US20090078222A1 - Valve timing control apparatus - Google Patents
Valve timing control apparatus Download PDFInfo
- Publication number
- US20090078222A1 US20090078222A1 US12/194,850 US19485008A US2009078222A1 US 20090078222 A1 US20090078222 A1 US 20090078222A1 US 19485008 A US19485008 A US 19485008A US 2009078222 A1 US2009078222 A1 US 2009078222A1
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- Prior art keywords
- valve
- advancing
- retarding
- passage
- chamber
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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
- 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
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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
-
- 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
- F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
- F01L2001/3444—Oil filters
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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
-
- 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
Definitions
- the present invention relates to a valve timing control apparatus, which controls opening and closing timing (hereinafter, simply referred to as valve timing) of at least one of an intake valve and an exhaust valve of an internal combustion engine.
- a previously known valve timing control apparatus includes a housing and a vane rotor (see, for example, Japanese Unexamined Patent Publication No. 2006-46315 corresponding to U.S. Pat. No. 7,182,052).
- the housing receives a drive force of a crankshaft of an internal combustion engine, and the vane rotor is received in the housing and transmits the drive force of the crankshaft to a camshaft.
- the vane rotor is rotated relative to the housing in a retarding direction or an advancing direction by controlling a pressure of hydraulic oil in retarding chambers and a pressure of hydraulic oil in advancing chambers, so that a phase of the camshaft relative to the crankshaft, i.e., valve timing is adjusted.
- the debris e.g., burrs detached from the interior of the internal combustion engine, abrasive powders generated by abrasion of slidable members
- the debris may possibly be clogged in the check valve to interfere the proper function of the check valve for blocking the flow of the hydraulic oil and thereby to disable the blocking of the outflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump unless the debris is reliably removed from the hydraulic oil.
- the present invention addresses the above disadvantages.
- a valve timing control apparatus that adjusts opening and closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine and is placed in a drive force transmission system, which transmits a drive force from a drive shaft of the internal combustion engine to a driven shaft that drives the at least one of the intake valve and the exhaust valve to open and close the same.
- the valve timing control apparatus includes a housing, a vane rotor, a phase change valve, a check valve and a filter. The housing is rotated together with one of the drive shaft and the driven shaft and has a receiving chamber, which is formed within a predetermined angular range in a rotational direction.
- the vane rotor is rotated together with the other one of the drive shaft and the driven shaft and has a vane, which is received in the receiving chamber to partition the receiving chamber into a retarding chamber and an advancing chamber.
- the vane rotor is rotated relative to the housing in a retarding direction or an advancing direction through use of a pressure of hydraulic fluid in the retarding chamber and a pressure of hydraulic fluid in the advancing chamber to control a relative phase of the vane rotor relative the housing.
- the phase change valve is changeable between an operational state for supplying hydraulic fluid from a fluid supply source to the retarding chamber and an operational state for discharging the hydraulic fluid from the retarding chamber and is also changeable between an operational state for supplying the hydraulic fluid from the fluid supply source to the advancing chamber and an operational state for discharging the hydraulic fluid from the advancing chamber.
- the check valve is provided in a fluid passage between the phase change valve and the fluid supply source. The check valve enables a flow of the hydraulic fluid from the fluid supply source to the retarding chamber or the advancing chamber and blocks a flow of the hydraulic fluid from the retarding chamber or the advancing chamber to a fluid supply source side.
- the filter is provided in the fluid passage between the check valve and the fluid supply source to remove debris from the hydraulic fluid before supplying of the hydraulic fluid to the check valve.
- FIG. 1 is a structural diagram showing a retarding control state of a valve timing control apparatus according to an embodiment of the present invention
- FIG. 2 is a cross sectional view taken along line II-II in FIG. 1 ;
- FIG. 3 is a structural diagram showing an advancing control state of the valve timing control apparatus according to the embodiment.
- FIG. 4A is a plan view of a check valve of the valve timing control apparatus
- FIG. 4B is a cross sectional view taken along line IVB-IVB in FIG. 4A ;
- FIG. 5 is a structural diagram showing the retarding control state of the valve timing control apparatus according to the embodiment.
- FIG. 6 is a structural diagram showing the advancing control state of the valve timing control apparatus according to the embodiment.
- FIG. 7 is a diagram illustrating a difference between response of the valve timing control apparatus having the check valve and a filter and a previously proposed valve timing control apparatus without the check valve and the filter.
- FIGS. 1 to 6 show a valve timing control apparatus according to an embodiment of the present invention.
- the valve timing control apparatus 1 of the present embodiment is of a hydraulically controlled type that uses hydraulic oil as working fluid (hydraulic fluid) and controls valve timing of intake valves.
- FIG. 1 shows an operational state, in which a vane rotor 30 is driven relative to a housing 10 in a retarding direction.
- FIG. 3 shows another operational state, in which the vane rotor 30 is driven relative to the housing 10 in an advancing direction.
- FIG. 5 shows a state, in which the vane rotor 30 is driven relative to the housing 10 in the retarding direction and in which a check valve limits a leak flow of the hydraulic oil from retarding chambers to a fluid supply source.
- FIG. 6 shows a state, in which the vane rotor 30 is driven relative to the housing 10 in the advancing direction and in which the check valve limits the leak flow of the hydraulic oil from advancing chambers to the fluid supply source.
- the valve timing control apparatus 1 of the present embodiment includes the housing 10 , the vane rotor 30 , a phase change valve 60 , a check valve 80 and a filter 52 .
- the housing 10 which serves as a driving-side rotator; includes a chain sprocket 11 and a shoe housing 12 .
- the shoe housing 12 includes a plurality of shoes 121 - 123 (see FIG. 2 ), annular peripheral wall 124 and a front plate 125 , which are formed integrally.
- the shoes 121 - 123 serve as partitioning members, respectively.
- the front plate 125 is located on the opposite side of the peripheral wall 124 , which is opposite from the chain sprocket 11 .
- the shoe housing 12 is coaxially fixed to the chain sprocket 11 with bolts 13 .
- the chain sprocket 11 is coupled with the undepicted crankshaft (serving as a drive shaft of the internal combustion engine) through an undepicted chain to receive a drive force therefrom and is thereby rotated together with the crankshaft.
- the drive force of the crankshaft is transmitted to a camshaft (serving as a driven shaft) 3 through the valve timing control apparatus 1 to drive the intake valves (not shown).
- the camshaft 3 is received in the chain sprocket 11 in such a manner that the camshaft 3 and the chain sprocket 11 are driven to rotate together by the drive force transmitted from the crankshaft to the chain sprocket 11 while the camshaft 3 is rotatable relative to the chain sprocket 11 within a predetermined range of a phase difference at the time of changing the phase difference of the camshaft 3 relative to the chain sprocket 11 and thereby to the crankshaft.
- the vane rotor (serving as a driven-side rotator) 30 contacts an axial end surface of the camshaft 3 .
- the camshaft 3 , the vane rotor 30 and a bush 14 are coaxially and securely joined together with a bolt 15 .
- the positioning between the vane rotor 30 and the camshaft 3 in the rotational direction is implemented by fitting a positioning pin 16 into the vane rotor 30 and the camshaft 3 .
- the camshaft 3 , the housing 10 and the vane rotor 30 are rotated in the clockwise direction when they are seen in a direction of an arrow X in FIG. 1 .
- this rotational direction will be referred to as an advancing direction of the camshaft 3 relative to the crankshaft.
- the shoes 121 - 123 each of which is formed into a trapezoidal shape, extend radially inward from the peripheral wall 124 and are placed one after another at generally equal intervals in the rotational direction of the peripheral wall 124 .
- the shoes 121 - 123 define three spaces, each of which extends a predetermined angular range in the rotational direction. These three spaces respectively form fan shaped receiving chambers 40 , which receive vanes 131 - 133 .
- the vane rotor 30 includes a boss 134 and the vanes 131 - 133 .
- the boss 134 is joined with the camshaft 3 at the axial end surface thereof.
- the vanes 131 - 133 are provided at the outer peripheral part of the boss 134 one after another at generally equal intervals in the rotational direction.
- the vane rotor 30 is received in the housing 10 in the rotatable manner relative to the housing 10 .
- the vanes 131 - 133 are rotatably received in the receiving chambers 40 , respectively.
- Each vane 131 - 133 divides, i.e., partitions the corresponding receiving chamber 40 into a retarding chamber and an advancing chamber. Arrows of FIG. 2 , which indicate a retarding direction and an advancing direction, respectively, show the retarding direction and the advancing direction of the vane rotor 30 relative to the housing 10 .
- Seal members 17 are provided in slide gaps, formed between the respective shoes 121 - 123 and the boss 134 and between the respective vanes 131 - 133 and the peripheral wall 124 .
- the seal members 17 are fitted into the grooves, which are provided in the outer peripheral wall of the boss 134 and in the outer peripheral wall of the respective vanes 131 - 133 .
- the seal members 17 are urged by, for example, springs, toward the inner peripheral wall of the respective shoes 121 - 123 and the inner peripheral wail of the peripheral wall 124 .
- the seal members 17 limit the leakage of the hydraulic oil between each retarding chamber and the adjacent advancing chamber.
- a cylindrical guide ring 18 is press fitted into a corresponding hole of the vane 131 .
- a cylindrical stopper pin 19 is axially slidably received in the guide ring 18 in the direction of the rotational axis.
- An engaging ring 20 is press fitted into and is held in a recess 126 , which is formed in the front plate 125 .
- the stopper pin 19 can be fitted, i.e., engaged into the engaging ring 20 .
- the engaging side of the stopper pin 19 and the engaging side of the engaging ring 20 which are engaged with each other, are tapered, so that the stopper pin 19 can be smoothly engaged into the engaging ring 20 .
- a spring 21 which serves as an urging means, urges the stopper pin 19 toward the engaging ring 20 side.
- the stopper pin 19 , the engaging ring 20 and the spring 21 form an arresting means for arresting the vane rotor 30 relative to the housing 10 .
- a hydraulic pressure chamber 22 is formed on a front plate 125 side of the stopper pin 19 , and a hydraulic pressure chamber 23 is formed at radially outward of the stopper pin 19 .
- the pressure of the hydraulic oil which is supplied to the hydraulic pressure chamber 22 and to the hydraulic pressure chamber 23 , acts in a direction of removing the stopper pin 19 from the engaging ring 20 .
- the hydraulic pressure chamber 22 is connected to an advancing chamber 45 described latter, and the hydraulic pressure chamber 23 is connected to a retarding chamber 41 described latter.
- a distal end portion of the stopper pin 19 is engageable with the engaging ring 20 when the vane rotor 30 is placed into a most retarded position relative to the housing 10 . In the state where the stopper pin 19 is engaged into the engaging ring 20 , the relative rotation of the vane rotor 30 relative to the housing 10 is arrested.
- the retarding chamber 41 is formed between the shoe 121 and the vane 131
- a retarding chamber 42 is formed between the shoe 122 and the vane 132
- a retarding chamber 43 is formed between the shoe 123 and the vane 133
- an advancing chamber 45 is formed between the shoe 123 and the vane 131
- an advancing chamber 46 is formed between the shoe 121 and the vane 132
- an advancing chamber 47 is formed between the shoe 122 and the vane 133 .
- an oil pump (a fluid supply source) 50 takes the hydraulic oil from an oil pan 51 and supplies it to a lubricating system of the internal combustion engine.
- a supply passage 203 supplies the hydraulic oil received from the oil pan 51 to the valve timing control apparatus 1 .
- One end of the supply passage 203 is connected to a connecting point 201 of a branch passage 205 , which supplies the hydraulic oil to the lubricating system of the internal combustion engine other than the valve timing control apparatus 1 .
- the other end of the supply passage 203 is connected to the filter 52 .
- the filter 52 is provided between the supply passage 203 and a supply passage 204 and includes a fine mesh 521 , which filters debris (foreign objects) contained in the hydraulic oil that is supplied only to the valve timing control apparatus 1 .
- One end of the supply passage 204 is connected to the filter 52 , and the other end of the supply passage 204 is connected to the check valve 80 .
- the check valve 80 is provided in the supply passages 204 , 207 located between the oil pump 50 and the phase change valve 60 .
- the check valve 80 includes a case 87 , guide 84 , a valve element 81 and a spring 83 .
- the case 87 has a valve passage 89 and a valve seat 82 .
- the valve passage 89 connects between the supply passage 204 and the supply passage 207 .
- the valve element 81 is seatable against the valve seat 82 .
- the valve element 81 is configured into a spherical body and is received in the valve passage 89 such that the valve element 81 is reciprocally movable in an axial direction of the case 87 .
- the spring 83 is a compression coil spring and is received in the valve passage 89 .
- One end of the spring 83 is in contact with the valve element 81
- the other end of the spring 83 is in contact with the guide 84 .
- the guide 84 is received in the valve passage 89 .
- a triple-forked portion 86 and a contacting portion 85 are formed integrally in the guide 84 .
- the triple-forked portion 86 holds the other end of the spring 83 .
- the contacting portion 85 guides movement of the valve element 81 .
- the valve element 81 is seated against the valve seat 82 to close the valve passage 89 when a sum of the hydraulic pressure of the hydraulic oil in the supply passage 207 and an urging force of the spring 83 per unit area is equal to or higher than the hydraulic pressure of the hydraulic oil in the supply passage 204 .
- the valve element 81 is lifted away from the valve seat 82 against the urging force of the spring 83 when the hydraulic pressure of the hydraulic oil in the supply passage 204 is larger than the sum of the hydraulic pressure of the hydraulic oil in the supply passage 207 and the urging force of the spring 83 per unit area.
- one end of the supply passage 207 is connected to the check valve 80 , and the other end of the supply passage 207 is connected to an opening 73 of the phase change valve 60 .
- the supply passages 203 , 204 , 207 are dedicated fluid passages, which supply the hydraulic oil only to the valve timing control apparatus 1 and are not connected to any other connecting point.
- One end of a discharge passage 208 is connected to an opening 74 of the phase change valve 60 , and the other end of the discharge passage 208 is connected to the oil pan 51 .
- One end of a discharge passage 206 ( FIG. 3 ) is connected to an opening 72 of the phase change valve 60 , and the other end of the discharge passage 206 is connected to the oil pan 51 .
- the discharge passages 208 , 206 are constructed to discharge the hydraulic oil to the oil pan 51 .
- the phase change valve 60 is a solenoid spool valve and is connected to the supply passage 207 , the discharge passages 206 , 208 , a retarding passage 210 and an advancing passage 220 . Also, the phase change valve 60 is located on an oil pump 50 side of a bearing 2 .
- a solenoid drive arrangement 61 of the phase change valve 60 includes a yoke 62 , a stationary core 63 , a movable core 64 and a coil 65 .
- the yoke 62 , the stationary core 63 and the movable core 64 are made of a magnetic material and form a magnetic circuit.
- the coil 65 When the coil 65 is energized, the coil 65 generates a magnetic flux, which passes through the magnetic circuit
- the coil 65 is electrically connected to an electronic control unit (ECU) 79 .
- the ECU 79 controls the energization of the coil 65 to change a magnetic attractive force, which is generated between the stationary core 63 and the movable core 64 , to drive the movable core 64 .
- a valve arrangement 66 of the phase change valve 60 includes a sleeve 67 and a spool 68 .
- the openings 70 - 74 are formed in predetermined locations of the sleeve 67 to conduct the hydraulic oil. More specifically the opening 73 is connected to the supply passage 207 , and the openings 72 , 74 are connected to the discharge passage 206 ( FIG. 3 ) and the discharge passage 208 , respectively. Furthermore, the opening 71 is connected to the retarding passage 210 , and the opening 70 is connected to the advancing passage 220 .
- the spool 68 is axially reciprocally movably supported by an inner peripheral wall of the sleeve 67 .
- Lands 75 , 76 of the spool 68 each of which has an outer diameter generally equal to an inner diameter of the sleeve 67 slidably engages the inner peripheral wall of the sleeve 67 .
- An end surface of the spool 68 which is opposite from the movable core 64 , contacts the spring 69 , which urges the spool 68 toward the movable core 64 side.
- FIG. 1 shows the off-state, in which the energization of the coil 65 is turned off by the ECU 79 .
- the spool 68 is urged by the spring 69 and is thereby held in the predetermined location at the left side in FIG. 1 .
- the hydraulic oil which is supplied from the oil pump 50 to the supply passages 203 , 204 , 207 , enters into the interior of the sleeve 67 through the opening 73 and is thereafter supplied to the retarding passage 210 through the opening 71 .
- the hydraulic oil of the advancing passage 220 enters into the interior of the sleeve 67 through the opening 70 and is thereafter discharged from the opening 74 to the oil pan 51 through the discharge passage 208 .
- FIG. 3 shows the on-state, in which the energization of the coil 65 is turned on by the ECU 79 and is controlled at a predetermined duty ratio.
- the spool 68 is urged against the urging force of the spring 69 toward the right side in FIG. 3 and is thereafter held in a balanced position, at which the urging force of the spring 69 and the magnetic attractive force between the cores 63 , 64 of the solenoid drive arrangement 61 are balanced.
- the hydraulic oil which is supplied from the oil pump 50 to the supply passages 203 , 204 , 207 , enters into the interior of the sleeve 67 through the opening 73 and is thereafter supplied to the advancing passage 220 through the opening 70 .
- the hydraulic oil of the retarding passage 210 enters into the interior of the sleeve 67 through the opening 71 and is thereafter discharged from the opening 72 to the oil pan 51 through the discharge passage 206 .
- the spool 68 is urged toward the right side in FIG. 3 by the amount less than that of FIG. 3 , so that the spool 68 is held in a corresponding balanced position, at which the urging force of the spring 69 and the electromagnetic force of the solenoid drive arrangement 61 are balanced.
- the hydraulic oil which is supplied from the oil pump 50 to the supply passages 203 , 204 , 207 , may enter into the interior of the sleeve 67 through the opening 73 .
- the openings 71 , 70 are respectively closed by the lands 75 , 76 , so that the flow of the above hydraulic oil to the retarding passage 210 and the advancing passage 220 is limited.
- annular passages 240 , 242 are formed in an outer peripheral wall of the camshaft 3 , which is supported by the bearing 2 of the valve timing control apparatus 1 .
- the retarding passage 210 extends from the phase change valve 60 to the interior of the boss 134 of the vane rotor 30 through the annular passage 240 and a retarding passage 211 of the interior of the camshaft 3 .
- the advancing passage 220 extends from the phase change valve 60 to the interior of the boss 134 of the vane rotor 30 through the annular passage 242 and an advancing passage 221 of the interior of the camshaft 3 .
- the retarding passage 211 is branched into three retarding passages 243 - 245 , which are connected to the retarding chambers 41 - 43 , respectively.
- the retarding passage 210 , the annular passage 240 and the retarding passages 211 , 243 - 245 supply the hydraulic oil to the respective retarding chambers 41 - 43 from the supply passage 204 through the phase change valve 60 and drain the hydraulic oil from the respective retarding chambers 41 - 43 to the oil pan 51 side (fluid discharge side) through the phase change valve 60 and the discharge passage 206 .
- the retarding passage 210 , the annular passage 240 and the retarding passages 211 , 243 - 245 serve as both a retarding side supply passage and a retarding side discharge passage.
- the advancing passage 221 is branched into three advancing passages 246 - 248 , which are connected to the advancing chambers 45 - 47 , respectively.
- the advancing passage 220 , the annular passage 242 and the advancing passages 221 , 246 - 248 supply the hydraulic oil to the respective advancing chambers 45 - 47 from the supply passage 204 through the phase change valve 60 and drain the hydraulic oil from the respective advancing chambers 45 - 47 to the oil pan 51 side (fluid discharge side) through the phase change valve 60 and the discharge passage 208 .
- the advancing passage 220 , the annular passage 242 and the advancing passages 221 , 246 - 248 serve as both an advancing side supply passage and an advancing side discharge passage.
- the check valve 80 which is provided between the supply passage 204 and the supply passage 207 , limits the backflow of the hydraulic oil from the respective retarding chambers 41 - 43 to the oil pump 50 side through the retarding passages 243 - 245 , 211 , the annular passage 240 , the retarding passage 210 and the supply passage 207 and also limits the backflow of the hydraulic oil from the respective advancing chambers 45 - 47 to the oil pump 50 side through the advancing passages 246 - 248 , 221 , the annular passage 242 , the advancing passage 220 and the supply passage 207 .
- the check valve 80 is provided in the supply passages 204 , 207 , which are located on the phase change valve 60 side of the connecting point 201 , the hydraulic oil, which tries to generate the backflow from the retarding chambers 41 - 43 or the advancing chambers 45 - 47 , does not flow to the lubricating system of the internal combustion engine other than the valve timing control apparatus 1 .
- the filter 52 is provided in the supply passages 203 , 204 , which are located on the check valve 80 side of the connecting point 201 .
- the filter 52 can remove the debris from the hydraulic oil.
- supply of the debris into the check valve 80 is limited. Therefore, the one-way valve function of the check valve 80 is not interfered, so that the flow of the hydraulic oil from the phase change valve 60 to the oil pump 50 can be reliably limited.
- the valve timing control apparatus 1 can make the appropriate response at the time of changing the phase to the advancing side or the retarding side regardless of the degree of the torque change.
- valve timing control apparatus 1 Next, the operation of the valve timing control apparatus 1 will be described with reference to FIGS. 1 and 3 .
- the stopper pin 19 In the stop state of the internal combustion engine, the stopper pin 19 is engaged into the engaging ring 20 . Right after starting of the internal combustion engine, sufficient hydraulic oil is not supplied from the oil pump 50 to the retarding chambers 41 - 43 , the advancing chambers 45 - 47 and the hydraulic pressure chambers 22 , 23 . Thus, the stopper pin 19 is still engaged into the engaging ring 20 , and the camshaft 3 is held in the most retarded position relative to the crankshaft. Therefore, the vane rotor 30 is repeatedly circumferentially swung back and forth to repeatedly hit the housing 10 , resulting in generation of hammering sound due to the torque fluctuations received by the camshaft until the hydraulic oil is supplied to the respective hydraulic chambers.
- the stopper pin 19 is removed from the engaging ring 20 by the hydraulic pressure of the hydraulic oil supplied to the hydraulic pressure chamber 22 or the hydraulic pressure chamber 23 . Thereby, the rotor 30 can now rotate relative to the housing 10 .
- the phase difference of the camshaft 3 relative to the crankshaft is adjusted by controlling the hydraulic pressure applied to the respective retarding chambers and the hydraulic pressure applied to the respective advancing chambers.
- the spool 68 is held in the position shown in FIG. 1 by the load of the spring 69 .
- the hydraulic oil which is discharged from the oil pump 50 , passes through the connecting point 201 and the supply passage 203 and is supplied to the filter 52 .
- the filter 52 removes the debris mixed into the hydraulic oil.
- the hydraulic oil, from which the debris is removed, is supplied from the supply passage 204 to the valve passage 89 of the check valve 80 and then passes through the supply passage 207 . Thereafter, the hydraulic oil is supplied from the supply passage 207 to the interior of the sleeve 67 through the opening 73 of the phase change valve 60 .
- the check valve 80 enables the flow of the hydraulic oil.
- the hydraulic oil which is outputted from the opening 71 of the phase change valve 60 , passes through the retarding passage 210 , the annular passage 240 and the retarding passages 211 , 243 - 245 and is supplied into the retarding chambers 41 - 43 . Furthermore, the hydraulic oil of the advancing chambers passes the advancing passages 246 - 248 , 221 , the annular passage 242 , the advancing passage 220 , the phase change valve 60 and the discharge passage 208 and is discharged into the oil pan 51 . Thereby, the hydraulic oil is supplied to the respective retarding chambers, and the hydraulic oil is discharged from the respective advancing chambers. In this way, the vane rotor 30 receives the hydraulic pressure from the three retarding chambers 41 - 43 , so that the vane rotor 30 is rotated relative to the housing 10 in the retarding direction.
- the spool 68 When the electric power supply to the phase change valve 60 is turned on, the spool 68 is moved to the position show in FIG. 3 by the electromagnetic force of the solenoid drive arrangement 61 , which is exerted against the load of the spring 69 .
- the hydraulic oil which is discharged from the oil pump 50 , passes through the connecting point 201 and the supply passage 203 and is supplied to the filter 52 .
- the filter 52 removes the debris mixed into the hydraulic oil.
- the hydraulic oil, from which the debris is removed, is supplied from the supply passage 204 to the valve passage 89 of the check valve 80 and then passes through the supply passage 207 .
- the hydraulic oil is supplied from the supply passage 207 to the interior of the sleeve 67 through the opening 73 of the phase change valve 60 .
- the hydraulic oil which is outputted from the opening 70 of the phase change valve 60 , passes through the advancing passage 220 , the annular passage 242 and the advancing passages 221 , 246 - 248 and is supplied into the advancing chambers 45 - 47 .
- the hydraulic oil of the retarding chambers passes the retarding passages 243 - 245 , 211 , the annular passage 240 , the retarding passage 210 , the phase change valve 60 and the discharge passage 206 and is discharged into the oil pan 51 .
- the hydraulic oil is supplied to the respective advancing chambers, and the hydraulic oil is discharged from the respective retarding chambers.
- the vane rotor 30 receives the hydraulic pressure from the three advancing chambers 45 - 47 , so that the vane rotor 30 is rotated relative to the housing 10 in the advancing direction.
- the ECU 79 controls the duty ratio of the drive current supplied to the phase change valve 60 to hold the spool 68 in an intermediate position between the position of FIG. 1 and the position of FIG. 3 .
- the hydraulic oil which is supplied from the oil pump 50 through the supply passage 207 , passes the gaps, each of which is formed between the corresponding one of the lands 75 , 76 and the corresponding one of the openings 71 , 70 , so that the small amount of hydraulic oil is supplied to both of the retarding passage 210 and the advancing passage 220 to apply the pressure.
- valve timing control apparatus 1 of the present embodiment will be described with reference to FIGS. 5 and 6 .
- the vane rotor 30 receives the torque changes (torque fluctuation) toward the retarding side and the advancing side with respect to the housing 10 due to the torque changes (torque fluctuation) applied to the camshaft 3 .
- the hydraulic oil in the respective retarding chambers receives the force to drive the hydraulic oil out of the retarding chambers toward the retarding passages 243 - 245 , 211 , the annular passage 240 , the retarding passage 210 and the supply passage 207 .
- the check valve 80 is provided between the supply passage 207 and the supply passage 204 . Therefore, the check valve 80 closes the valve passage 89 when the sum of the hydraulic pressure of the hydraulic oil, which is applied from the respective retarding chambers to the retarding passages 243 - 245 , 211 , the annular passage 240 , the retarding passage 210 and the supply passage 207 , and the urging force of the spring 83 per unit area is larger than the hydraulic pressure of the hydraulic oil discharged from the oil pump 50 .
- the hydraulic fluid does not flow out of the respective retarding chambers to the retarding passages 243 - 245 , 211 , the annular passage 240 , the retarding passage 210 and the supply passage 207 .
- the filter 52 is provided in the supply passages 203 , 204 on the check valve 80 side of the connecting point 201 to limit the inflow of the debris of the hydraulic oil into the check valve 80 . Therefore, the check valve 80 can reliably limit the backflow of the hydraulic oil. Therefore, in the state where the hydraulic pressure of the oil pump 50 is low, even when the vane rotor 30 receives the torque change toward the advancing side, the check valve 80 can limit the returning of the vane rotor 30 toward the advancing side relative to the housing 10 . As described above, it is possible to limit the returning of the vane rotor 30 relative to the housing 10 toward the advancing side, which is opposite from the target phase. Thus, the vane rotor 30 can quickly reach the target phase at the retarding side.
- the vane rotor 30 receives the torque changes (torque fluctuation) toward the retarding side and the advancing side with respect to the housing 10 due to the torque changes (torque fluctuation) applied to the camshaft 3 .
- the hydraulic oil in the respective advancing chambers receives the force to drive the hydraulic oil out of the advancing chambers toward the advancing passages 246 - 248 , 221 , the annular passage 242 , the advancing passage 220 and the supply passage 207 .
- the check valve 80 is provided between the supply passage 207 and the supply passage 204 . Therefore, the check valve 80 closes the valve passage 89 when the sum of the hydraulic pressure of the hydraulic oil, which is applied from the respective advancing chambers to the advancing passages 246 - 248 , 221 , the annular passage 242 , the advancing passage 220 and the supply passage 207 , and the urging force of the spring 83 per unit area is larger than the hydraulic pressure of the hydraulic oil discharged from the oil pump 50 .
- the hydraulic oil in the respective advancing chambers do not flow out of the advancing chambers toward the advancing passages 246 - 248 , 221 , the annular passage 242 , the advancing passage 220 and the supply passage 207 .
- the filter 52 is provided in the supply passages 203 , 204 on the check valve 80 side of the connecting point 201 to limit inflow of the debris of the hydraulic oil into the check valve 80 . Therefore, the check valve 80 can reliably limit the backflow of the hydraulic oil. Therefore, in the state where the hydraulic pressure of the oil pump 50 is low, even when the vane rotor 30 receives the torque change toward the retarding side, the check valve 80 can limit the returning of the vane rotor 30 toward the retarding side relative to the housing 10 . As described above, it is possible to limit the returning of the vane rotor 30 relative to the housing 10 toward the retarding side, which is opposite from the target phase. Thus, the vane rotor 30 can quickly reach the target phase at the advancing side.
- the check valve 80 closes the valve passage 89 upon seating of the valve element 81 against the valve seat 82 when the sum of the hydraulic pressure of the hydraulic oil in the supply passage 207 and the urging force of the spring 83 per unit area becomes equal to or larger than the hydraulic pressure of the hydraulic oil discharged from the oil pump 50 .
- the retarding passage 210 and the advancing passage 220 are both closed, and thereby the backflow of the hydraulic oil from the respective retarding chambers and the respective advancing chambers toward the oil pump 50 side through the retarding passage 210 , the advancing passage 220 and the supply passage 207 is limited.
- valve timing control apparatus 1 of the present embodiment the response of the valve timing control apparatus 1 of the present embodiment at the time of controlling the phase will be compared with that of a previously proposed valve timing control apparatus based on FIG. 7 .
- the check valve 80 and the filter 52 reliably block the backflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump to implement the appropriate phase control operation.
- the amount of return movement b of the vane rotor toward the retarding side caused by the torque change is relatively small, and the vane rotor reaches the target phase within the predetermined time period.
- the check valve and the filter are provided to reliably block the backflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump and thereby to improve the response in the phase control operation regardless of the degree of the torque change.
- the present invention is implemented in the valve timing control apparatus of the intake valves.
- the present invention may be applied to a valve timing control apparatus, which controls the exhaust valves or both of the intake valves and the exhaust valves.
- phase change valve of the solenoid spool valve type is used.
- a phase change valve of any other type may be used as long as the hydraulic oil from the oil pump can be switched to supply it to the retarding passage or the advancing passage while the hydraulic oil from the retarding passage or the advancing passage can be switched to discharge it into the discharge passage.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A check valve is provided in a fluid passage between a phase change valve and a fluid supply source. The check valve enables a flow of the hydraulic fluid from the fluid supply source to a retarding chamber or an advancing chamber defined in a housing in corporation with a vane rotor received therein. The check valve blocks a flow of the hydraulic fluid from the retarding chamber or the advancing chamber to a fluid supply source side. A filter is provided in the fluid passage between the check valve and the fluid supply source to remove debris from the hydraulic fluid before supplying of the hydraulic fluid to the check valve.
Description
- This application is based on and incorporates herein by reference Japanese Patent Application No. 2007-243509 filed on Sep. 20, 2007.
- 1. Field of the Invention
- The present invention relates to a valve timing control apparatus, which controls opening and closing timing (hereinafter, simply referred to as valve timing) of at least one of an intake valve and an exhaust valve of an internal combustion engine.
- 2. Description of Related Art
- A previously known valve timing control apparatus includes a housing and a vane rotor (see, for example, Japanese Unexamined Patent Publication No. 2006-46315 corresponding to U.S. Pat. No. 7,182,052). The housing receives a drive force of a crankshaft of an internal combustion engine, and the vane rotor is received in the housing and transmits the drive force of the crankshaft to a camshaft. The vane rotor is rotated relative to the housing in a retarding direction or an advancing direction by controlling a pressure of hydraulic oil in retarding chambers and a pressure of hydraulic oil in advancing chambers, so that a phase of the camshaft relative to the crankshaft, i.e., valve timing is adjusted.
- When intake valves or exhaust valves are driven to open and close by the valve timing control apparatus, fluctuating forces applied from the intake valves or the exhaust valves are conducted to the vane rotor, so that the torque change (torque fluctuation) is exerted in the vane rotor relative to the housing.
- In a case where the hydraulic oil is supplied to the advancing chambers to change the phase of the camshaft relative to the crankshaft from the retarding side to a target phase on the advancing side, when the torque change is applied to the vane rotor toward the retarding side, the vane rotor receives the torque change in a direction for reducing a volume of each advancing chamber. Thus, the hydraulic oil in each advancing chamber receives the force, which drives the hydraulic oil out of the advancing chamber. Then, the vane rotor is returned to the retarding side by the torque change, and thereby a response time period, which is required to reach the target phase, is disadvantageously lengthened. This disadvantage becomes particularly prominent when the pressure of the hydraulic oil supplied from the oil pump is low.
- In view of the above disadvantage, it has been studied to provide a check valve in an oil passage extending from a phase change valve, which supplies the hydraulic oil, to the retarding chambers and the advancing chambers to block the outflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump even upon application of the torque change to the vane rotor. However, when the check valve is provided in the oil passage extending from the phase change valve to the retarding chambers and the advancing chambers, it is required to provide an oil passage and a change valve for discharging the hydraulic oil from the retarding chambers and the advancing chambers. Therefore, the construction of the oil passages becomes complicated.
- Furthermore, it is conceivable to provide a check valve in an oil passage, which is present between the phase change valve and the oil pump to provide the hydraulic oil to the retarding chambers and the advancing chambers, to block the outflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump even upon application of the torque change to the vane rotor, like in the case of Japanese Unexamined Patent Publication No. 2004-100523.
- However, when debris (e.g., burrs detached from the interior of the internal combustion engine, abrasive powders generated by abrasion of slidable members) is mixed into the hydraulic oil, the debris may possibly be clogged in the check valve to interfere the proper function of the check valve for blocking the flow of the hydraulic oil and thereby to disable the blocking of the outflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump unless the debris is reliably removed from the hydraulic oil.
- The present invention addresses the above disadvantages. Thus, it is an objective of the present invention to provide a valve timing control apparatus, which has a check valve and limits intrusion of debris mixed in hydraulic fluid into the check valve while implementing relatively good response in a phase control operation toward an advancing side or a retarding side regardless of a degree of torque change.
- To achieve the objective of the present invention, there is provided a valve timing control apparatus that adjusts opening and closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine and is placed in a drive force transmission system, which transmits a drive force from a drive shaft of the internal combustion engine to a driven shaft that drives the at least one of the intake valve and the exhaust valve to open and close the same. The valve timing control apparatus includes a housing, a vane rotor, a phase change valve, a check valve and a filter. The housing is rotated together with one of the drive shaft and the driven shaft and has a receiving chamber, which is formed within a predetermined angular range in a rotational direction. The vane rotor is rotated together with the other one of the drive shaft and the driven shaft and has a vane, which is received in the receiving chamber to partition the receiving chamber into a retarding chamber and an advancing chamber. The vane rotor is rotated relative to the housing in a retarding direction or an advancing direction through use of a pressure of hydraulic fluid in the retarding chamber and a pressure of hydraulic fluid in the advancing chamber to control a relative phase of the vane rotor relative the housing. The phase change valve is changeable between an operational state for supplying hydraulic fluid from a fluid supply source to the retarding chamber and an operational state for discharging the hydraulic fluid from the retarding chamber and is also changeable between an operational state for supplying the hydraulic fluid from the fluid supply source to the advancing chamber and an operational state for discharging the hydraulic fluid from the advancing chamber. The check valve is provided in a fluid passage between the phase change valve and the fluid supply source. The check valve enables a flow of the hydraulic fluid from the fluid supply source to the retarding chamber or the advancing chamber and blocks a flow of the hydraulic fluid from the retarding chamber or the advancing chamber to a fluid supply source side. The filter is provided in the fluid passage between the check valve and the fluid supply source to remove debris from the hydraulic fluid before supplying of the hydraulic fluid to the check valve.
- The invention, together with additional objectives, features and advantages thereof, will be best understood from the following description, the appended claims and the accompanying drawings in which:
-
FIG. 1 is a structural diagram showing a retarding control state of a valve timing control apparatus according to an embodiment of the present invention; -
FIG. 2 is a cross sectional view taken along line II-II inFIG. 1 ; -
FIG. 3 is a structural diagram showing an advancing control state of the valve timing control apparatus according to the embodiment; -
FIG. 4A is a plan view of a check valve of the valve timing control apparatus; -
FIG. 4B is a cross sectional view taken along line IVB-IVB inFIG. 4A ; -
FIG. 5 is a structural diagram showing the retarding control state of the valve timing control apparatus according to the embodiment; -
FIG. 6 is a structural diagram showing the advancing control state of the valve timing control apparatus according to the embodiment; and -
FIG. 7 is a diagram illustrating a difference between response of the valve timing control apparatus having the check valve and a filter and a previously proposed valve timing control apparatus without the check valve and the filter. -
FIGS. 1 to 6 show a valve timing control apparatus according to an embodiment of the present invention. The valvetiming control apparatus 1 of the present embodiment is of a hydraulically controlled type that uses hydraulic oil as working fluid (hydraulic fluid) and controls valve timing of intake valves.FIG. 1 shows an operational state, in which avane rotor 30 is driven relative to ahousing 10 in a retarding direction.FIG. 3 shows another operational state, in which thevane rotor 30 is driven relative to thehousing 10 in an advancing direction.FIG. 5 shows a state, in which thevane rotor 30 is driven relative to thehousing 10 in the retarding direction and in which a check valve limits a leak flow of the hydraulic oil from retarding chambers to a fluid supply source.FIG. 6 shows a state, in which thevane rotor 30 is driven relative to thehousing 10 in the advancing direction and in which the check valve limits the leak flow of the hydraulic oil from advancing chambers to the fluid supply source. - First, the mechanical structure of the valve
timing control apparatus 1 will be described with reference toFIGS. 1 and 2 . The valvetiming control apparatus 1 of the present embodiment includes thehousing 10, thevane rotor 30, aphase change valve 60, acheck valve 80 and afilter 52. As shown inFIG. 1 , thehousing 10, which serves as a driving-side rotator; includes achain sprocket 11 and ashoe housing 12. Theshoe housing 12 includes a plurality of shoes 121-123 (seeFIG. 2 ), annularperipheral wall 124 and afront plate 125, which are formed integrally. The shoes 121-123 serve as partitioning members, respectively. Thefront plate 125 is located on the opposite side of theperipheral wall 124, which is opposite from thechain sprocket 11. Theshoe housing 12 is coaxially fixed to thechain sprocket 11 withbolts 13. Thechain sprocket 11 is coupled with the undepicted crankshaft (serving as a drive shaft of the internal combustion engine) through an undepicted chain to receive a drive force therefrom and is thereby rotated together with the crankshaft. - The drive force of the crankshaft is transmitted to a camshaft (serving as a driven shaft) 3 through the valve
timing control apparatus 1 to drive the intake valves (not shown). Thecamshaft 3 is received in thechain sprocket 11 in such a manner that thecamshaft 3 and thechain sprocket 11 are driven to rotate together by the drive force transmitted from the crankshaft to thechain sprocket 11 while thecamshaft 3 is rotatable relative to thechain sprocket 11 within a predetermined range of a phase difference at the time of changing the phase difference of thecamshaft 3 relative to thechain sprocket 11 and thereby to the crankshaft. - The vane rotor (serving as a driven-side rotator) 30 contacts an axial end surface of the
camshaft 3. Thecamshaft 3, thevane rotor 30 and abush 14 are coaxially and securely joined together with abolt 15. The positioning between thevane rotor 30 and thecamshaft 3 in the rotational direction is implemented by fitting apositioning pin 16 into thevane rotor 30 and thecamshaft 3. Thecamshaft 3, thehousing 10 and thevane rotor 30 are rotated in the clockwise direction when they are seen in a direction of an arrow X inFIG. 1 . Hereinafter, this rotational direction will be referred to as an advancing direction of thecamshaft 3 relative to the crankshaft. - As shown in
FIG. 2 , the shoes 121-123, each of which is formed into a trapezoidal shape, extend radially inward from theperipheral wall 124 and are placed one after another at generally equal intervals in the rotational direction of theperipheral wall 124. The shoes 121-123 define three spaces, each of which extends a predetermined angular range in the rotational direction. These three spaces respectively form fan shaped receivingchambers 40, which receive vanes 131-133. - The
vane rotor 30 includes aboss 134 and the vanes 131-133. Theboss 134 is joined with thecamshaft 3 at the axial end surface thereof. The vanes 131-133 are provided at the outer peripheral part of theboss 134 one after another at generally equal intervals in the rotational direction. Thevane rotor 30 is received in thehousing 10 in the rotatable manner relative to thehousing 10. The vanes 131-133 are rotatably received in the receivingchambers 40, respectively. Each vane 131-133 divides, i.e., partitions the corresponding receivingchamber 40 into a retarding chamber and an advancing chamber. Arrows ofFIG. 2 , which indicate a retarding direction and an advancing direction, respectively, show the retarding direction and the advancing direction of thevane rotor 30 relative to thehousing 10. -
Seal members 17 are provided in slide gaps, formed between the respective shoes 121-123 and theboss 134 and between the respective vanes 131-133 and theperipheral wall 124. Theseal members 17 are fitted into the grooves, which are provided in the outer peripheral wall of theboss 134 and in the outer peripheral wall of the respective vanes 131-133. Furthermore, theseal members 17 are urged by, for example, springs, toward the inner peripheral wall of the respective shoes 121-123 and the inner peripheral wail of theperipheral wall 124. With the above construction, theseal members 17 limit the leakage of the hydraulic oil between each retarding chamber and the adjacent advancing chamber. - As shown in
FIG. 1 , acylindrical guide ring 18 is press fitted into a corresponding hole of thevane 131. Acylindrical stopper pin 19 is axially slidably received in theguide ring 18 in the direction of the rotational axis. An engagingring 20 is press fitted into and is held in arecess 126, which is formed in thefront plate 125. Thestopper pin 19 can be fitted, i.e., engaged into the engagingring 20. The engaging side of thestopper pin 19 and the engaging side of the engagingring 20, which are engaged with each other, are tapered, so that thestopper pin 19 can be smoothly engaged into the engagingring 20. Aspring 21, which serves as an urging means, urges thestopper pin 19 toward the engagingring 20 side. Thestopper pin 19, the engagingring 20 and thespring 21 form an arresting means for arresting thevane rotor 30 relative to thehousing 10. - A
hydraulic pressure chamber 22 is formed on afront plate 125 side of thestopper pin 19, and ahydraulic pressure chamber 23 is formed at radially outward of thestopper pin 19. The pressure of the hydraulic oil, which is supplied to thehydraulic pressure chamber 22 and to thehydraulic pressure chamber 23, acts in a direction of removing thestopper pin 19 from the engagingring 20. Thehydraulic pressure chamber 22 is connected to an advancingchamber 45 described latter, and thehydraulic pressure chamber 23 is connected to a retardingchamber 41 described latter. A distal end portion of thestopper pin 19 is engageable with the engagingring 20 when thevane rotor 30 is placed into a most retarded position relative to thehousing 10. In the state where thestopper pin 19 is engaged into the engagingring 20, the relative rotation of thevane rotor 30 relative to thehousing 10 is arrested. - When the
vane rotor 30 is rotated from the most retarded position toward the advancing side, thestopper pin 19 and the engagingring 20 are displaced from each other in the rotational direction, so that thestopper pin 19 cannot be engaged into the engagingring 20. - As shown in
FIG. 2 , the retardingchamber 41 is formed between theshoe 121 and thevane 131, and a retardingchamber 42 is formed between theshoe 122 and thevane 132. Furthermore, a retardingchamber 43 is formed between theshoe 123 and thevane 133. Furthermore, an advancingchamber 45 is formed between theshoe 123 and thevane 131, and an advancingchamber 46 is formed between theshoe 121 and thevane 132. Also, an advancingchamber 47 is formed between theshoe 122 and thevane 133. - Next, the construction of the oil passages of the valve
timing control apparatus 1 will be described with reference toFIGS. 1 to 4 . - As shown in
FIG. 1 , an oil pump (a fluid supply source) 50 takes the hydraulic oil from anoil pan 51 and supplies it to a lubricating system of the internal combustion engine. Asupply passage 203 supplies the hydraulic oil received from theoil pan 51 to the valvetiming control apparatus 1. One end of thesupply passage 203 is connected to a connectingpoint 201 of abranch passage 205, which supplies the hydraulic oil to the lubricating system of the internal combustion engine other than the valvetiming control apparatus 1. The other end of thesupply passage 203 is connected to thefilter 52. Thefilter 52 is provided between thesupply passage 203 and asupply passage 204 and includes afine mesh 521, which filters debris (foreign objects) contained in the hydraulic oil that is supplied only to the valvetiming control apparatus 1. One end of thesupply passage 204 is connected to thefilter 52, and the other end of thesupply passage 204 is connected to thecheck valve 80. - The
check valve 80 is provided in thesupply passages oil pump 50 and thephase change valve 60. As shown inFIGS. 4A and 4B , thecheck valve 80 includes acase 87, guide 84, avalve element 81 and aspring 83. Thecase 87 has avalve passage 89 and avalve seat 82. Thevalve passage 89 connects between thesupply passage 204 and thesupply passage 207. Thevalve element 81 is seatable against thevalve seat 82. Thevalve element 81 is configured into a spherical body and is received in thevalve passage 89 such that thevalve element 81 is reciprocally movable in an axial direction of thecase 87. Thespring 83 is a compression coil spring and is received in thevalve passage 89. One end of thespring 83 is in contact with thevalve element 81, and the other end of thespring 83 is in contact with theguide 84. Theguide 84 is received in thevalve passage 89. A triple-forkedportion 86 and a contactingportion 85 are formed integrally in theguide 84. The triple-forkedportion 86 holds the other end of thespring 83. The contactingportion 85 guides movement of thevalve element 81. - In the
check valve 80, as indicated by a solid line inFIG. 4B , thevalve element 81 is seated against thevalve seat 82 to close thevalve passage 89 when a sum of the hydraulic pressure of the hydraulic oil in thesupply passage 207 and an urging force of thespring 83 per unit area is equal to or higher than the hydraulic pressure of the hydraulic oil in thesupply passage 204. In contrast, as indicated by a dot-dot-dash line inFIG. 4B , thevalve element 81 is lifted away from thevalve seat 82 against the urging force of thespring 83 when the hydraulic pressure of the hydraulic oil in thesupply passage 204 is larger than the sum of the hydraulic pressure of the hydraulic oil in thesupply passage 207 and the urging force of thespring 83 per unit area. - As shown in
FIG. 1 , one end of thesupply passage 207 is connected to thecheck valve 80, and the other end of thesupply passage 207 is connected to anopening 73 of thephase change valve 60. Thesupply passages timing control apparatus 1 and are not connected to any other connecting point. - One end of a
discharge passage 208 is connected to anopening 74 of thephase change valve 60, and the other end of thedischarge passage 208 is connected to theoil pan 51. One end of a discharge passage 206 (FIG. 3 ) is connected to anopening 72 of thephase change valve 60, and the other end of thedischarge passage 206 is connected to theoil pan 51. Thedischarge passages oil pan 51. - The
phase change valve 60 is a solenoid spool valve and is connected to thesupply passage 207, thedischarge passages retarding passage 210 and an advancingpassage 220. Also, thephase change valve 60 is located on anoil pump 50 side of abearing 2. Asolenoid drive arrangement 61 of thephase change valve 60 includes ayoke 62, astationary core 63, amovable core 64 and acoil 65. Theyoke 62, thestationary core 63 and themovable core 64 are made of a magnetic material and form a magnetic circuit. When thecoil 65 is energized, thecoil 65 generates a magnetic flux, which passes through the magnetic circuit Thecoil 65 is electrically connected to an electronic control unit (ECU) 79. TheECU 79 controls the energization of thecoil 65 to change a magnetic attractive force, which is generated between thestationary core 63 and themovable core 64, to drive themovable core 64. - A
valve arrangement 66 of thephase change valve 60 includes asleeve 67 and aspool 68. The openings 70-74 are formed in predetermined locations of thesleeve 67 to conduct the hydraulic oil. More specifically theopening 73 is connected to thesupply passage 207, and theopenings FIG. 3 ) and thedischarge passage 208, respectively. Furthermore, theopening 71 is connected to theretarding passage 210, and theopening 70 is connected to the advancingpassage 220. Thespool 68 is axially reciprocally movably supported by an inner peripheral wall of thesleeve 67.Lands spool 68, each of which has an outer diameter generally equal to an inner diameter of thesleeve 67 slidably engages the inner peripheral wall of thesleeve 67. An end surface of thespool 68, which is opposite from themovable core 64, contacts thespring 69, which urges thespool 68 toward themovable core 64 side. Thus, when thesolenoid drive arrangement 61 reciprocally drives themovable core 64, thespool 68 reciprocates in thesleeve 67. Thespool 68 is electromagnetically driven through the energization of thecoil 65 of thesolenoid drive arrangement 61. -
FIG. 1 shows the off-state, in which the energization of thecoil 65 is turned off by theECU 79. In this state, thespool 68 is urged by thespring 69 and is thereby held in the predetermined location at the left side inFIG. 1 . In this way, the hydraulic oil, which is supplied from theoil pump 50 to thesupply passages sleeve 67 through theopening 73 and is thereafter supplied to theretarding passage 210 through theopening 71. Furthermore, the hydraulic oil of the advancingpassage 220 enters into the interior of thesleeve 67 through theopening 70 and is thereafter discharged from theopening 74 to theoil pan 51 through thedischarge passage 208. -
FIG. 3 shows the on-state, in which the energization of thecoil 65 is turned on by theECU 79 and is controlled at a predetermined duty ratio. In this state, thespool 68 is urged against the urging force of thespring 69 toward the right side inFIG. 3 and is thereafter held in a balanced position, at which the urging force of thespring 69 and the magnetic attractive force between thecores solenoid drive arrangement 61 are balanced. In this way, the hydraulic oil, which is supplied from theoil pump 50 to thesupply passages sleeve 67 through theopening 73 and is thereafter supplied to the advancingpassage 220 through theopening 70. Furthermore, the hydraulic oil of theretarding passage 210 enters into the interior of thesleeve 67 through theopening 71 and is thereafter discharged from theopening 72 to theoil pan 51 through thedischarge passage 206. - In another state, in which the energization of the
coil 65 is turned on by theECU 79 and is controlled at a different duty ratio that is different from that ofFIG. 3 , thespool 68 is urged toward the right side inFIG. 3 by the amount less than that ofFIG. 3 , so that thespool 68 is held in a corresponding balanced position, at which the urging force of thespring 69 and the electromagnetic force of thesolenoid drive arrangement 61 are balanced. In this way, the hydraulic oil, which is supplied from theoil pump 50 to thesupply passages sleeve 67 through theopening 73. However, at this time, theopenings lands retarding passage 210 and the advancingpassage 220 is limited. - As shown in
FIG. 1 ,annular passages camshaft 3, which is supported by thebearing 2 of the valvetiming control apparatus 1. Theretarding passage 210 extends from thephase change valve 60 to the interior of theboss 134 of thevane rotor 30 through theannular passage 240 and aretarding passage 211 of the interior of thecamshaft 3. Furthermore, the advancingpassage 220 extends from thephase change valve 60 to the interior of theboss 134 of thevane rotor 30 through theannular passage 242 and an advancingpassage 221 of the interior of thecamshaft 3. - With reference to
FIG. 2 , theretarding passage 211 is branched into three retarding passages 243-245, which are connected to the retarding chambers 41-43, respectively. Theretarding passage 210, theannular passage 240 and the retardingpassages 211, 243-245 supply the hydraulic oil to the respective retarding chambers 41-43 from thesupply passage 204 through thephase change valve 60 and drain the hydraulic oil from the respective retarding chambers 41-43 to theoil pan 51 side (fluid discharge side) through thephase change valve 60 and thedischarge passage 206. Thus, theretarding passage 210, theannular passage 240 and the retardingpassages 211, 243-245 serve as both a retarding side supply passage and a retarding side discharge passage. - The advancing
passage 221 is branched into three advancing passages 246-248, which are connected to the advancing chambers 45-47, respectively. The advancingpassage 220, theannular passage 242 and the advancingpassages 221, 246-248 supply the hydraulic oil to the respective advancing chambers 45-47 from thesupply passage 204 through thephase change valve 60 and drain the hydraulic oil from the respective advancing chambers 45-47 to theoil pan 51 side (fluid discharge side) through thephase change valve 60 and thedischarge passage 208. Thus, the advancingpassage 220, theannular passage 242 and the advancingpassages 221, 246-248 serve as both an advancing side supply passage and an advancing side discharge passage. - Because of the above mechanical construction and the oil passages of the valve
timing control apparatus 1, thecheck valve 80, which is provided between thesupply passage 204 and thesupply passage 207, limits the backflow of the hydraulic oil from the respective retarding chambers 41-43 to theoil pump 50 side through the retarding passages 243-245, 211, theannular passage 240, theretarding passage 210 and thesupply passage 207 and also limits the backflow of the hydraulic oil from the respective advancing chambers 45-47 to theoil pump 50 side through the advancing passages 246-248, 221, theannular passage 242, the advancingpassage 220 and thesupply passage 207. Furthermore, since thecheck valve 80 is provided in thesupply passages phase change valve 60 side of the connectingpoint 201, the hydraulic oil, which tries to generate the backflow from the retarding chambers 41-43 or the advancing chambers 45-47, does not flow to the lubricating system of the internal combustion engine other than the valvetiming control apparatus 1. - The
filter 52 is provided in thesupply passages check valve 80 side of the connectingpoint 201. Thus, even when the hydraulic oil containing the debris is taken by theoil pump 50, thefilter 52 can remove the debris from the hydraulic oil. Thus, supply of the debris into thecheck valve 80 is limited. Therefore, the one-way valve function of thecheck valve 80 is not interfered, so that the flow of the hydraulic oil from thephase change valve 60 to theoil pump 50 can be reliably limited. In this way, the valvetiming control apparatus 1 can make the appropriate response at the time of changing the phase to the advancing side or the retarding side regardless of the degree of the torque change. - Next, the operation of the valve
timing control apparatus 1 will be described with reference toFIGS. 1 and 3 . - In the stop state of the internal combustion engine, the
stopper pin 19 is engaged into the engagingring 20. Right after starting of the internal combustion engine, sufficient hydraulic oil is not supplied from theoil pump 50 to the retarding chambers 41-43, the advancing chambers 45-47 and thehydraulic pressure chambers stopper pin 19 is still engaged into the engagingring 20, and thecamshaft 3 is held in the most retarded position relative to the crankshaft. Therefore, thevane rotor 30 is repeatedly circumferentially swung back and forth to repeatedly hit thehousing 10, resulting in generation of hammering sound due to the torque fluctuations received by the camshaft until the hydraulic oil is supplied to the respective hydraulic chambers. - When the sufficient hydraulic oil is supplied from the
oil pump 50 after the starting of the internal combustion engine, thestopper pin 19 is removed from the engagingring 20 by the hydraulic pressure of the hydraulic oil supplied to thehydraulic pressure chamber 22 or thehydraulic pressure chamber 23. Thereby, therotor 30 can now rotate relative to thehousing 10. The phase difference of thecamshaft 3 relative to the crankshaft is adjusted by controlling the hydraulic pressure applied to the respective retarding chambers and the hydraulic pressure applied to the respective advancing chambers. - During the operating period of the internal combustion engine, in the state of
FIG. 1 where the electric power supply to thephase change valve 60 is turned off, thespool 68 is held in the position shown inFIG. 1 by the load of thespring 69. When thephase change valve 60 is held in the state shown inFIG. 1 , the hydraulic oil, which is discharged from theoil pump 50, passes through the connectingpoint 201 and thesupply passage 203 and is supplied to thefilter 52. Thefilter 52 removes the debris mixed into the hydraulic oil. The hydraulic oil, from which the debris is removed, is supplied from thesupply passage 204 to thevalve passage 89 of thecheck valve 80 and then passes through thesupply passage 207. Thereafter, the hydraulic oil is supplied from thesupply passage 207 to the interior of thesleeve 67 through theopening 73 of thephase change valve 60. At this time, thecheck valve 80 enables the flow of the hydraulic oil. - The hydraulic oil, which is outputted from the
opening 71 of thephase change valve 60, passes through theretarding passage 210, theannular passage 240 and the retardingpassages 211, 243-245 and is supplied into the retarding chambers 41-43. Furthermore, the hydraulic oil of the advancing chambers passes the advancing passages 246-248, 221, theannular passage 242, the advancingpassage 220, thephase change valve 60 and thedischarge passage 208 and is discharged into theoil pan 51. Thereby, the hydraulic oil is supplied to the respective retarding chambers, and the hydraulic oil is discharged from the respective advancing chambers. In this way, thevane rotor 30 receives the hydraulic pressure from the three retarding chambers 41-43, so that thevane rotor 30 is rotated relative to thehousing 10 in the retarding direction. - When the electric power supply to the
phase change valve 60 is turned on, thespool 68 is moved to the position show inFIG. 3 by the electromagnetic force of thesolenoid drive arrangement 61, which is exerted against the load of thespring 69. When thephase change valve 60 is held in the state shown inFIG. 3 , the hydraulic oil, which is discharged from theoil pump 50, passes through the connectingpoint 201 and thesupply passage 203 and is supplied to thefilter 52. Thefilter 52 removes the debris mixed into the hydraulic oil. The hydraulic oil, from which the debris is removed, is supplied from thesupply passage 204 to thevalve passage 89 of thecheck valve 80 and then passes through thesupply passage 207. Thereafter, the hydraulic oil is supplied from thesupply passage 207 to the interior of thesleeve 67 through theopening 73 of thephase change valve 60. The hydraulic oil, which is outputted from theopening 70 of thephase change valve 60, passes through the advancingpassage 220, theannular passage 242 and the advancingpassages 221, 246-248 and is supplied into the advancing chambers 45-47. Furthermore, the hydraulic oil of the retarding chambers passes the retarding passages 243-245, 211, theannular passage 240, theretarding passage 210, thephase change valve 60 and thedischarge passage 206 and is discharged into theoil pan 51. Thereby, the hydraulic oil is supplied to the respective advancing chambers, and the hydraulic oil is discharged from the respective retarding chambers. In this way, thevane rotor 30 receives the hydraulic pressure from the three advancing chambers 45-47, so that thevane rotor 30 is rotated relative to thehousing 10 in the advancing direction. - When the
vane rotor 30 reaches a target phase, theECU 79 controls the duty ratio of the drive current supplied to thephase change valve 60 to hold thespool 68 in an intermediate position between the position ofFIG. 1 and the position ofFIG. 3 . In this state, the hydraulic oil, which is supplied from theoil pump 50 through thesupply passage 207, passes the gaps, each of which is formed between the corresponding one of thelands openings retarding passage 210 and the advancingpassage 220 to apply the pressure. - Next, the characteristic operation of the valve
timing control apparatus 1 of the present embodiment will be described with reference toFIGS. 5 and 6 . - During the operating period of the internal combustion engine, as shown in
FIG. 5 , at the time of phase control operation (retarding operation) for adjusting the phase to the target phase at the retarding side by supplying the hydraulic oil to the respective retarding chambers and by discharging the hydraulic oil from the respective advancing chambers, thevane rotor 30 receives the torque changes (torque fluctuation) toward the retarding side and the advancing side with respect to thehousing 10 due to the torque changes (torque fluctuation) applied to thecamshaft 3. When thevane rotor 30 receives the torque change toward the advancing side, the hydraulic oil in the respective retarding chambers receives the force to drive the hydraulic oil out of the retarding chambers toward the retarding passages 243-245, 211, theannular passage 240, theretarding passage 210 and thesupply passage 207. - Here, in the present embodiment, the
check valve 80 is provided between thesupply passage 207 and thesupply passage 204. Therefore, thecheck valve 80 closes thevalve passage 89 when the sum of the hydraulic pressure of the hydraulic oil, which is applied from the respective retarding chambers to the retarding passages 243-245, 211, theannular passage 240, theretarding passage 210 and thesupply passage 207, and the urging force of thespring 83 per unit area is larger than the hydraulic pressure of the hydraulic oil discharged from theoil pump 50. Thus, the hydraulic fluid does not flow out of the respective retarding chambers to the retarding passages 243-245, 211, theannular passage 240, theretarding passage 210 and thesupply passage 207. Thefilter 52 is provided in thesupply passages check valve 80 side of the connectingpoint 201 to limit the inflow of the debris of the hydraulic oil into thecheck valve 80. Therefore, thecheck valve 80 can reliably limit the backflow of the hydraulic oil. Therefore, in the state where the hydraulic pressure of theoil pump 50 is low, even when thevane rotor 30 receives the torque change toward the advancing side, thecheck valve 80 can limit the returning of thevane rotor 30 toward the advancing side relative to thehousing 10. As described above, it is possible to limit the returning of thevane rotor 30 relative to thehousing 10 toward the advancing side, which is opposite from the target phase. Thus, thevane rotor 30 can quickly reach the target phase at the retarding side. - As shown in
FIG. 6 , at the time of phase control operation (advancing operation) for adjusting the phase to the target phase at the advancing side by supplying the hydraulic oil to the respective advancing chambers and by discharging the hydraulic oil from the respective retarding chambers, thevane rotor 30 receives the torque changes (torque fluctuation) toward the retarding side and the advancing side with respect to thehousing 10 due to the torque changes (torque fluctuation) applied to thecamshaft 3. When thevane rotor 30 receives the torque changes toward the retarding side, the hydraulic oil in the respective advancing chambers receives the force to drive the hydraulic oil out of the advancing chambers toward the advancing passages 246-248, 221, theannular passage 242, the advancingpassage 220 and thesupply passage 207. - Here, in the present embodiment, the
check valve 80 is provided between thesupply passage 207 and thesupply passage 204. Therefore, thecheck valve 80 closes thevalve passage 89 when the sum of the hydraulic pressure of the hydraulic oil, which is applied from the respective advancing chambers to the advancing passages 246-248, 221, theannular passage 242, the advancingpassage 220 and thesupply passage 207, and the urging force of thespring 83 per unit area is larger than the hydraulic pressure of the hydraulic oil discharged from theoil pump 50. Thus, the hydraulic oil in the respective advancing chambers do not flow out of the advancing chambers toward the advancing passages 246-248, 221, theannular passage 242, the advancingpassage 220 and thesupply passage 207. Thefilter 52 is provided in thesupply passages check valve 80 side of the connectingpoint 201 to limit inflow of the debris of the hydraulic oil into thecheck valve 80. Therefore, thecheck valve 80 can reliably limit the backflow of the hydraulic oil. Therefore, in the state where the hydraulic pressure of theoil pump 50 is low, even when thevane rotor 30 receives the torque change toward the retarding side, thecheck valve 80 can limit the returning of thevane rotor 30 toward the retarding side relative to thehousing 10. As described above, it is possible to limit the returning of thevane rotor 30 relative to thehousing 10 toward the retarding side, which is opposite from the target phase. Thus, thevane rotor 30 can quickly reach the target phase at the advancing side. - Even in the intermediate holding position, the small amount of hydraulic oil flows backward from both of the
retarding passage 210 and the advancingpassage 220 toward thesupply passage 207 to apply the pressure to thecheck valve 80. Even in this case, thecheck valve 80 closes thevalve passage 89 upon seating of thevalve element 81 against thevalve seat 82 when the sum of the hydraulic pressure of the hydraulic oil in thesupply passage 207 and the urging force of thespring 83 per unit area becomes equal to or larger than the hydraulic pressure of the hydraulic oil discharged from theoil pump 50. In this way, theretarding passage 210 and the advancingpassage 220 are both closed, and thereby the backflow of the hydraulic oil from the respective retarding chambers and the respective advancing chambers toward theoil pump 50 side through theretarding passage 210, the advancingpassage 220 and thesupply passage 207 is limited. - Now, the response of the valve
timing control apparatus 1 of the present embodiment at the time of controlling the phase will be compared with that of a previously proposed valve timing control apparatus based onFIG. 7 . - As indicated by a solid line Q in
FIG. 7 , in the valvetiming control apparatus 1 of the present embodiment, thecheck valve 80 and thefilter 52 reliably block the backflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump to implement the appropriate phase control operation. Thus, the amount of return movement b of the vane rotor toward the retarding side caused by the torque change is relatively small, and the vane rotor reaches the target phase within the predetermined time period. - In contrast, in the previously proposed valve timing control apparatus, which does not have the check valve and the filter described above, the appropriate phase control operation cannot be performed. Thus, as indicated by a dotted line P in
FIG. 7 , the amount of return movement a of the vane rotor becomes relatively large, and thereby the vane rotor cannot reach the target phase within the predetermined time period. - As described above, in the valve
timing control apparatus 1 of the present embodiment, the check valve and the filter are provided to reliably block the backflow of the hydraulic oil from the retarding chambers and the advancing chambers toward the oil pump and thereby to improve the response in the phase control operation regardless of the degree of the torque change. - In the above embodiment, the present invention is implemented in the valve timing control apparatus of the intake valves. Alternatively, the present invention may be applied to a valve timing control apparatus, which controls the exhaust valves or both of the intake valves and the exhaust valves.
- Furthermore, in the present embodiment, the phase change valve of the solenoid spool valve type is used. Alternatively, a phase change valve of any other type may be used as long as the hydraulic oil from the oil pump can be switched to supply it to the retarding passage or the advancing passage while the hydraulic oil from the retarding passage or the advancing passage can be switched to discharge it into the discharge passage.
- Additional advantages and modifications will readily occur to those skilled in the art. The invention in its broader terms is therefore not limited to the specific details, representative apparatus, and illustrative examples shown and described.
Claims (3)
1. A valve timing control apparatus that adjusts opening and closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine and is placed in a drive force transmission system, which transmits a drive force from a drive shaft of the internal combustion engine to a driven shaft that drives the at least one of the intake valve and the exhaust valve to open and close the same, the valve timing control apparatus comprising:
a housing that is rotated together with one of the drive shaft and the driven shaft and has a receiving chamber, which is formed within a predetermined angular range in a rotational direction;
a vane rotor that is rotated together with the other one of the drive shaft and the driven shaft and has a vane, which is received in the receiving chamber to partition the receiving chamber into a retarding chamber and an advancing chamber, wherein the vane rotor is rotated relative to the housing in a retarding direction or an advancing direction through use of a pressure of hydraulic fluid in the retarding chamber and a pressure of hydraulic fluid in the advancing chamber to control a relative phase of the vane rotor relative the housing;
a phase change valve that is changeable between an operational state for supplying hydraulic fluid from a fluid supply source to the retarding chamber and an operational state for discharging the hydraulic fluid from the retarding chamber and is also changeable between an operational state for supplying the hydraulic fluid from the fluid supply source to the advancing chamber and an operational state for discharging the hydraulic fluid from the advancing chamber;
a check valve that is provided in a fluid passage between the phase change valve and the fluid supply source, wherein the check valve enables a flow of the hydraulic fluid from the fluid supply source to the retarding chamber or the advancing chamber and blocks a flow of the hydraulic fluid from the retarding chamber or the advancing chamber to a fluid supply source side; and
a filter that is provided in the fluid passage between the check valve and the fluid supply source to remove debris from the hydraulic fluid before supplying of the hydraulic fluid to the check valve.
2. The valve timing control apparatus according to claim 1 , wherein:
the fluid passage between the phase change valve and the fluid supply source includes a connecting point, which is connected to a branch passage that supplies the hydraulic fluid to a lubricating system of the internal combustion engine; and
the check valve is provided in the fluid passage between the connecting portion and the phase change valve.
3. The valve timing control apparatus according to claim 2 , wherein the filter is provided in the fluid passage between the connecting point and the check valve.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2007-243509 | 2007-09-20 | ||
JP2007243509A JP2009074424A (en) | 2007-09-20 | 2007-09-20 | Valve timing adjusting device |
Publications (1)
Publication Number | Publication Date |
---|---|
US20090078222A1 true US20090078222A1 (en) | 2009-03-26 |
Family
ID=40384603
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/194,850 Abandoned US20090078222A1 (en) | 2007-09-20 | 2008-08-20 | Valve timing control apparatus |
Country Status (4)
Country | Link |
---|---|
US (1) | US20090078222A1 (en) |
JP (1) | JP2009074424A (en) |
KR (1) | KR20090031268A (en) |
DE (1) | DE102008041839A1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN101994535A (en) * | 2010-12-08 | 2011-03-30 | 成都恒高机械电子有限公司 | Continuously variable valve timing phaser |
US20110203540A1 (en) * | 2010-02-23 | 2011-08-25 | Denso Corporation | Valve timing adjuster |
US20120291735A1 (en) * | 2010-01-25 | 2012-11-22 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster |
US9004028B2 (en) | 2010-10-27 | 2015-04-14 | Aisin Seiki Kabushiki Kaisha | Valve timing control apparatus |
US9453438B2 (en) | 2013-07-31 | 2016-09-27 | Denso Corporation | Valve timing adjusting device |
US20170114728A1 (en) * | 2014-07-11 | 2017-04-27 | Honda Motor Co., Ltd. | Control apparatus for internal combustion engine |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010255533A (en) * | 2009-04-24 | 2010-11-11 | Toyota Motor Corp | Variable valve timing device |
JP4900451B2 (en) * | 2009-11-09 | 2012-03-21 | 株式会社デンソー | Valve timing adjustment device |
JP2011190816A (en) * | 2010-02-19 | 2011-09-29 | Denso Corp | Check valve device |
JP5274533B2 (en) * | 2010-10-22 | 2013-08-28 | アイシン精機株式会社 | Valve timing control device |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7182052B2 (en) * | 2004-06-28 | 2007-02-27 | Denso Corporation | Valve timing controller |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2004100523A (en) | 2002-09-06 | 2004-04-02 | Mitsubishi Electric Corp | Solenoid valve for controlling oil pressure |
-
2007
- 2007-09-20 JP JP2007243509A patent/JP2009074424A/en active Pending
-
2008
- 2008-08-20 US US12/194,850 patent/US20090078222A1/en not_active Abandoned
- 2008-09-05 DE DE102008041839A patent/DE102008041839A1/en not_active Withdrawn
- 2008-09-19 KR KR1020080091850A patent/KR20090031268A/en not_active Application Discontinuation
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7182052B2 (en) * | 2004-06-28 | 2007-02-27 | Denso Corporation | Valve timing controller |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20120291735A1 (en) * | 2010-01-25 | 2012-11-22 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster |
US8931446B2 (en) * | 2010-01-25 | 2015-01-13 | Schaeffler Technologies Gmbh & Co. Kg | Camshaft adjuster |
US20110203540A1 (en) * | 2010-02-23 | 2011-08-25 | Denso Corporation | Valve timing adjuster |
US9004028B2 (en) | 2010-10-27 | 2015-04-14 | Aisin Seiki Kabushiki Kaisha | Valve timing control apparatus |
CN101994535A (en) * | 2010-12-08 | 2011-03-30 | 成都恒高机械电子有限公司 | Continuously variable valve timing phaser |
US9453438B2 (en) | 2013-07-31 | 2016-09-27 | Denso Corporation | Valve timing adjusting device |
US20170114728A1 (en) * | 2014-07-11 | 2017-04-27 | Honda Motor Co., Ltd. | Control apparatus for internal combustion engine |
US10113490B2 (en) * | 2014-07-11 | 2018-10-30 | Honda Motor Co., Ltd. | Control apparatus for internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
KR20090031268A (en) | 2009-03-25 |
JP2009074424A (en) | 2009-04-09 |
DE102008041839A1 (en) | 2009-04-02 |
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Owner name: DENSO CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MURAO, YOSHIYUKI;TAKENAKA, AKIHIKO;REEL/FRAME:021417/0265 Effective date: 20080729 |
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