WO2012053447A1 - 弁開閉時期制御装置 - Google Patents
弁開閉時期制御装置 Download PDFInfo
- Publication number
- WO2012053447A1 WO2012053447A1 PCT/JP2011/073685 JP2011073685W WO2012053447A1 WO 2012053447 A1 WO2012053447 A1 WO 2012053447A1 JP 2011073685 W JP2011073685 W JP 2011073685W WO 2012053447 A1 WO2012053447 A1 WO 2012053447A1
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- WO
- WIPO (PCT)
- Prior art keywords
- rotating body
- side rotating
- driven
- urging
- partition
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- 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
- 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
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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
- F01L1/356—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 making the angular relationship oscillate, e.g. non-homokinetic drive
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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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0476—Camshaft bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
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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
- F01L2001/34453—Locking means between driving and driven members
- F01L2001/34469—Lock movement parallel 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
- F01L2001/34479—Sealing of phaser devices
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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
- F01L2250/00—Camshaft drives characterised by their transmission means
- F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
Definitions
- the present invention relates to a valve opening / closing timing control device that adjusts the opening / closing timing of an intake valve and an exhaust valve of an internal combustion engine such as an automobile in accordance with an operating state.
- valve opening / closing timing control device in order to prevent the working fluid from leaking between the advance chamber and the retard chamber, the position of the partition that faces the drive side rotor or the driven side rotor Alternatively, an urging member is disposed at a position facing the partition portion of the driving side rotating body or the driven side rotating body. At this time, in order to save the space of the urging member, the valve opening / closing timing control device has been downsized.
- Patent Document 1 discloses that a partition portion is configured by a vane disposed in a vane groove of a driven side rotating body, and the urging member is formed by an arcuate leaf spring. A configuration in which the intermediate side of the urging member abuts on the driven side rotating body and both end sides of the urging member abut on the vane is disclosed.
- the partition portion is configured by a projecting portion that protrudes from the driving side rotating body and the driven side rotating body, the biasing member is configured by an arcuate leaf spring, and the intermediate side of the biasing member is the partition portion.
- a structure is disclosed in which both end sides of the urging member abut against the seal member.
- the biasing force of the biasing member is too small, engine oil will leak between the advance chamber and the retard chamber.
- the urging force of the urging member is too large, the frictional force between the drive side rotator and the vane or the seal member becomes too large, and the driven side rotator is difficult to move smoothly, and the intake valve is appropriately timed. There is a possibility that the opening and closing operation cannot be performed. Further, the vane and the seal member are easily worn and damaged. Therefore, it is desirable that the urging force of the urging member be within an appropriate range.
- Patent Document 1 since only a stroke corresponding to the swing width of the bow-shaped leaf spring can be obtained, the stroke of the urging member is shortened. For this reason, for example, if there is an error in the dimensions of the drive-side rotator and the driven-side rotator, the distance between the vane and the driven-side rotator, the protrusion and the drive-side rotator as the driven-side rotator moves. Or the space
- An object of the present invention is to provide a valve opening / closing timing control device capable of reducing the working accuracy of the driving side rotating body and the driven side rotating body while saving space.
- a first characteristic configuration of the valve opening / closing timing control device of the present invention is a drive-side rotator that rotates synchronously with a crankshaft, and is arranged coaxially with respect to the drive-side rotator and is used for opening and closing a valve of an internal combustion engine.
- the drive-side rotator and the driven-side rotator that rotate synchronously with the camshaft, and the hydraulic chamber formed by the drive-side rotator and the driven-side rotator are divided into a retard chamber and an advance chamber, and A partition provided on at least one of the driven-side rotator, and a position of the partition facing the drive-side rotator or the driven-side rotator, or the drive-side rotator or the driven-side rotator Among them, the working fluid is disposed between the retarding chamber and the advance chamber based on the relative rotation of the driving side rotating body and the driven side rotating body.
- the seal member is moved from the partition portion side to the driving side rotating body or the driven side rotating body side, or the seal member is moved from the driving side rotating body or the driven side rotating body side to the partition.
- An urging member that urges toward the portion side, and the urging member includes at least one valley fold portion and a mountain fold portion, and one end portion of the urging member and the one end portion side.
- At least one valley fold portion and one mountain fold portion exist between the abutting portion on one end side and the abutting portion on the other end side, and along with the urging of the urging member Since the distance between the contact portions on the one end side and the other end side and the angles of the valley fold portion and the mountain fold portion are reduced, the stroke of the urging member can be made sufficiently long. For this reason, for example, due to variations in the dimensions of the drive-side rotator and the driven-side rotator, the distance between the partition portion and the drive-side rotator or the driven-side rotator varies as the driven-side rotator moves. Even if the radial width of the biasing member varies, the biasing force does not vary so much.
- the biasing force of the biasing member can be easily kept within a predetermined range without enlarging the working accuracy of the driving side rotating body and the driven side rotating body, and the seal member is biased with an appropriate biasing force. be able to.
- the biasing member includes a non-contact portion between the contact portion on the one end side and the contact portion on the other end side, and in the longitudinal direction of the biasing member.
- the contact part on the one end side and the contact part on the other end side are shorter than the non-contact part.
- a third characteristic configuration of the present invention is a drive-side rotator that rotates synchronously with respect to a crankshaft, and is arranged coaxially with the drive-side rotator and rotates synchronously with a camshaft for opening and closing a valve of an internal combustion engine. At least one of the driving side rotating body and the driven side rotating body so as to partition a fluid pressure chamber formed by the driven side rotating body, the driving side rotating body and the driven side rotating body into a retard chamber and an advance chamber.
- a partition provided on one side and a position of the partition that faces the drive-side rotator or the driven-side rotator, or the drive-side rotator or the driven-side rotator that faces the partition A sealing member that is disposed at a position to prevent leakage of the working fluid between the retard chamber and the advance chamber based on relative rotation between the driving side rotating body and the driven side rotating body; By the biasing force based on elastic deformation, From the partition part side to the driving side rotating body or the driven side rotating body side, or the seal member from the driving side rotating body or the driven side rotating body side to the partition side.
- An urging member that urges the urging member, and the urging member includes at least one valley fold portion and a mountain fold portion, and is positioned on one end portion of the urging member and the one end portion side. Formed between the valley fold or the mountain fold, and between the other end of the biasing member and the valley fold or the mountain fold located on the other end, A sealing member, or a contact portion on both ends contacting the partition portion or the driving-side rotating body or the driven-side rotating body; the valley folding portion or the mountain folding portion located on the one end side; and The valley fold or the mountain located on the other end side Formed on the opposite side of the seal member, the partition, the driving-side rotator, or the driven-side rotator, on the side opposite to the side where the abutting portions on both ends abut.
- At least one valley fold portion and one mountain fold portion exist between the abutting portion on one end side and the abutting portion on the other end side, and along with the urging of the urging member Since the distance between the contact portions on the one end side and the other end side and the angles of the valley fold portion and the mountain fold portion are reduced, the stroke of the urging member can be made sufficiently long. For this reason, for example, even if the distance between the partitioning portion and the drive-side rotator or the driven-side rotator and the radial width of the urging member change with the movement of the driven-side rotator, the urging force is not increased. It does not fluctuate so much.
- the working accuracy of the driving side rotating body and the driven side rotating body can be relaxed.
- the urging member is supported at three points by the abutting portions on both ends and the abutting portion on the intermediate side, the posture of the urging member is stabilized.
- the biasing member is a leaf spring material
- the contact portion is in surface contact with the seal member, the partition portion, the driving side rotating body, or the driven side rotating body. This is in that a contact surface is formed.
- the biasing member abuts the seal member, the partition portion, the driving-side rotating body, or the driven-side rotating body through a predetermined area, and thus the posture of the biasing member is further stabilized. To do.
- FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1 and shows a valve opening / closing timing control device in a locked state.
- FIG. 5 is an enlarged cross-sectional view around the protrusion on the outer rotor side.
- These are exploded perspective views showing a sealing member and a biasing member according to the present invention.
- These are side views which show a biasing member.
- These are side views which show the biasing member of 2nd Embodiment.
- valve timing control device according to the present invention is applied to the intake valve side of an automobile engine E (an example of an internal combustion engine) will be described.
- the valve timing control device includes a housing 1 (an example of a drive side rotating body) that rotates synchronously with a crankshaft C, and is coaxially disposed with respect to the housing 1 and rotates synchronously with a camshaft 21.
- An internal rotor 2 (an example of a driven rotor).
- the internal rotor 2 is integrally assembled with the tip portion of the camshaft 21.
- the housing 1 includes a front plate 11 on the side opposite to the side to which the camshaft 21 is connected, an external rotor 12 having a timing sprocket 15, and a rear plate 13 on the side to which the camshaft 21 is connected. .
- crankshaft C When the crankshaft C is rotationally driven, the rotational driving force is transmitted to the timing sprocket 15 via the power transmission member 22, and the housing 1 is rotationally driven in the rotational direction S (see FIG. 2). As the housing 1 is rotationally driven, the internal rotor 2 is rotationally driven in the rotational direction S, and the camshaft 21 is rotationally driven. As the camshaft 21 rotates, a cam (not shown) provided on the camshaft 21 opens and closes an intake valve (not shown).
- first protrusions 14 (an example of a partition part) protruding inward in the radial direction are formed on the inner peripheral surface of the outer rotor 12 in the rotation direction S. It is formed along.
- the first protrusion 14 is close to the outer peripheral surface of the inner rotor 2. Thereby, the space surrounded by the outer rotor 12 and the inner rotor 2 is partitioned by the first projecting portion 14 and partitioned into a plurality of (four in the present embodiment) fluid pressure chambers 4.
- a plurality of (four in this embodiment) second projecting portions 16 (an example of a partitioning portion) projecting radially outward are formed on the outer peripheral surface of the inner rotor 2 along the rotational direction S.
- the second protrusion 16 is close to the inner peripheral surface of the outer rotor 12.
- each fluid pressure chamber 4 is partitioned by the second projecting portion 16, and is divided into an advance chamber 4a and a retard chamber 4b adjacent to each other in the rotation direction S.
- the internal rotor 2 and the camshaft 21 are formed with advance passages 17 communicating with each advance chamber 4a and retard passages 18 communicating with each retard chamber 4b.
- Engine oil (an example of a working fluid) is supplied to the advance chamber 4a through the advance passage 17, and the engine oil is discharged from the retard chamber 4b through the retard passage 18.
- the pressure of the engine oil is applied to the second protrusion 16 in the advance direction S1 (see FIG. 2) in which the volume of the advance chamber 4a increases, and the relative rotation of the internal rotor 2 with respect to the housing 1
- the phase is displaced in the advance direction S1, that is, the camshaft is advanced with respect to the crankshaft C.
- Engine oil is supplied to the retard chamber 4b through the retard passage 18 and discharged from the advance chamber 4a through the advance passage 17.
- the engine oil pressure is applied to the second projecting portion 16 in the retarding direction S2 (see FIG. 2) in which the volume of the retarding chamber 4b increases, and the relative rotational phase is shifted in the retarding direction S2. That is, the camshaft is retarded with respect to the crankshaft C.
- the relative rotational phase is maintained at an arbitrary phase by stopping the supply and discharge of engine oil to the advance chamber 4a and the retard chamber 4b.
- the valve opening / closing timing control device is provided with a lock mechanism 6 that can restrict the relative rotation phase to the lock phase when the engine E is started.
- the lock mechanism 6 includes a housing portion 6a formed in the second projecting portion 16, a lock member 6b housed in the housing portion 6a, a lock groove (not shown) formed in the rear plate 13, and a lock.
- a spring (not shown) for urging the member 6b in a direction protruding into the lock groove.
- the lock mechanism 6 is operated by supplying and discharging engine oil to and from a lock passage 6c communicating with the accommodating portion 6a.
- the valve opening / closing timing control device is provided with an advance chamber 4a and a retard chamber 4b, and a fluid supply / discharge mechanism 5 for controlling supply / discharge of engine oil to / from the housing portion 6a. ing.
- the fluid supply / discharge mechanism 5 includes an oil pan 5a that stores engine oil, an oil pump 5b that sends engine oil, and a fluid control valve (OCV) that controls supply / discharge of engine oil to the advance passage 17 and the retard passage 18. ) 5c and a fluid switching valve (OSV) 5d for controlling supply and discharge of engine oil to and from the lock passage 6c.
- the fluid control valve 5c and the fluid switching valve 5d are controlled by the ECU 7.
- seal member SE is disposed at the tip portion of the first projecting portion 14 facing the inner rotor 2 so that the engine oil does not leak, and the seal member SE is disposed from the first projecting portion 14 side to the inside.
- a biasing member SP that biases toward the rotor 2 (inward in the radial direction) is disposed.
- a seal member SE is disposed at a tip portion of the second projecting portion 16 that faces the external rotor 12, and the seal member SE is disposed from the second projecting portion 16 side to the outer rotor 12 side (radially outward).
- a biasing member SP that biases the side is disposed.
- a mounting groove 31 having a rectangular cross section is formed along the rotation axis X at the tip of the second protrusion 16.
- a seal member SE is disposed in the mounting groove 31 so as to be slidable along the radial direction (biasing direction) of the inner rotor 2.
- the seal member SE has one rectangular parallelepiped slidable contact portion 32 and two cuboids that protrude from both ends of the slidable contact portion 32 in a direction intersecting the slidable contact portion 32 (the rear side direction of the mounting groove 31). Shaped leg 33.
- a substantially S-shaped biasing member SP is accommodated between the seal member SE and the mounting groove 31 and between the two leg portions 33.
- the urging member SP troughs a portion on one end side of one surface of the long leaf spring material to form a bent portion 34 (one example of a valley fold portion) on one end side of the arc shape.
- the part on the other end side of the one surface of the leaf spring material is mountain-folded to form the arc-shaped bent part 35 (an example of the mountain folded part) on the other end side.
- a flat plate part 36 on one end side that makes surface contact with the sliding contact part 32 of the seal member SE (an example of a contact part and a contact surface). Is formed.
- An intermediate flat plate portion 37 (an example of a non-contact portion) is formed between the bent portion 34 on one end side and the bent portion 35 on the other end side.
- the flat plate portion 38 (the abutting portion, which is in surface contact with the bottom of the mounting groove 31 of the second projecting portion 16).
- An example of a contact surface is formed.
- the radial distance between the flat plate portion 36 on the one end side and the flat plate portion 38 on the other end side becomes smaller, and the bent portion 34 on the one end side and the bent portion on the other end side are bent.
- the angle of the part 35 becomes small.
- the urging force of the urging member SP is too small, the engine oil leaks between the advance chamber 4a and the retard chamber 4b.
- the urging force of the urging member SP is too large, the frictional force between the inner peripheral surface of the outer rotor 12 and the seal member SE and the frictional force between the outer peripheral surface of the inner rotor 2 and the seal member SE become too large.
- the internal rotor 2 is difficult to move smoothly, and there is a possibility that the intake valve cannot be opened / closed at an appropriate timing. Further, the seal member SE is easily worn and damaged. Therefore, it is desirable that the urging force of the urging member SP be within an appropriate range.
- the bent portion 34 on the one end side and the bent portion 35 on the other end side exist between the flat plate portion 36 on the one end side and the flat plate portion 38 on the other end side. For this reason, the stroke of the urging member SP can be lengthened by the number of bent portions.
- the flat plate portion 36 on one end side is in close contact with the sliding contact portion 32 of the seal member SE, and the flat plate portion 38 on the other end side is in close contact with the bottom portion of the mounting groove 31 of the second projecting portion 16. The posture is stabilized.
- the stroke of the urging member SP refers to the radial width of the urging member SP when the urging member SP is compressed most and the radial direction of the urging member SP when the urging member SP is not compressed at all. It is the difference from the width.
- the flat plate portion 37 on the intermediate side is substantially the same as the inner width of the leg portion 33, and the flat plate portion 36 on one end side and the flat plate portion 38 on the other end side are shorter than the flat plate portion 37 on the intermediate side. . If the intermediate flat plate portion 37, the flat plate portion 36 on one end side, and the flat plate portion 38 on the other end side are substantially the same as the inner width of the leg portion 33, for example, when a large force is applied to the seal member SE, The flat plate portion 36 on one end side is sandwiched between the sliding contact portion 32 of the seal member SE and the bent portion 35 on the other end side, or the bottom portion and the bent portion on the one end side of the mounting groove 31 of the second projecting portion 16.
- the seal member SE may be sandwiched between the flat plate portion 38 on the other end side. At this time, the degree of deformation of the bent portion 34 on the one end side and the bent portion 35 on the other end side may increase, and the seal member SE may not be biased with an appropriate biasing force. Therefore, it is necessary to widen the space between the seal member SE and the mounting groove 31.
- the intermediate flat plate portion 37, the flat plate portion 36 on one end side, and the flat plate portion 38 on the other end side are substantially equal to the inner width of the leg portion 33. It may be the same. Thereby, the contact area between the flat plate portion 36 on one end side and the sliding contact portion 32 of the seal member SE and the contact area between the flat plate portion 38 on the other end side and the bottom portion of the mounting groove 31 of the second projecting portion 16 are minimized. It can be taken widely, and the posture of the urging member SP is further stabilized.
- a folded portion on one end side that is folded back to the opposite side of the sliding contact portion 32 of the seal member SE is formed at the end portion of the flat plate portion 36 on one end side, and the end portion of the flat plate portion 38 on the other end side is formed.
- a folded portion on the other end side that is folded back to the opposite side of the bottom of the mounting groove 31 of the second projecting portion 16 is formed.
- a flat plate portion on one end side instead of forming a folded portion on one end side at the end portion of the flat plate portion 36 on one end side and forming a folded portion on the other end side on the end portion of the flat plate portion 38 on the other end side, a flat plate portion on one end side.
- the rounded portion may be formed by polishing 36 and the end of the flat plate portion 38 on the other end side.
- the urging member SP of the present invention may have a substantially M shape.
- the urging member SP is formed with three bent portions 41, 42, 43. With the urging of the urging member SP, a flat plate portion 44 on one end side and a flat plate portion 47 on the other end side are formed. And the angle of the three bent portions 41, 42, 43 is reduced. Thereby, the effect similar to 1st Embodiment can be achieved.
- the bent portion 34 on one end side and the bent portion 35 on the other end side are longer than the urging member SP. It moves along the direction (direction intersecting the urging direction), and the flat plate portion 36 on one end side and the flat plate portions 38 on the other end side move relative to each other. For this reason, the flat plate portion 36 on one end side and the flat plate portion 38 on the other end side slide.
- the two bent portions 41 and 42 and the two bent portions 42 and 43 are along the longitudinal direction.
- the two bent portions 41 and 43 do not move along the longitudinal direction, and the flat plate portion 44 on one end side and the flat plate portion 47 on the other end side do not move relative to each other. Therefore, the flat plate portion 44 on the one end side and the flat plate portion 47 on the other end side do not slide, and the seal member SE and the second protruding portion 16 are hardly worn or damaged.
- the flat plate portion 44 on one end side, the flat plate portion 45 near one end (an example of a non-contact portion), the flat plate portion 46 near the other end (an example of a non-contact portion), and the flat plate portion 47 on the other end side is substantially the same as the inner width of the leg 33.
- the flat plate portion 45 near one end and the flat plate portion 46 near the other end are made substantially the same as the inner width of the leg portion 33, and the flat plate portion 44 closer to one end than the flat plate portion 45 near one end and the flat plate portion 46 near the other end.
- the flat plate portion 47 on the other end side may be shortened.
- the bent portions 41, 42, and 43 have the same radius of curvature.
- the other bent portions 41 and 43 may have different radii of curvature with respect to the bent portion 42 on the intermediate side. Thereby, it becomes easy to balance the respective urging forces of the urging members SP.
- the flat plate portion 44 on one end side and the flat plate portion 47 on the other end side may be shortened. Thereby, even if the size of the intermediate bent portion 42 increases, the intermediate bent portion 42 is unlikely to contact the flat plate portion 44 on one end side and the flat plate portion 47 on the other end side. Therefore, deformation of the bent portion 42 on the intermediate side can be suitably prevented.
- the urging member SP of the present invention may have a substantially ⁇ -shape.
- This urging member SP is the same as that obtained by connecting two urging members SP (see FIG. 5) of the first embodiment.
- a flat plate portion 55 on one end side that makes surface contact with the sliding contact portion 32 of the seal member SE (an example of a contact portion and a contact surface).
- a flat plate portion 56 near one end is formed between the bent portion 51 on one end side and the bent portion 52 near one end.
- an intermediate flat plate portion 57 (abutting portion, abutting portion) that comes into surface contact with the bottom of the mounting groove 31 of the second projecting portion 16.
- An example of a surface) is formed.
- a flat plate portion 58 near the other end is formed between the bent portion 53 near the other end and the bent portion 54 near the other end.
- a flat plate portion 59 (contact portion, contact surface) on the other end side that comes into surface contact with the sliding contact portion 32 of the seal member SE. Example) is formed.
- the same effect as the first embodiment can be achieved.
- the biasing member SP is supported by the three surfaces of the flat plate portion 55 on the one end side, the flat plate portion 57 on the intermediate side, and the flat plate portion 59 on the other end side, the posture of the biasing member SP is stabilized.
- the urging member SP of the present invention may have a continuous drum shape as shown in FIG.
- This urging member SP is the same as one in which two urging members SP (see FIG. 6) of the second embodiment are connected.
- the urging member SP includes a first flat plate portion 61 (an example of a contact portion and a contact surface) that comes into surface contact with the sliding contact portion 32 of the seal member SE, and a bottom portion of the mounting groove 31 of the second projecting portion 16. And a second flat plate portion 62 (an example of an abutting portion and an abutting surface) that are in surface contact with each other.
- the same effect as the first embodiment can be achieved.
- the first flat plate portion 61 and the second flat plate portion 62 do not move relative to each other as the urging member SP is compressed. Therefore, the seal member SE and the second protrusion 16 are not easily worn or damaged. In this way, if the biasing member SP is in a loop shape, there is no end face, and therefore, the sliding contact portion 32 of the seal member SE and the bottom portion of the mounting groove 31 of the second protruding portion 16 are hardly scratched.
- the second projecting portion 16 is formed on the inner rotor 2, but the present invention is not limited to this.
- a configuration in which a vane groove is formed in the internal rotor 2 and a plate-shaped vane is disposed in the vane groove may be employed.
- the vane itself is urged toward the external rotor 12 and serves as a seal member. Therefore, the sealing member and the urging member according to the present invention are disposed only in the first projecting portion 14 as the partitioning portion on the external rotor 12 side.
- mounting grooves are formed in the first projecting portion 14 of the outer rotor 12 and the second projecting portion 16 of the inner rotor 2, and the seal member SE is disposed in these mounting grooves.
- a mounting groove may be formed in the inner rotor 2 facing the first projecting portion 14 and the outer rotor 12 facing the second projecting portion 16 of the inner rotor 2, and the seal member SE may be disposed in the groove portion. .
- the urging member SP is made of a leaf spring material, but is not limited thereto.
- the urging member SP may be constituted by a wire spring material or a member obtained by joining a wire spring material and a leaf spring material.
- valve timing control apparatus can be applied not only to the intake valve side but also to both the intake valve side and the exhaust valve side.
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Abstract
Description
この種の弁開閉時期制御装置においては、進角室と遅角室との間での作動流体の漏洩を防止するために、仕切部のうち駆動側回転体もしくは従動側回転体に対向する位置、または、駆動側回転体もしくは従動側回転体のうち仕切部に対向する位置に付勢部材を配設してある。このとき、付勢部材の省スペース化を図って、弁開閉時期制御装置を小型化することが行われてきた。
従来、省スペース化を図ることができる付勢部材として、特許文献1には、仕切部を従動側回転体のベーン溝に配設されたベーンで構成し、付勢部材を弓形の板バネで構成して、付勢部材の中間側が従動側回転体に当接し、付勢部材の両端側がベーンに当接する構成が開示されている。
このため、例えば、駆動側回転体および従動側回転体の寸法に誤差があると、従動側回転体の移動に伴って、ベーンと従動側回転体との間隔や、突出部と駆動側回転体もしくは従動側回転体との間隔が変動し、付勢部材の径方向の幅が変動する。このとき、上述したように、付勢部材のストロークが短いため、付勢部材の径方向の幅の変動がたとえわずかであったとしても、付勢部材の付勢力が大きく変動してしまう。したがって、付勢部材の付勢力を適度の範囲内に収めるためには、駆動側回転体および従動側回転体の工作精度を高くしておく必要があった。
〔全体構成〕
図1に示すように、弁開閉時期制御装置は、クランクシャフトCと同期回転するハウジング1(駆動側回転体の一例)と、そのハウジング1に対して同軸配置されてカムシャフト21と同期回転する内部ロータ2(従動側回転体の一例)と、を備えている。
図1に示すように、内部ロータ2は、カムシャフト21の先端部に一体的に組み付けられている。ハウジング1は、カムシャフト21が接続される側とは反対側のフロントプレート11と、タイミングスプロケット15を有する外部ロータ12と、カムシャフト21が接続される側のリアプレート13と、を備えている。
図2に示すように、弁開閉時期制御装置には、エンジンEの始動時等に相対回転位相をロック位相に拘束可能なロック機構6が設けられている。このロック機構6は、第2突出部16に形成された収容部6aと、その収容部6aに収容されたロック部材6bと、リアプレート13に形成されたロック溝(図示せず)と、ロック部材6bをロック溝に突出する方向に付勢するバネ(図示せず)と、を備えている。
図1,図2に示すように、弁開閉時期制御装置には、進角室4aおよび遅角室4b、並びに、収容部6aに対するエンジンオイルの給排を制御する流体給排機構5が設けられている。
図1~図5に示すように、進角室4aと進角室4aとの間でエンジンオイルが漏洩すると、吸気弁を適切なタイミングで開閉操作できなくなる虞がある。このため、エンジンオイルが漏洩しないように、第1突出部14のうち内部ロータ2に対向する先端部分にシール部材SEを配設するとともに、そのシール部材SEを第1突出部14の側から内部ロータ2の側(径方向内方側)に付勢する付勢部材SPを配設してある。
仮に、中間側の平板部37、一端側の平板部36、他端側の平板部38を脚部33の内幅とほぼ同じにすると、例えば、シール部材SEに大きな力が掛かったときに、シール部材SEの摺接部32と他端側の折曲部35との間に一端側の平板部36が挟み込まれたり、第2突出部16の取付溝31の底部と一端側の折曲部34との間に他端側の平板部38が挟み込まれることがある。このとき、一端側の折曲部34および他端側の折曲部35の変形度が増大して、適正な付勢力でシール部材SEを付勢できなくなることがある。よって、シール部材SEと取付溝31との間を広く取る必要がある。
この実施形態では、第1実施形態の構成と異なる構成についてのみ説明し、同じ構成については説明を省略する。
この付勢部材SPには、3つの折曲部41,42,43が形成されており、付勢部材SPの付勢に伴って、一端側の平板部44と他端側の平板部47との径方向における間隔が小さくなると共に、3つの折曲部41,42,43の角度が小さくなる。これにより、第1実施形態と同様の作用効果を叶えることができる。
図7に示すように、本発明の付勢部材SPとしては、略Ω字状の形状としてもよい。この付勢部材SPは、第1実施形態の付勢部材SP(図5を参照)を2つ連結したものと同じである。
さらに、本発明の付勢部材SPは、図8に示すように、連続した鼓形状としてもよい。この付勢部材SPは、第2実施形態の付勢部材SP(図6を参照)を2つ連結したものと同じである。
2 従動側回転体
4 流体圧室
4a 進角室
4b 遅角室
14 仕切部
16 仕切部
35、41、43、52、53、65、70 山折り部
34、42、51、54、63、67、68、72 谷折り部
36、38、44、47、55、57、59、61、62 当接部、当接面
37、45、46 非当接部
SE シール部材
SP 付勢部材
Claims (4)
- クランクシャフトに対して同期回転する駆動側回転体と、
前記駆動側回転体に対して同軸上に配置され、内燃機関の弁開閉用のカムシャフトに同期回転する従動側回転体と、
前記駆動側回転体と前記従動側回転体とで形成された流体圧室を遅角室と進角室とに仕切るよう前記駆動側回転体及び前記従動側回転体の少なくとも一方に設けられた仕切部と、
前記仕切部のうち前記駆動側回転体もしくは前記従動側回転体に対向する位置、または、前記駆動側回転体もしくは前記従動側回転体のうち前記仕切部に対向する位置に配設されて、前記駆動側回転体と前記従動側回転体との相対回転に基づく前記遅角室と前記進角室との間での作動流体の漏洩を防止するシール部材と、
弾性変形に基づく付勢力によって、前記シール部材を前記仕切部の側から前記駆動側回転体もしくは前記従動側回転体の側へ、または、前記シール部材を前記駆動側回転体もしくは前記従動側回転体の側から前記仕切部の側へ付勢する付勢部材と、を備え、
前記付勢部材は、谷折り部と山折り部とを少なくとも1つずつ備えると共に、
前記付勢部材の一端部と該一端部の側に位置する前記谷折り部もしくは前記山折り部との間に形成され、前記シール部材に当接する一端側の当接部と、前記付勢部材の他端部と該他端部の側に位置する前記谷折り部もしくは前記山折り部との間に形成され、前記仕切部または前記駆動側回転体もしくは前記従動側回転体に当接する他端側の当接部と、を備え、
前記付勢部材の付勢に伴って、前記一端側の当接部と前記他端側の当接部との付勢方向における間隔が小さくなると共に、前記谷折り部および前記山折り部の角度が小さくなる弁開閉時期制御装置。 - 前記付勢部材は、前記一端側の当接部と前記他端側の当接部との間に非当接部を備え、
前記付勢部材の長手方向において、前記非当接部よりも前記一端側の当接部および前記他端側の当接部のほうが短い請求項1に記載の弁開閉時期制御装置。 - クランクシャフトに対して同期回転する駆動側回転体と、
前記駆動側回転体に対して同軸上に配置され、内燃機関の弁開閉用のカムシャフトに同期回転する従動側回転体と、
前記駆動側回転体と前記従動側回転体とで形成された流体圧室を遅角室と進角室とに仕切るよう前記駆動側回転体及び前記従動側回転体の少なくとも一方に設けられた仕切部と、
前記仕切部のうち前記駆動側回転体もしくは前記従動側回転体に対向する位置、または、前記駆動側回転体もしくは前記従動側回転体のうち前記仕切部に対向する位置に配設されて、前記駆動側回転体と前記従動側回転体との相対回転に基づく前記遅角室と前記進角室との間での作動流体の漏洩を防止するシール部材と、
弾性変形に基づく付勢力によって、前記シール部材を前記仕切部の側から前記駆動側回転体もしくは前記従動側回転体の側へ、または、前記シール部材を前記駆動側回転体もしくは前記従動側回転体の側から前記仕切部の側へ付勢する付勢部材と、を備え、
前記付勢部材は、谷折り部と山折り部とを少なくとも1つずつ備えると共に、
前記付勢部材の一端部と該一端部の側に位置する前記谷折り部もしくは前記山折り部との間、および、前記付勢部材の他端部と該他端部の側に位置する前記谷折り部もしくは前記山折り部との間に形成され、前記シール部材、または、前記仕切部または前記駆動側回転体もしくは前記従動側回転体に当接する両端側の当接部と、前記一端部の側に位置する前記谷折り部もしくは前記山折り部と前記他端部の側に位置する前記谷折り部もしくは前記山折り部との間に形成され、前記シール部材、または、前記仕切部または前記駆動側回転体もしくは前記従動側回転体のうち、前記両端側の当接部が当接した側とは反対側に位置する部材に当接する中間側の当接部と、を備え、
前記付勢部材の付勢に伴って、前記両端側の当接部と前記中間側の当接部との付勢方向における間隔が小さくなると共に、前記谷折り部および前記山折り部の角度が小さくなる弁開閉時期制御装置。 - 前記付勢部材は板バネ材であり、
前記当接部として、前記シール部材、または、前記仕切部または前記駆動側回転体もしくは前記従動側回転体に面接触する当接面を構成してある請求項1~3のいずれか1項に記載の弁開閉時期制御装置。
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CN201180050977.9A CN103210188B (zh) | 2010-10-22 | 2011-10-14 | 阀开闭定时控制装置 |
US13/880,913 US8915223B2 (en) | 2010-10-22 | 2011-10-14 | Valve timing control apparatus |
KR1020137012516A KR101455054B1 (ko) | 2010-10-22 | 2011-10-14 | 밸브 개폐 시기 제어 장치 |
EP20110834287 EP2631439B1 (en) | 2010-10-22 | 2011-10-14 | Device for controlling valve opening/closing timing |
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JP2010237784A JP5274533B2 (ja) | 2010-10-22 | 2010-10-22 | 弁開閉時期制御装置 |
JP2010-237784 | 2010-10-22 |
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US (1) | US8915223B2 (ja) |
EP (1) | EP2631439B1 (ja) |
JP (1) | JP5274533B2 (ja) |
KR (1) | KR101455054B1 (ja) |
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WO2012050913A1 (en) | 2010-09-28 | 2012-04-19 | The Ohio State University | Predictive network system and method |
DE102014208598B4 (de) | 2014-05-08 | 2020-10-29 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller mit zum Erreichen eines hydraulischen Freilaufs hin- und herschaltbarem Hydraulikkammerabdichtelement |
CN105736083A (zh) * | 2014-12-12 | 2016-07-06 | 舍弗勒技术股份两合公司 | 凸轮轴相位调节器 |
CN106285815A (zh) * | 2015-05-13 | 2017-01-04 | 舍弗勒技术股份两合公司 | 凸轮轴调节器 |
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- 2011-10-14 KR KR1020137012516A patent/KR101455054B1/ko active IP Right Grant
- 2011-10-14 WO PCT/JP2011/073685 patent/WO2012053447A1/ja active Application Filing
- 2011-10-14 US US13/880,913 patent/US8915223B2/en not_active Expired - Fee Related
- 2011-10-14 EP EP20110834287 patent/EP2631439B1/en not_active Not-in-force
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EP2631439B1 (en) | 2015-04-22 |
CN103210188A (zh) | 2013-07-17 |
US20130213327A1 (en) | 2013-08-22 |
KR20130100174A (ko) | 2013-09-09 |
EP2631439A1 (en) | 2013-08-28 |
EP2631439A4 (en) | 2013-11-27 |
JP5274533B2 (ja) | 2013-08-28 |
JP2012087764A (ja) | 2012-05-10 |
US8915223B2 (en) | 2014-12-23 |
CN103210188B (zh) | 2015-11-25 |
KR101455054B1 (ko) | 2014-11-04 |
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