuervorrichtung Withdrawn EP2843201A1 (de)

Applications Claiming Priority (1)

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JP2013177121A JP2015045282A (ja) 2013-08-28 2013-08-28 弁開閉時期制御装置

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EP (1) EP2843201A1 (de)
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CN108474274A (zh) * 2015-12-28 2018-08-31 株式会社三国 阀定时变更装置
EP3399163A4 (de) * 2015-12-28 2019-08-14 Mikuni Corporation Vorrichtung zur änderung der ventilsteuerzeit

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Publication number Priority date Publication date Assignee Title
US10041384B2 (en) * 2016-05-31 2018-08-07 Gm Global Technology Operations Control valve
JP6954764B2 (ja) * 2017-05-12 2021-10-27 株式会社デンソー バルブタイミング調整装置

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EP2428656A1 (de) * 2010-09-10 2012-03-14 Aisin Seiki Kabushiki Kaisha Vorrichtung zur Regelung der variablen Ventilsteuerzeit
WO2012111388A1 (ja) * 2011-02-18 2012-08-23 アイシン精機株式会社 弁開閉時期制御装置

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JP4247624B2 (ja) * 2004-12-28 2009-04-02 株式会社デンソー バルブタイミング調整装置
JP5321926B2 (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
JP5426626B2 (ja) * 2011-09-03 2014-02-26 本田技研工業株式会社 開弁特性可変型内燃機関

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EP2428656A1 (de) * 2010-09-10 2012-03-14 Aisin Seiki Kabushiki Kaisha Vorrichtung zur Regelung der variablen Ventilsteuerzeit
JP2012057578A (ja) 2010-09-10 2012-03-22 Aisin Seiki Co Ltd 弁開閉時期制御装置
WO2012111388A1 (ja) * 2011-02-18 2012-08-23 アイシン精機株式会社 弁開閉時期制御装置

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108474274A (zh) * 2015-12-28 2018-08-31 株式会社三国 阀定时变更装置
EP3399162A4 (de) * 2015-12-28 2019-08-07 Mikuni Corporation Vorrichtung zur änderung der ventilsteuerzeit
EP3399163A4 (de) * 2015-12-28 2019-08-14 Mikuni Corporation Vorrichtung zur änderung der ventilsteuerzeit
US10533462B2 (en) 2015-12-28 2020-01-14 Mikuni Corporation Valve timing change device
US10858966B2 (en) 2015-12-28 2020-12-08 Mikuni Corporation Valve timing change device

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JP2015045282A (ja) 2015-03-12
CN104420918A (zh) 2015-03-18

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