US20090178635A1 - Valve timing adjuster - Google Patents
Valve timing adjuster Download PDFInfo
- Publication number
- US20090178635A1 US20090178635A1 US12/349,637 US34963709A US2009178635A1 US 20090178635 A1 US20090178635 A1 US 20090178635A1 US 34963709 A US34963709 A US 34963709A US 2009178635 A1 US2009178635 A1 US 2009178635A1
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- United States
- Prior art keywords
- spool
- advance
- retard
- output port
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
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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
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
- F01L2001/34423—Details relating to the hydraulic feeding circuit
- F01L2001/34426—Oil control valves
- F01L2001/3443—Solenoid driven oil control valves
Definitions
- the present invention relates to a valve timing adjuster for adjusting a valve of an internal combustion engine, which is opened and closed by a camshaft of the engine through torque transmission from a crankshaft of the engine.
- Hydraulic valve timing adjusters have been used widely, each of which has a housing serving as a driving rotor (first rotor) and a vane rotor serving as a driven rotor (second rotor).
- the housing rotates synchronously with the crankshaft of an internal combustion engine.
- the vane rotor rotates synchronously with the camshaft of the engine.
- JP-A-2006-177344 corresponding to U.S. Pat. No. 7,124,722 discloses a hydraulic valve timing adjuster having a housing and a vane rotor.
- An advance chamber is defined between one of the shoes of the housing and the corresponding vane of the vane rotor.
- a retard chamber is defined between the other shoe and the vane.
- the advance and retard chambers are supplied with working fluid to drive the camshaft relative to the crankshaft in a advance direction and a retard direction, respectively, and thereby adjusting valve timing of the valve of the engine.
- the valve timing adjuster disclosed in JP-A-2006-177344 further has a spool valve, which supplies the working fluid from a fluid supply source to the advance or retard chamber by shifting a spool of the spool valve to change a phase (engine phase) of the camshaft relative to the crankshaft.
- a spool valve which supplies the working fluid from a fluid supply source to the advance or retard chamber by shifting a spool of the spool valve to change a phase (engine phase) of the camshaft relative to the crankshaft.
- the valve timing adjuster disclosed in JP-A-2006-177344 further has an advance output line and a retard output line, each of which is fitted with a check valve.
- the spool valve has an input port, an advance output port, a retard output port, an advance return port, and a retard return port.
- the advance and retard output ports can communicate with the advance and retard chambers, respectively, through the advance and retard output lines respectively.
- the advance and retard return ports communicate with intermediate points of the advance and retard output lines respectively.
- the valve timing adjuster retards the engine phase by shifting the spool in the retard direction to connect the advance return port and the retard output port in the spool valve.
- the working fluid discharged from the advance chamber to the advance return port is supplied from the retard output port to the retard output line together with the working fluid, which is supplied from the fluid supply source into the input port.
- the pressure of the output fluid opens the check valve in the retard output line, so that the fluid from the fluid supply source and the advance chamber is supplied to the retard chamber.
- the fluid is supplied to the retard chamber when positive variable torque, which biases the camshaft in the retard direction relative to the crankshaft, acts on the vane rotor.
- the back flow to the advance chamber lowers the responsibility that the valve timing adjuster has when the engine phase changes.
- the back flow also lowers the stability of the engine phase when the valve timing adjuster holds the phase fully retarded by pressing the vane against the appropriate shoe.
- the responsibility and the phase stability lower as above when the camshaft is driven or rotated relative to the crankshaft in the advance direction. Therefore, it is demanded that the valve timing adjuster be improved.
- the present invention is made in view of the above disadvantages. Thus, it is an objective of the present invention to address at least one of the above disadvantages.
- a valve timing adjuster for an internal combustion engine having a crankshaft, a valve, and a camshaft, wherein the adjuster adjusts valve timing of the valve, which is opened and closed by the camshaft through torque transmission from the crankshaft, the adjuster including a first rotor, a second rotor, a spool valve, a connection passage, and a connection check valve.
- the first rotor is rotatable synchronously with the crankshaft.
- the second rotor is rotatable synchronously with the camshaft.
- the first rotor and the second rotor define therebetween an advance chamber and a retard chamber, which are arranged circumferentially one after another.
- the second rotor is adapted to drive the camshaft relative to the crankshaft in an advance direction when working fluid is supplied to the advance chamber.
- the second rotor is adapted to drive the camshaft relative to the crankshaft in a retard direction when working fluid is supplied to the retard chamber.
- the spool valve includes an input port, a drain port, a first output port, a second output port, and a spool.
- Working fluid is supplied to the spool valve from an external fluid supply source through the input port.
- Working fluid is drained through the drain port.
- Working fluid is output to one of the advance chamber and the retard chamber through the first output port.
- Working fluid is output to the other one of the advance chamber and the retard chamber through the second output port.
- the spool is adapted to be displaceable to a first position, at which the first rotor is rotated relative to the second rotor in order to shift a phase of the camshaft relative to the crankshaft.
- the spool is adapted to be displaceable to a second position, at which the second rotor is pressed against the first rotor in order to hold the phase of the camshaft at a full phase, at which the phase is fully shifted.
- the spool valve When the spool is positioned at the second position, the spool valve connects the first output port with the input port and connects the second output port with the drain port.
- the connection passage is provided in the spool, wherein the connection passage connects the first output port with the second output port when the spool is positioned at the first position.
- the connection check valve is provided in the connection passage. The connection check valve opens to allow working fluid to flow from the second output port toward the first output port when the spool is positioned at the first position. The connection check valve closes to limit working fluid from flowing from the first output port toward the second output port when the spool is positioned at the first position.
- FIG. 1 is a schematic diagram of a valve timing adjuster according to a first embodiment of the present invention
- FIG. 2 is a chart showing the variable torque acting on the drive unit of the valve timing adjuster according to the first embodiment
- FIG. 3 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in an advance position;
- FIG. 4 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in a retard position;
- FIG. 5 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in a full retard position;
- FIG. 6 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in a hold position;
- FIG. 7 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in the advance position;
- FIG. 8 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in the advance position;
- FIG. 9 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in the retard position;
- FIG. 10 is a schematic diagram of a valve timing adjuster according to a second embodiment of the present invention.
- FIG. 11 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a full advance position;
- FIG. 12 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in an advance position;
- FIG. 13 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a retard position;
- FIG. 14 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a full retard position;
- FIG. 15 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a hold position;
- FIG. 16 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in the full advance position;
- FIG. 17 is an axial sectional view of the spool valve of a valve timing adjuster according to another embodiment of the present inventions this valve being a modified form of the spool valve of the valve timing adjuster according to the second embodiment.
- FIG. 1 is a schematic diagram of a valve timing adjuster 1 according to a first embodiment of the present invention.
- the adjuster 1 is applied to an internal combustion engine of a vehicle.
- the adjuster 1 is a hydraulic valve timing adjuster using hydraulic oil serving as working fluid.
- the adjuster 1 adjusts valve timing of an intake valve serving as a “valve” of the engine.
- the adjuster 1 includes a drive unit 10 and a control unit 30 .
- the drive unit 10 is fitted to a driving force transmission system for transmitting the driving force of a crankshaft (not shown) of the engine to a camshaft 2 of the engine and is driven with hydraulic oil.
- the control unit 30 controls the supply of hydraulic oil to the drive unit 10 .
- the drive unit 10 includes a housing 12 serving as a first rotor (driving rotor), which has a cylindrical sprocket 12 a and shoes 12 b to 12 e as partitions.
- the sprocket 12 a is connected to the crankshaft by a timing chain (not shown). While the engine is running, driving force is transmitted from the crankshaft to the sprocket 12 a, so that the housing 12 rotates with the crankshaft clockwise in FIG. 1 .
- the shoes 12 b to 12 e are formed on the inner periphery of the sprocket 12 a and spaced circumferentially at substantially regular intervals.
- the shoes 12 b to 12 e project radially inwardly from the sprocket 12 a and each of the shoes 12 b to 12 e has a radially inner surface that has an arcuate recess shape in section taken perpendicularly to a rotational axis of the housing 12 .
- the drive unit 10 further includes a vane rotor 14 , which has a cylindrical boss 14 a.
- the radially inner surface of each of the shoes 12 b to 12 e is in slidable contact with an outer peripheral surface of the boss 14 a.
- a vane chamber 50 is formed between adjacent shoes 12 b to 12 c. Another vane chamber 50 is formed between adjacent shoes 12 c to 12 d. Another vane chamber 50 is formed between adjacent shoes 12 d to 12 e. Another vane chamber 50 is formed between adjacent shoes 12 e to 12 b.
- the vane rotor 14 is a driven rotor (second rotor), which is received in the housing 12 in axially slidable contact with it.
- the vane rotor 14 further has vanes 14 b to 14 e.
- the boss 14 a is bolted to the camshaft 2 coaxially with it.
- the vane rotor 14 rotates synchronously with the camshaft 2 clockwise in FIG. 1 and is rotatable relative to the housing 12 .
- the vanes 14 b to 14 e are formed on the outer periphery of the boss 14 a and spaced circumferentially at substantially regular intervals. Each of the vanes 14 b to 14 e is positioned in one of the vane chambers 50 .
- the vanes 14 b to 14 e radially outwardly project from the boss 14 a, and each of the vanes 14 b to 14 e has a radially outer surface that has an arcuate projecting shape in section taken perpendicularly to the rotational axis of the vane rotor 14 .
- the top face of each of the vanes 14 b to 14 e is in slidable contact with an inner peripheral surface of the sprocket 12 a.
- the vane 14 b and the shoe 12 b define an advance chamber 52 therebetween in the corresponding vane chamber 50 associated with this vane.
- the vane 14 c and the shoe 12 c define an advance chamber 53 therebetween in the corresponding vane chamber 50 .
- the vane 14 d and the shoe 12 d define an advance chamber 54 therebetween in the corresponding vane chamber 50 .
- the vane 14 e and the shoe 12 e define an advance chamber 55 therebetween in the corresponding vane chamber 50 .
- the vane 14 b and the shoe 12 c define a retard chamber 56 therebetween in the corresponding vane chamber 50 .
- the vane 14 c and the shoe 12 d define a retard chamber 57 therebetween in the corresponding vane chamber 50 .
- the vane 14 d and the shoe 12 e define a retard chamber 58 therebetween in the corresponding vane chamber 50 .
- the vane 14 e and the shoe 12 b define a retard chamber 59 therebetween in the corresponding vane chamber
- the supply of hydraulic oil to the advance chambers 52 to 55 turns or rotates the vane rotor 14 in the advance direction relative to the housing 12 , driving the camshaft 2 in the advance direction relative to the crankshaft.
- the engine phase that determines the valve timing is advanced.
- Continued supply of hydraulic oil to the advance chambers 52 to 55 presses the vanes 14 b, 14 c, 14 d, 14 e in the advance direction against the shoes 12 c, 12 d, 12 e, 12 b, respectively, and thereby the engine phase is held fully advanced at a full advance phase (full phase on the advance side).
- the supply of hydraulic oil to the retard chambers 56 to 59 turns the vane rotor 14 in the retard direction relative to the housing 12 , driving the camshaft 2 in the retard direction relative to the crankshaft. This retards the engine phase.
- Continued supply of hydraulic oil to the retard chambers 56 to 59 presses the vanes 14 b to 14 e in the retard direction against the shoes 12 b to 12 e, respectively, and thereby the engine phase is held fully retarded at a full retard phase (full phase on the retard side).
- the control unit 30 has an advance output line 72 and a retard output line 76 , which lead through the camshaft 2 and the bearing (not shown) for the camshaft.
- the advance output line 72 communicates with the advance chambers 52 to 55 in any operational condition of the drive unit 10 .
- the retard output line 76 communicates with the retard chambers 56 to 59 in any operational condition of the drive unit 10 .
- the control unit 30 further has an input line 80 , which communicates with the discharge port of a pump 4 serving as a fluid supply source.
- the pump 4 pumps up hydraulic oil from an oil pan 5 of the engine and discharges the oil to the input line 80 under a pressure higher than the atmospheric pressure.
- the pump 4 is a mechanical pump, which the crankshaft drives. While the engine is running, the pump 4 keeps pumping hydraulic oil into the input line 80 .
- the control unit 30 further has a drain line 82 , which opens into the atmosphere, and through which hydraulic oil is drained into the oil pan 5 .
- the control unit 30 includes a spool valve 100 , which is an electromagnetic control valve having a solenoid 120 and a spool 130 .
- the solenoid 120 creates electromagnetic driving force in order to linearly reciprocate the spool 130 .
- the valve 100 further has an advance output port 112 , a retard output port 114 , an input port 116 , and a drain port 118 .
- the valve 100 outputs hydraulic oil through the advance output port 112 and the advance output line 72 to the advance chambers 52 to 55 .
- the valve 100 outputs hydraulic oil through the retard output port 114 and the retard output line 76 to the retard chambers 56 to 59 .
- the oil from the pump 4 is input through the input line 80 into the input port 116 .
- the drain port 118 opens into the atmosphere through the drain line 82 .
- the valve 100 drains hydraulic oil through the drain port 118 into the drain line 82 .
- the solenoid reciprocates the spool 130 such that ports communicated with the input port 116 and the drain port 118 , respectively, are selected among the output ports 112 , 114 .
- the control unit 30 further includes a control circuit 200 , the main component of which is a microcomputer having a memory 200 a.
- the control circuit 200 is connected electrically to the solenoid 120 .
- the control circuit 200 controls the current supply to the solenoid 120 and the operation of the engine.
- the control circuit 200 is connected electrically to a crank sensor 202 that senses the rotation of the crankshaft and a cam sensor 204 that senses the rotation of the camshaft 2 .
- the sensors 202 , 204 output signals for controlling the current supply to the solenoid 120 and the operation of the engine.
- the spool valve 100 controls the position of the spool 130 .
- the spool 130 When the spool 130 is in a certain position, where the input port 116 communicates with the advance output port 112 , the oil supplied from the pump 4 to the input line 80 is output by the valve 100 to the advance output line 72 , and thereby the oil is supplied to the advance chambers 52 to 55 .
- the spool 130 When the spool 130 is in another position, where the input port 116 communicates with the retard output port 114 , the oil supplied from the pump 4 to the input line 80 is output by the valve 100 to the retard output line 76 , and thereby the oil is supplied to the retard chambers 56 to 59 .
- valve 100 can drain the oil in the advance chambers 52 to 55 to the oil pan 5 through the advance output line 72 and the drain line 82 .
- variable torque torque reversals
- the variable torque is transmitted through the camshaft 2 and acts on the vane rotor 14 .
- the variable torque alternates periodically between negative torque and positive torque, which bias the camshaft 2 in the advance and retard directions respectively relative to the crankshaft.
- the peak positive torque T+ and the peak negative torque Tto may be substantially equal to each other in absolute value, so that the average variable torque may be substantially zero.
- the peak positive torque T+ may be greater in absolute value than the peak negative torque Tto, so that the average variable torque may deflect positively.
- the spool valve 100 further has a sleeve 110 , a driving shaft 139 , and a return spring 140 .
- the sleeve 110 is metallic and has a hollow cylindrical shape.
- the solenoid 120 is fixed to one end 110 a of the sleeve 110 .
- the retard output port 114 , the input port 116 , the advance output port 112 , and the drain port 118 are formed in the sleeve 110 in this order in a direction away from the sleeve end 110 a toward the other sleeve end 110 b.
- the spool 130 is metallic, and has a column shape with lands formed thereon, and positioned in the sleeve 110 coaxially with the sleeve 110 .
- One end 130 a of the spool 130 is connected coaxially with the driving shaft 139 .
- the solenoid 120 drives the shaft 139 electromagnetically to move the spool 130 axially with the shaft.
- the spool 130 has an advance support land 132 , an advance switch land 134 , a retard switch land 136 , and a retard support land 138 , which are formed in this order in a direction away from the other spool end 130 b toward the spool end 130 a.
- the advance support land 132 is supported slidably by the portion of the sleeve 110 that lies between the advance output port 112 and the drain port 118 .
- the advance switch land 134 is supported slidably by at least one of the above portion of the sleeve 110 and the other portion of the sleeve 110 that lies between the advance output port 112 and the input port 116 .
- the retard support land 138 is supported slidably by a portion of the sleeve 110 that lies between the retard output port 114 and the sleeve end 110 a.
- the retard switch land 136 is supported slidably by at least one of the above portion of the sleeve 110 and the other portion of the sleeve 110 that lies between the retard output port 114 and the input port 116 .
- the input port 116 communicates with the space between the switch lands 134 , 136 regardless of the position of the spool 130 .
- the return spring 140 is a metallic compression coil spring, which is positioned in the sleeve 110 coaxially with the sleeve 110 .
- the spring 140 is positioned in the sleeve 110 between the sleeve end 110 b and the advance support land 132 of the spool 130 .
- the compressive deformation of the spring 140 creates a restoring force that biases the spool 130 axially toward the solenoid 120 .
- the current supply to the solenoid 120 creates an electromagnetic driving force that biases the spool 130 with the driving shaft 139 axially toward the spring 140 . Accordingly, the spool 130 is driven according to the balance between the restoring force created by the spring 140 and the electromagnetic driving force created by the solenoid 120 .
- connection check valves 210 , 230 fitted in the connection passages 220 , 240 respectively formed in the spool 130 .
- one end 221 of the advance connection passage 220 opens at a peripheral surface of the spool 130 between the switch lands 134 , 136 at multiple positions. Accordingly, as shown in FIGS. 3 to 6 , the passage end 221 communicates with the space between the switch lands 134 , 136 , regardless of the position of the spool 130 . In particular when the spool 130 is in the spool position shown in FIG. 3 , the passage end 221 communicates with the advance output port 112 and the input port 116 through the space between the switch lands 134 , 136 .
- the other end 222 of the advance connection passage 220 opens at the peripheral surface of the spool 130 between the retard switch land 136 and the retard support land 138 at multiple positions. Accordingly, as shown in FIGS. 3 to 6 , this passage end 222 communicates with the space between these lands 136 , 138 , regardless of the position of the spool 130 .
- the advance connection passage 220 communicates with the advance output port 112 as stated above, and the end 222 of the advance connection passage 220 communicates with the retard output port 114 through the space between the lands 136 , 138 .
- the output ports 112 , 114 communicate with each other through the advance connection passage 220 .
- the advance connection check valve 210 closes to limit fluid from flowing in a direction from the end 221 of the advance connection passage 220 toward the other end 222 . Also, the advance connection check valve 210 opens to allow fluid to flow in the opposite direction opposite from the above.
- the advance connection check valve 210 includes an advance valve seat 212 , an advance valve member 214 , an advance retainer 215 , and an elastic member 216 .
- the advance valve seat 212 is a conical wall of the advance connection passage 220 , and the conical wall has a diameter that becomes smaller toward the end 222 of the advance connection passage 220 .
- the advance retainer 215 is positioned between the advance valve seat 212 and the other end 221 of the advance connection passage 220 .
- the advance valve member 214 is positioned between the advance valve seat 212 and the advance retainer 215 .
- the retard connection check valve 230 is positioned between the advance connection check valve 210 and the spool end 110 b.
- the elastic member 216 is interposed between the retard connection check valve 230 and the advance retainer 215 .
- the advance valve member 214 is a metallic ball and is axially movable in the advance connection passage 220 such that the advance valve member 214 is brought into and out of contact with the advance valve seat 212 .
- the advance retainer 215 is metallic and has a peripheral wall part 215 a and a bottom. The peripheral wall part 215 a is supported by the inner peripheral wall of the advance connection passage 220 and receives the advance valve member 214 therein.
- the advance retainer 215 is axially slidable in the advance connection passage 220 .
- the elastic member 216 is a metallic compression spring. The compressive deformation of the elastic member 216 creates a restoring force, which biases the advance retainer 215 together with the advance valve member 214 toward the advance valve seat 212 .
- the end 221 of the advance connection passage 220 which communicates with the space between the switch lands 134 , 136 , serves also as one end of the retard connection passage 240 .
- the passage end 221 is common to or shared by the connection passages 220 , 240 . Accordingly, when the spool 130 is in the spool position shown in FIG. 4 or 5 , the common passage end 221 communicates with the retard output port 114 and the input port 116 through the space between the switch lands 134 , 136 .
- the other end 242 of the retard connection passage 240 opens at the peripheral surface of the spool 130 between the advance support land 132 and the advance switch land 134 at multiple positions. Accordingly, as shown in FIGS. 3 to 6 , this passage end 242 communicates with the space between these lands 132 , 134 , wherever the spool 130 is positioned.
- the retard connection passage 240 communicates with the retard output port 114 as stated above, and the end 242 of the retard connection passage 240 communicates with the advance output port 112 through the space between the lands 132 , 134 .
- the output ports 112 , 114 communicate with each other through the retard connection passage 240 .
- the retard connection check valve 230 closes to limit fluid from flowing in a direction from the common end 221 of the retard connection passage 240 toward the other end 242 . Also, the retard connection check valve 230 opens to allow fluid to flow in the opposite direction opposite from the above.
- the retard connection check valve 230 is similar in structure to the advance connection check valve 210 . Specifically, the retard connection check valve 230 includes a retard valve seat 232 , a retard valve member 234 , a retard retainer 235 , and the elastic member 216 .
- the retard valve seat 232 is a conical wall of the retard connection passage 240 , and the conical wall has a diameter that becomes smaller toward the end 242 of this passage.
- the retard retainer 235 is positioned between the retard valve seat 232 and the common passage end 221 .
- the retard valve member 234 is positioned between the retard valve seat 232 and the retard retainer 235 .
- the elastic member 216 is interposed between the retard retainer 235 and the advance retainer 215 .
- the retard valve member 234 is axially movable in the retard connection passage 240 such that the retard valve member 234 is brought into and out of contact with the retard valve seat 232 .
- the retard retainer 235 has a peripheral wall part 235 a and a bottom.
- the peripheral wall part 235 a is supported by an inner peripheral wall of the retard connection passage 240 and receives the retard valve member 234 therein.
- the restoring force created by the compressive deformation of the elastic member 216 biases the retard retainer 235 together with the retard valve member 234 toward the retard valve seat 232 .
- the retard valve member 234 moves toward the common end 221 such that the retard valve member 234 becomes out of contact with or disengaged from the retard valve seat 232 as shown in FIG. 4 .
- the retard connection check valve 230 opens and allows hydraulic oil to flow in a direction from the passage end 242 to the common passage end 221 .
- the retard valve member 234 moves toward the end 242 such that the retard valve member 234 is brought into contact with or becomes engaged with the retard valve seat 232 as shown in FIGS. 3 , 5 to 9 .
- the retard connection check valve 230 closes and limits the hydraulic oil from flowing in a direction from the common passage end 221 to the other passage end 242 .
- the present embodiment is also characterized by a junction passage 260 formed in the spool 130 so that the advance output port 112 can communicate with the drain port 118 , as shown in FIGS. 1 , 5 .
- the junction passage 260 has an open end 261 formed at the spool end 130 b inside the advance support land 132 . At least when the spool 130 is in the spool position shown in FIG. 5 , the passage end 261 communicates with the drain pod 118 through the space between the spool end 130 b and the adjacent sleeve end 110 b.
- the other end 262 of the junction passage 260 open to the peripheral wall of the spool 130 at the advance support land 132 at multiple positions.
- the passage end 262 communicates with the space between the advance support land 132 and the advance switch land 134 through the space between the inner periphery of the sleeve 110 and the outer periphery of the support land 132 .
- the junction passage 260 communicates with the drain port 118 , and the space between the lands 132 , 134 communicates with the advance output port 112 , as stated above. Accordingly, these ports 118 , 112 communicate with each other through the junction passage 260 .
- the input line 80 which communicates with the pump 4 and the input port 116 , is fitted with an input check valve 280 .
- the input check valve 280 opens, as shown in FIGS. 3 to 6 . This allows hydraulic oil to flow from the pump 4 to the input port 116 .
- the input check valve 280 closes, as shown in FIGS. 7 to 9 . This restrains the flow of hydraulic oil from the input port 116 to the pump 4 .
- the control circuit 200 calculates the actual engine phase Pr and target engine phase Pt of the camshaft 2 relative to the crankshaft. Based on the calculated phases Pr and Pt, the control circuit 200 controls the current supply to the solenoid 120 of the spool valve 100 . This controls the position of the spool 130 of the spool valve 100 . According to the controlled position, the spool valve 100 supplies hydraulic oil to or discharge hydraulic oil from the advance chambers 52 to 55 or the retard chambers 56 to 59 . This adjusts the engine phase, thereby adjusting the valve timing.
- the valve timing adjustment through the valve timing adjuster 1 will be described below in detail.
- valve timing adjuster 1 advances the valve timing by varying the engine phase of the camshaft 2 relative to the crankshaft in the advance direction as follows.
- the control circuit 200 controls the current to be supplied to the solenoid 120 at a specified advance value Ia.
- the spool 130 is shifted to the advance phase position (first position on the advance side) shown in FIGS. 3 , 7 .
- the advance connection passage 220 connects the retard output port 114 with the advance output port 112 communicating with the input port 116 and blocked from the drain port 118 .
- the advance connection check valve 210 opens, allowing hydraulic oil to flow from the retard output port 114 to the advance output port 112 .
- the valve 100 is capable of being supplied with hydraulic oil through the retard output port 114 . This limits the shortage of hydraulic oil in the advance chambers 52 to 55 that is increased in volume by the action of the negative torque.
- the oil from the pump 4 also flows into the retard connection passage 240 communicating with the advance output port 112 through the common passage end 221 , but the closure of the retard connection check valve 230 restrains the flow of hydraulic oil toward the other end 242 of the passage 240 . Also, the advance output port 112 communicating with the advance connection passage 220 through the common passage end 221 is blocked or discommunicated from the drain port 118 . This restrains the drain of hydraulic oil through the drain port 118 .
- the advance operation of advancing the valve timing enables the connection check valves 210 , 230 to function properly and timely to discharge hydraulic oil from the retard chambers 56 to 59 and supply a sufficient amount of hydraulic oil to the advance chambers 52 to 55 . This enables high advance responsibility.
- valve timing adjuster 1 retards the valve timing by varying the engine phase or phase relation of the camshaft 2 relative to the crankshaft in the retard direction as follows.
- the control circuit 200 controls the current to be supplied to the solenoid 120 at a retard value Ir that is smaller than the advance value Ia.
- the spool 130 is shifted to the retard phase position (first position on the retard side) shown in FIGS. 4 , 8 .
- the retard connection passage 240 connects the retard output port 114 to the advance output port 112 .
- the retard output port 114 communicates with the input port 116 , and the advance output port 112 is blocked from the drain port 118 .
- the retard connection check valve 230 opens and allows hydraulic oil to flow in a direction from the advance output port 112 to the retard output port 114 . If the amount of hydraulic oil being input from the pump 4 into the spool valve 100 decreases, the valve 100 is capable of being supplied with hydraulic oil through the advance output port 112 . This limits the shortage of hydraulic oil in the retard chambers 56 to 59 , a volume of each of which has been increased by the positive torque.
- the oil from the pump 4 also flows into the advance connection passage 220 communicating with the retard output port 114 through the common passage end 221 , but the closure of the advance connection check valve 210 restrains the flow of hydraulic oil toward the other end 222 of the passage 220 . Also, the advance output port 112 communicating with the retard connection passage 240 through the passage end 242 is blocked from the drain port 118 . This restrains the drain of hydraulic oil through the drain port 118 .
- hydraulic oil is restrained from flowing back through the retard output port 114 to the connection passages 240 , 220 and the input line 80 .
- This not only restrains the flow of hydraulic oil out of the retard chambers 56 to 59 but also prevents erroneous supply of hydraulic oil to the advance chambers 52 to 55 .
- the retard operation of the valve timing enables the connection check valves 230 , 210 to function properly and timely to discharge hydraulic oil from the advance chambers 52 to 55 and supply a sufficient amount of hydraulic oil to the retard chambers 56 to 59 . This enables high retard responsibility.
- valve timing adjuster 1 retards the valve timing to the maximum or to the full by holding the engine phase fully retarded as follows.
- the control circuit 200 controls the current to be supplied to the solenoid 120 at a full retard value Ir0 smaller than the retard value Ir.
- the spool 130 is driven to the full retard phase position (second position on the retard side) shown in FIGS. 5 , 9 , which is a position located in the retard direction away from the retard phase position shown in FIGS. 4 , 8 .
- the full retard phase position and the retard phase position are arranged adjacent to each other in a direction, in which the spool 130 is displaceable.
- the retard connection passage 240 connects the retard output port 114 communicating with the input port 116 to the advance output port 112 communicating with the drain port 118 .
- the set value R may be a low engine speed (for example, 500 to 1,400 rpm) at which the rotation of the drive unit 10 less influences the engine phase.
- the latest reference phase is learned when the engine has started. This contributes to the improvement in the accuracy in valve timing adjustment.
- the engine rotates at a relatively low speed when the start of the engine has been completed, it is possible to learn the reference phase while the housing 12 and the vane rotor 14 rotate with weak or slight vibration. This, too, contributes to the improvement in the adjustment accuracy.
- the oil from the pump 4 is supplied continuously to the retard chambers 56 to 59 , as is the case with the retard operation. Also, as shown in FIG. 5 , the oil input into the input port 116 flows into the common end 221 of the retard connection passage 240 , and the oil compressed by the action of the positive torque in the advance chambers 52 to 55 flows into the advance output port 112 . The oil flowing into the advance output port 112 then flows into not only the other end 242 of the retard connection passage 240 but also the drain port 118 , which is open to the atmosphere, so that the pressure of the oil becomes the atmospheric pressure.
- the oil flowing into the passage end 242 which is currently adjacent to the advance output port 112 , is lower in pressure than the oil flowing into the common passage end 221 , which is currently adjacent to the retard output port 114 .
- This closes the retard connection check valve 230 restraining not only the flow of hydraulic oil from the retard output port 114 to the advance output port 112 but also the oil flow in the opposite direction. Accordingly, a substantial part of the oil flowing into the advance output port 112 is drained through the drain port 118 .
- the fully retarded engine phase is capable of being held reliably and stably.
- connection passage 240 connects the retard output port 114 and the advance output port 112 (first and second output ports) as is the case when the spool 130 is in the retard position (first position on the retard side).
- working fluid is discharged from the advance chamber through the advance output port 112 to the connection passage 240 , and thereby the communication between the advance output port 112 and the drain port 118 opening to atmosphere causes pressure at the end 242 of the connection passage 240 that is adjacent to the advance output port 112 to be lower than pressure at the other end 221 , which is adjacent to the retard output port 114 communicating with the input port 116 .
- connection check valve 230 closes, and thereby limiting working fluid from flowing through the connection passage 240 between the advance and retard output ports 112 , 114 .
- This makes it possible to simplify the valve timing adjuster 1 in structure by arranging the first position and the second position adjacent to each other and by making the connection passage 240 commonly provide connection between the advance and retard output ports 112 , 114 when the spool 130 is positioned at either of the above first and second positions. This also makes it possible to stabilize the engine phase by draining working fluid quickly from the advance chamber through the output port 112 to the drain port 118 .
- the control circuit 200 monitors the actual engine phase Pr, which is calculated from the signals from the crank sensor 202 and the cam sensor 204 .
- the control circuit 200 learns a stable value of the monitored phase Pr (actual phase) as a reference phase Pr 0 , which is stored in a memory 200 a of the control circuit 200 .
- the reference phase Pr 0 is updated every time the control circuit 200 learns a stable value of the monitored phase Pr.
- the above operation of learning the reference phase Pr 0 using the monitored phase Pr is defined as learning of the reference phase Pr 0 in the present embodiment.
- the control circuit 200 calculates the present actual engine phase Pr and the present target phase Pt, which are necessary for controlling the current supply to the solenoid 120 .
- the fully retarded engine phase is capable of being held effectively stably when the control circuit 200 learns the reference phase Pr 0 . This makes it possible to increase the accuracy of valve timing adjustment by realizing current supply control based on accurate reference phase Pr 0 .
- valve timing adjuster 1 keeps the valve timing by holding the engine phase within a specified target phase range excluding the full retard phase, as follows.
- the control circuit 200 controls the current to be supplied to the solenoid 120 at a normal hold value In smaller than the advance value la and larger than the retard value Ir. As a result, the spool 130 is shifted to the normal hold operation position shown in FIG. 6 . When the spool 130 is in the above position, both of the output ports 112 , 114 are blocked from the input port 116 and the drain port 118 .
- the oil input from the pump through the input line 80 to the input port 116 is not supplied to the advance and retard chambers 52 to 59 , and hydraulic oil is restrained from flowing out of the advance and retard chambers 52 to 59 .
- the first embodiment enables quick and accurate valve timing adjustment suitable for the engine.
- a second embodiment of the present invention is a modified form of the first embodiment.
- the control unit 1030 of the second embodiment has a drain line 1082 in addition to the drain line 82 .
- the drain line 1082 opens into the atmosphere, and hydraulic oil can be drained through this line to the oil pan 5 .
- the spool valve 1100 of the control unit 1030 has a drain port 1118 in addition to the drain port 118 .
- the drain port 1118 is open to the atmosphere through the drain line 1082 , and hydraulic oil is drained through the port 1118 to the line 1082 .
- the drain port 1118 is positioned between the retard output port 114 and the sleeve end 110 a.
- the spool 1130 of the spool valve 1100 has a junction passage 1260 in addition to the junction passage 260 .
- the junction passage 1260 enables the retard output port 114 to communicate with the drain port 1118 .
- the junction passage 1260 extends through the retard support land 138 .
- the ends 1261 , 1262 of the junction passage 1260 are open on an outer peripheral surface of the spool 1130 .
- the passage ends 1261 , 1262 communicate with the drain port 1118 at least when the spool 1130 is in the spool position shown in FIG. 11 .
- the passage ends 1261 , 1262 communicate with the space between the retard switch land 136 and the retard support land 138 through the space formed in the sleeve 1110 at the outer peripheral side of the support land 138 .
- the retard switch land 136 is supported only on the side of the retard output port 114 that is adjacent to the input port 116 . This makes the output port 114 communicate with the space between the switch land 136 and the retard support land 138 . Accordingly, when the spool 1130 is in this position, the drain port 1118 and the output port 114 communicate with each other through the junction passage 1260 .
- the ends 1261 , 1262 of the junction passage 1260 are blocked from the space between the lands 136 , 138 , so that the output port 114 is blocked from the drain port 1118 .
- the advance switch land 134 is supported only on the side of the advance output port 112 that is adjacent to the drain port 118 . This makes the output port 112 communicate with the input port 116 through the space between the switch lands 134 , 136 .
- valve timing adjuster 1 advances the valve timing, retards the valve timing, fully retards the valve timing, and holds the valve timing by locating the spool 1130 at the positions shown in FIGS. 12 to 15 , respectively.
- this adjuster 1 fully advances the valve timing by locating the spool 1130 in the position shown in FIG. 11 .
- the valve timing adjuster 1 starts to fully advance the valve timing if a certain operating condition for adjusting the engine phase to the fully advanced phase is satisfied during the operation of the engine at a speed not higher than a set value R.
- the above operating condition may be that the throttle is fully open at an engine speed of 4,000 or less rpm.
- the control circuit 200 controls the current to be supplied to the solenoid 120 at a full advance value Ia0 higher than the advance value Ia.
- the spool 1130 is driven to the full advance phase position shown (second position on the advance side) in FIGS. 11 , 16 , which is a position located in the advance direction away from the advance phase position.
- the full advance phase position and the advance phase position are arranged adjacent to each other in a direction, in which the spool 130 is displaceable.
- the advance connection passage 220 connects the advance output port 112 with the retard output port 114 .
- the advance output port 112 communicates with the input port 116
- the retard output port 114 communicates with the drain port 1118 .
- the set value R may be equal to the set value R for the full retard operation in the first embodiment.
- the oil from the pump 4 is supplied continuously to the advance chambers 52 to 55 , as is the case with the advance operation in the first embodiment. Also, as shown in FIG. 11 , the oil input into the input port 116 flows into the end 221 of the advance connection passage 220 , and the oil in the retard chambers 56 to 59 which is compressed by the action of the negative torque flows into the retard output port 114 . The oil flowing into the retard output port 114 flows into not only the other end 222 of the advance connection passage 220 but also the drain port 1118 , which opens into the atmosphere, so that the pressure of the oil is atmospheric pressure.
- the oil flowing into the passage end 222 which is adjacent to the retard output port 114 , is lower in pressure than the oil flowing into the passage end 221 , which is adjacent to the advance output port 112 .
- This closes the retard connection check valve 230 restraining not only the flow of hydraulic oil from the advance output port 112 to the retard output port 114 but also the oil flow in the opposite direction. Consequently, substantially all part of the oil flowing into the retard output port 114 is drained through the drain port 1118 .
- the oil from the pump 4 also flows into the retard connection passage 240 , as is the case with the advance operation in the first embodiment, but the closure of the retard connection check valve 230 restrains the flow of hydraulic oil toward the end 242 of the passage 240 .
- positive torque is acting on the vane rotor 14 , with the spool 1130 in the full advance operation, as shown in FIG. 16 , the backflow from the advance output port 112 to the connection passages 240 , 220 and the input line 80 is restrained, as is the case with the advance operation in the first embodiment.
- the control circuit 200 may alternatively learn the reference phase Pr 0 during the full advance operation, instead of learning the reference phase Pr 0 during the full retard operation. This makes it possible to increase the accuracy of valve timing adjustment.
- the second embodiment too, can make quick and accurate valve timing adjustment for the engine.
- the drive unit 10 might include an assist spring or another elastic member for biasing the camshaft 2 in a direction opposite from a direction, in which the average value of variable torque is biased or urged.
- the housing 12 of the drive unit 10 might be rotated with the camshaft 2
- the vane rotor 14 of the drive unit 10 might be rotated with the crankshaft.
- connection check valves 210 , 230 of the spool valves 100 , 1100 might be fitted with an elastic member for biasing the corresponding valve member 214 or 234 .
- One end of this elastic member would be in contact with the corresponding valve member 214 or 234 , and the other end would be fixed to the wall of the corresponding connection passage 220 or 240 .
- the solenoid 120 for actuating each of the spools 130 , 1130 of the spool valves 100 , 1100 may be alternatively replaced by a piezoelectric or hydraulic actuator.
- the port 114 of each of the sleeves 110 , 1110 of the spool valves 100 , 1100 may alternatively communicate with the advance chambers 52 to 55 through the corresponding advance output line 72 .
- the port 112 of each of the sleeves 110 , 1110 may alternatively communicate with the retard chambers 56 to 59 through the corresponding retard output line 76 .
- the relation between the advance operation and the retard operation and the relation between the full advance operation and the full retard operation are reverse to those in the first and second embodiments.
- the spool valve 1100 may, as shown in FIG. 17 , not have the drain port 118 and the junction passage 260 .
- the valve timing adjuster 1 may not fully retard the valve timing, and the control circuit 200 may learn the reference phase Pr 0 when the adjuster 1 fully advances the valve timing.
- the present invention can be applied to not only an apparatus for adjusting the valve timing for a intake valve but also an apparatus for adjusting the valve timing for an exhaust valve as a valve and an apparatus for adjusting the valve timing for both a intake valve and an exhaust valve.
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- Valve Device For Special Equipments (AREA)
Abstract
A valve timing adjuster includes a first rotor, a second rotor, a spool valve, a connection passage, and a connection check valve. A spool of the spool valve is displaceable to a first position such that the first rotor is rotated relative to the second rotor. The spool is displaceable to a second position to hold the phase of a camshaft at a full phase. The connection passage connects a first output port with a second output port of the spool valve when the spool is positioned at the first position. The connection check valve of the connection passage allows working fluid to flow from the second output port toward the first output port.
Description
- This application is based on and incorporates herein by reference Japanese Patent Application No. 2008-3604 filed on Jan. 10, 2008.
- 1. Field of the Invention
- The present invention relates to a valve timing adjuster for adjusting a valve of an internal combustion engine, which is opened and closed by a camshaft of the engine through torque transmission from a crankshaft of the engine.
- 2. Description of Related Art
- Hydraulic valve timing adjusters have been used widely, each of which has a housing serving as a driving rotor (first rotor) and a vane rotor serving as a driven rotor (second rotor). The housing rotates synchronously with the crankshaft of an internal combustion engine. The vane rotor rotates synchronously with the camshaft of the engine. JP-A-2006-177344 corresponding to U.S. Pat. No. 7,124,722 discloses a hydraulic valve timing adjuster having a housing and a vane rotor. An advance chamber is defined between one of the shoes of the housing and the corresponding vane of the vane rotor. A retard chamber is defined between the other shoe and the vane. The advance and retard chambers are supplied with working fluid to drive the camshaft relative to the crankshaft in a advance direction and a retard direction, respectively, and thereby adjusting valve timing of the valve of the engine.
- Specifically, the valve timing adjuster disclosed in JP-A-2006-177344 further has a spool valve, which supplies the working fluid from a fluid supply source to the advance or retard chamber by shifting a spool of the spool valve to change a phase (engine phase) of the camshaft relative to the crankshaft. When working fluid is supplied to one of the advance and retard chambers, the working fluid discharged from the other one is utilized again by being supplied to the one of the chambers. Even if the variable torque transmitted from the camshaft to the vane rotor increases the volume of the chamber supplied with working fluid, the increase in volume is filled with the fluid utilized again. This improves the responsibility of the valve timing adjuster. It should be noted that the variable torque (torque reversals) biases the camshaft alternately in the advance and retard directions relative to the crankshaft.
- The valve timing adjuster disclosed in JP-A-2006-177344 further has an advance output line and a retard output line, each of which is fitted with a check valve. The spool valve has an input port, an advance output port, a retard output port, an advance return port, and a retard return port. The advance and retard output ports can communicate with the advance and retard chambers, respectively, through the advance and retard output lines respectively. The advance and retard return ports communicate with intermediate points of the advance and retard output lines respectively.
- For example, the valve timing adjuster retards the engine phase by shifting the spool in the retard direction to connect the advance return port and the retard output port in the spool valve. As a result, the working fluid discharged from the advance chamber to the advance return port is supplied from the retard output port to the retard output line together with the working fluid, which is supplied from the fluid supply source into the input port. The pressure of the output fluid opens the check valve in the retard output line, so that the fluid from the fluid supply source and the advance chamber is supplied to the retard chamber. The fluid is supplied to the retard chamber when positive variable torque, which biases the camshaft in the retard direction relative to the crankshaft, acts on the vane rotor. However, it is difficult to supply the working fluid when negative variable torque, which biases the camshaft in the advance direction relative to the crankshaft, acts on the vane rotor, because the negative variable torque increases the volume of the advance chamber, causing the fluid, which has been supplied into the input port, to flow into the advance chamber through the advance output port.
- The back flow to the advance chamber lowers the responsibility that the valve timing adjuster has when the engine phase changes. The back flow also lowers the stability of the engine phase when the valve timing adjuster holds the phase fully retarded by pressing the vane against the appropriate shoe. The responsibility and the phase stability lower as above when the camshaft is driven or rotated relative to the crankshaft in the advance direction. Therefore, it is demanded that the valve timing adjuster be improved.
- The present invention is made in view of the above disadvantages. Thus, it is an objective of the present invention to address at least one of the above disadvantages.
- To achieve the objective of the present invention, there is provided a valve timing adjuster for an internal combustion engine having a crankshaft, a valve, and a camshaft, wherein the adjuster adjusts valve timing of the valve, which is opened and closed by the camshaft through torque transmission from the crankshaft, the adjuster including a first rotor, a second rotor, a spool valve, a connection passage, and a connection check valve. The first rotor is rotatable synchronously with the crankshaft. The second rotor is rotatable synchronously with the camshaft. The first rotor and the second rotor define therebetween an advance chamber and a retard chamber, which are arranged circumferentially one after another. The second rotor is adapted to drive the camshaft relative to the crankshaft in an advance direction when working fluid is supplied to the advance chamber. The second rotor is adapted to drive the camshaft relative to the crankshaft in a retard direction when working fluid is supplied to the retard chamber. The spool valve includes an input port, a drain port, a first output port, a second output port, and a spool. Working fluid is supplied to the spool valve from an external fluid supply source through the input port. Working fluid is drained through the drain port. Working fluid is output to one of the advance chamber and the retard chamber through the first output port. Working fluid is output to the other one of the advance chamber and the retard chamber through the second output port. The spool is adapted to be displaceable to a first position, at which the first rotor is rotated relative to the second rotor in order to shift a phase of the camshaft relative to the crankshaft. The spool is adapted to be displaceable to a second position, at which the second rotor is pressed against the first rotor in order to hold the phase of the camshaft at a full phase, at which the phase is fully shifted. When the spool is positioned at the first position, the spool valve connects the first output port with the input port and disconnects the second output port from the drain port. When the spool is positioned at the second position, the spool valve connects the first output port with the input port and connects the second output port with the drain port. The connection passage is provided in the spool, wherein the connection passage connects the first output port with the second output port when the spool is positioned at the first position. The connection check valve is provided in the connection passage. The connection check valve opens to allow working fluid to flow from the second output port toward the first output port when the spool is positioned at the first position. The connection check valve closes to limit working fluid from flowing from the first output port toward the second output port when the spool is positioned at the first position.
- 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:
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FIG. 1 is a schematic diagram of a valve timing adjuster according to a first embodiment of the present invention; -
FIG. 2 is a chart showing the variable torque acting on the drive unit of the valve timing adjuster according to the first embodiment; -
FIG. 3 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in an advance position; -
FIG. 4 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in a retard position; -
FIG. 5 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in a full retard position; -
FIG. 6 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in a hold position; -
FIG. 7 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in the advance position; -
FIG. 8 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in the advance position; -
FIG. 9 is an axial sectional view of the spool valve of the valve timing adjuster according to the first embodiment, showing the spool in the retard position; -
FIG. 10 is a schematic diagram of a valve timing adjuster according to a second embodiment of the present invention; -
FIG. 11 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a full advance position; -
FIG. 12 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in an advance position; -
FIG. 13 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a retard position; -
FIG. 14 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a full retard position; -
FIG. 15 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in a hold position; -
FIG. 16 is an axial sectional view of the spool valve of the valve timing adjuster according to the second embodiment, showing the spool in the full advance position; and -
FIG. 17 is an axial sectional view of the spool valve of a valve timing adjuster according to another embodiment of the present inventions this valve being a modified form of the spool valve of the valve timing adjuster according to the second embodiment. - Embodiments of the present invention will be described below with reference to the drawings. The counterparts in the embodiments will be assigned the same reference numerals so that repeated descriptions can be avoided.
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FIG. 1 is a schematic diagram of avalve timing adjuster 1 according to a first embodiment of the present invention. Theadjuster 1 is applied to an internal combustion engine of a vehicle. Theadjuster 1 is a hydraulic valve timing adjuster using hydraulic oil serving as working fluid. Theadjuster 1 adjusts valve timing of an intake valve serving as a “valve” of the engine. - The basic structure of the
valve timing adjuster 1 will be described below. Theadjuster 1 includes adrive unit 10 and acontrol unit 30. Thedrive unit 10 is fitted to a driving force transmission system for transmitting the driving force of a crankshaft (not shown) of the engine to acamshaft 2 of the engine and is driven with hydraulic oil. Thecontrol unit 30 controls the supply of hydraulic oil to thedrive unit 10. - The
drive unit 10 includes ahousing 12 serving as a first rotor (driving rotor), which has acylindrical sprocket 12 a and shoes 12 b to 12 e as partitions. - The
sprocket 12 a is connected to the crankshaft by a timing chain (not shown). While the engine is running, driving force is transmitted from the crankshaft to thesprocket 12 a, so that thehousing 12 rotates with the crankshaft clockwise inFIG. 1 . - The
shoes 12 b to 12 e are formed on the inner periphery of thesprocket 12 a and spaced circumferentially at substantially regular intervals. Theshoes 12 b to 12 e project radially inwardly from thesprocket 12 a and each of theshoes 12 b to 12 e has a radially inner surface that has an arcuate recess shape in section taken perpendicularly to a rotational axis of thehousing 12. Thedrive unit 10 further includes avane rotor 14, which has acylindrical boss 14 a. The radially inner surface of each of theshoes 12 b to 12 e is in slidable contact with an outer peripheral surface of theboss 14 a. Avane chamber 50 is formed betweenadjacent shoes 12 b to 12 c. Anothervane chamber 50 is formed between adjacent shoes 12 c to 12 d. Anothervane chamber 50 is formed betweenadjacent shoes 12 d to 12 e. Anothervane chamber 50 is formed betweenadjacent shoes 12 e to 12 b. - The
vane rotor 14 is a driven rotor (second rotor), which is received in thehousing 12 in axially slidable contact with it. Thevane rotor 14 further hasvanes 14 b to 14 e. - The
boss 14 a is bolted to thecamshaft 2 coaxially with it. Thevane rotor 14 rotates synchronously with thecamshaft 2 clockwise inFIG. 1 and is rotatable relative to thehousing 12. - The
vanes 14 b to 14 e are formed on the outer periphery of theboss 14 a and spaced circumferentially at substantially regular intervals. Each of thevanes 14 b to 14 e is positioned in one of thevane chambers 50. Thevanes 14 b to 14 e radially outwardly project from theboss 14 a, and each of thevanes 14 b to 14 e has a radially outer surface that has an arcuate projecting shape in section taken perpendicularly to the rotational axis of thevane rotor 14. The top face of each of thevanes 14 b to 14 e is in slidable contact with an inner peripheral surface of thesprocket 12 a. - The
vane 14 b and theshoe 12 b define anadvance chamber 52 therebetween in the correspondingvane chamber 50 associated with this vane. Thevane 14 c and the shoe 12 c define anadvance chamber 53 therebetween in the correspondingvane chamber 50. Thevane 14 d and theshoe 12 d define anadvance chamber 54 therebetween in the correspondingvane chamber 50. Thevane 14 e and theshoe 12 e define anadvance chamber 55 therebetween in the correspondingvane chamber 50. Thevane 14 b and the shoe 12 c define aretard chamber 56 therebetween in the correspondingvane chamber 50. Thevane 14 c and theshoe 12 d define aretard chamber 57 therebetween in the correspondingvane chamber 50. Thevane 14 d and theshoe 12 e define aretard chamber 58 therebetween in the correspondingvane chamber 50. Thevane 14 e and theshoe 12 b define aretard chamber 59 therebetween in the correspondingvane chamber 50. - The supply of hydraulic oil to the
advance chambers 52 to 55 turns or rotates thevane rotor 14 in the advance direction relative to thehousing 12, driving thecamshaft 2 in the advance direction relative to the crankshaft. As a result, the engine phase that determines the valve timing is advanced. Continued supply of hydraulic oil to theadvance chambers 52 to 55 presses thevanes shoes - The supply of hydraulic oil to the
retard chambers 56 to 59 turns thevane rotor 14 in the retard direction relative to thehousing 12, driving thecamshaft 2 in the retard direction relative to the crankshaft. This retards the engine phase. Continued supply of hydraulic oil to theretard chambers 56 to 59 presses thevanes 14 b to 14 e in the retard direction against theshoes 12 b to 12 e, respectively, and thereby the engine phase is held fully retarded at a full retard phase (full phase on the retard side). - The
control unit 30 has anadvance output line 72 and aretard output line 76, which lead through thecamshaft 2 and the bearing (not shown) for the camshaft. Theadvance output line 72 communicates with theadvance chambers 52 to 55 in any operational condition of thedrive unit 10. Theretard output line 76 communicates with theretard chambers 56 to 59 in any operational condition of thedrive unit 10. - The
control unit 30 further has aninput line 80, which communicates with the discharge port of apump 4 serving as a fluid supply source. Thepump 4 pumps up hydraulic oil from anoil pan 5 of the engine and discharges the oil to theinput line 80 under a pressure higher than the atmospheric pressure. Thepump 4 is a mechanical pump, which the crankshaft drives. While the engine is running, thepump 4 keeps pumping hydraulic oil into theinput line 80. Thecontrol unit 30 further has adrain line 82, which opens into the atmosphere, and through which hydraulic oil is drained into theoil pan 5. - The
control unit 30 includes aspool valve 100, which is an electromagnetic control valve having asolenoid 120 and aspool 130. Thesolenoid 120 creates electromagnetic driving force in order to linearly reciprocate thespool 130. Thevalve 100 further has anadvance output port 112, aretard output port 114, aninput port 116, and adrain port 118. Thevalve 100 outputs hydraulic oil through theadvance output port 112 and theadvance output line 72 to theadvance chambers 52 to 55. Thevalve 100 outputs hydraulic oil through theretard output port 114 and theretard output line 76 to theretard chambers 56 to 59. The oil from thepump 4 is input through theinput line 80 into theinput port 116. Thedrain port 118 opens into the atmosphere through thedrain line 82. Thevalve 100 drains hydraulic oil through thedrain port 118 into thedrain line 82. According to the electric current supply to thesolenoid 120, the solenoid reciprocates thespool 130 such that ports communicated with theinput port 116 and thedrain port 118, respectively, are selected among theoutput ports - The
control unit 30 further includes acontrol circuit 200, the main component of which is a microcomputer having amemory 200 a. Thecontrol circuit 200 is connected electrically to thesolenoid 120. Thecontrol circuit 200 controls the current supply to thesolenoid 120 and the operation of the engine. In the present embodiment, thecontrol circuit 200 is connected electrically to a cranksensor 202 that senses the rotation of the crankshaft and acam sensor 204 that senses the rotation of thecamshaft 2. Thesensors solenoid 120 and the operation of the engine. - According to the current supply from the
control circuit 200 to thesolenoid 120, thespool valve 100 controls the position of thespool 130. When thespool 130 is in a certain position, where theinput port 116 communicates with theadvance output port 112, the oil supplied from thepump 4 to theinput line 80 is output by thevalve 100 to theadvance output line 72, and thereby the oil is supplied to theadvance chambers 52 to 55. When thespool 130 is in another position, where theinput port 116 communicates with theretard output port 114, the oil supplied from thepump 4 to theinput line 80 is output by thevalve 100 to theretard output line 76, and thereby the oil is supplied to theretard chambers 56 to 59. When thespool 130 is in the spool position where thedrain port 118 communicates with theadvance output port 112, thevalve 100 can drain the oil in theadvance chambers 52 to 55 to theoil pan 5 through theadvance output line 72 and thedrain line 82. - Characteristics of the
valve timing adjuster 1 will be described below in detail. - While the engine is running, variable torque (torque reversals) caused by the spring reaction force of a valve spring of the intake valve, which the
camshaft 2 drives. The variable torque is transmitted through thecamshaft 2 and acts on thevane rotor 14. As shown inFIG. 2 , the variable torque alternates periodically between negative torque and positive torque, which bias thecamshaft 2 in the advance and retard directions respectively relative to the crankshaft. The peak positive torque T+ and the peak negative torque Tto may be substantially equal to each other in absolute value, so that the average variable torque may be substantially zero. Alternatively, the peak positive torque T+ may be greater in absolute value than the peak negative torque Tto, so that the average variable torque may deflect positively. - As shown in
FIG. 3 , thespool valve 100 further has asleeve 110, a drivingshaft 139, and areturn spring 140. - The
sleeve 110 is metallic and has a hollow cylindrical shape. Thesolenoid 120 is fixed to oneend 110 a of thesleeve 110. Theretard output port 114, theinput port 116, theadvance output port 112, and thedrain port 118 are formed in thesleeve 110 in this order in a direction away from thesleeve end 110 a toward theother sleeve end 110 b. - The
spool 130 is metallic, and has a column shape with lands formed thereon, and positioned in thesleeve 110 coaxially with thesleeve 110. Oneend 130 a of thespool 130 is connected coaxially with the drivingshaft 139. Thesolenoid 120 drives theshaft 139 electromagnetically to move thespool 130 axially with the shaft. Thespool 130 has anadvance support land 132, anadvance switch land 134, aretard switch land 136, and aretard support land 138, which are formed in this order in a direction away from the other spool end 130 b toward the spool end 130 a. - The
advance support land 132 is supported slidably by the portion of thesleeve 110 that lies between theadvance output port 112 and thedrain port 118. Theadvance switch land 134 is supported slidably by at least one of the above portion of thesleeve 110 and the other portion of thesleeve 110 that lies between theadvance output port 112 and theinput port 116. When thespool 130 is in the position shown inFIG. 3 , where theadvance switch land 134 is supported only by the sleeve portion between theadvance output port 112 and thedrain port 118, theadvance output port 112 communicates with theinput port 116 through the space between the switch lands 134, 136. When thespool 130 is in the spool position shown inFIG. 4 or 5, where theadvance switch land 134 is supported only by the sleeve portion between theadvance output port 112 and theinput port 116, thisoutput port 112 communicates with the space between theadvance support land 132 and theadvance switch land 134. When thespool 130 is in the spool position shown inFIG. 6 , where theadvance switch land 134 is supported by both the portion of thesleeve 110 that lies between theadvance output port 112 and thesleeve end 110 b and the sleeve portion betweenadvance output port 112 and theinput port 116, theadvance output port 112 is blocked from theother ports - As shown in
FIG. 3 , theretard support land 138 is supported slidably by a portion of thesleeve 110 that lies between theretard output port 114 and thesleeve end 110 a. Theretard switch land 136 is supported slidably by at least one of the above portion of thesleeve 110 and the other portion of thesleeve 110 that lies between theretard output port 114 and theinput port 116. When thespool 130 is in the position shown inFIG. 4 or 5, where theretard switch land 136 is supported only by the sleeve portion between theretard output port 114 and thesleeve end 110 a, thisoutput port 114 communicates with theinput port 116 through the space between the switch lands 134, 136. When thespool 130 is in the spool position shown inFIG. 3 , where theretard switch land 136 is supported only by the sleeve portion between theretard output port 114 and theinput port 116, theretard output port 114 communicates with the space between theretard switch land 136 and theretard support land 138. When thespool 130 is in the spool position shown inFIG. 6 , where theretard switch land 136 is supported by the sleeve portions on both sides of theretard output port 114, theretard output port 114 is blocked from theother ports - As shown in
FIGS. 3 to 6 , theinput port 116 communicates with the space between the switch lands 134, 136 regardless of the position of thespool 130. - The
return spring 140 is a metallic compression coil spring, which is positioned in thesleeve 110 coaxially with thesleeve 110. Thespring 140 is positioned in thesleeve 110 between thesleeve end 110 b and theadvance support land 132 of thespool 130. The compressive deformation of thespring 140 creates a restoring force that biases thespool 130 axially toward thesolenoid 120. The current supply to thesolenoid 120 creates an electromagnetic driving force that biases thespool 130 with the drivingshaft 139 axially toward thespring 140. Accordingly, thespool 130 is driven according to the balance between the restoring force created by thespring 140 and the electromagnetic driving force created by thesolenoid 120. - As shown in
FIGS. 1 , 3, the present embodiment is characterized byconnection check valves connection passages spool 130. - As shown in
FIG. 3 , oneend 221 of theadvance connection passage 220 opens at a peripheral surface of thespool 130 between the switch lands 134, 136 at multiple positions. Accordingly, as shown inFIGS. 3 to 6 , thepassage end 221 communicates with the space between the switch lands 134, 136, regardless of the position of thespool 130. In particular when thespool 130 is in the spool position shown inFIG. 3 , thepassage end 221 communicates with theadvance output port 112 and theinput port 116 through the space between the switch lands 134, 136. - The
other end 222 of theadvance connection passage 220 opens at the peripheral surface of thespool 130 between theretard switch land 136 and theretard support land 138 at multiple positions. Accordingly, as shown inFIGS. 3 to 6 , thispassage end 222 communicates with the space between theselands spool 130. In particular, when thespool 130 is in the spool position shown inFIG. 3 , theadvance connection passage 220 communicates with theadvance output port 112 as stated above, and theend 222 of theadvance connection passage 220 communicates with theretard output port 114 through the space between thelands spool 130 is in this position, theoutput ports advance connection passage 220. - The advance
connection check valve 210 closes to limit fluid from flowing in a direction from theend 221 of theadvance connection passage 220 toward theother end 222. Also, the advanceconnection check valve 210 opens to allow fluid to flow in the opposite direction opposite from the above. The advanceconnection check valve 210 includes anadvance valve seat 212, anadvance valve member 214, anadvance retainer 215, and anelastic member 216. - The
advance valve seat 212 is a conical wall of theadvance connection passage 220, and the conical wall has a diameter that becomes smaller toward theend 222 of theadvance connection passage 220. Theadvance retainer 215 is positioned between theadvance valve seat 212 and theother end 221 of theadvance connection passage 220. Theadvance valve member 214 is positioned between theadvance valve seat 212 and theadvance retainer 215. The retardconnection check valve 230 is positioned between the advanceconnection check valve 210 and thespool end 110 b. Theelastic member 216 is interposed between the retardconnection check valve 230 and theadvance retainer 215. Theadvance valve member 214 is a metallic ball and is axially movable in theadvance connection passage 220 such that theadvance valve member 214 is brought into and out of contact with theadvance valve seat 212. Theadvance retainer 215 is metallic and has aperipheral wall part 215 a and a bottom. Theperipheral wall part 215 a is supported by the inner peripheral wall of theadvance connection passage 220 and receives theadvance valve member 214 therein. Theadvance retainer 215 is axially slidable in theadvance connection passage 220. Theelastic member 216 is a metallic compression spring. The compressive deformation of theelastic member 216 creates a restoring force, which biases theadvance retainer 215 together with theadvance valve member 214 toward theadvance valve seat 212. - When the
end 222 of theadvance connection passage 220 is higher in pressure than theother end 221, theadvance valve member 214 moves toward theend 221 out of contact with theadvance valve seat 212 as shown inFIG. 3 . This opens the advanceconnection check valve 210, allowing hydraulic oil to flow from thepassage end 222 to theother passage end 221. - When the
end 222 of theadvance connection passage 220 is lower in pressure than theother end 221, theadvance valve member 214 moves toward theend 222 into contact with theadvance valve seat 212 as shown inFIGS. 4 to 6 . This closes the advanceconnection check valve 210, restraining the flow of hydraulic oil from thepassage end 221 to theother passage end 222. - As shown in
FIG. 3 , theend 221 of theadvance connection passage 220, which communicates with the space between the switch lands 134, 136, serves also as one end of theretard connection passage 240. In other words, thepassage end 221 is common to or shared by theconnection passages spool 130 is in the spool position shown inFIG. 4 or 5, thecommon passage end 221 communicates with theretard output port 114 and theinput port 116 through the space between the switch lands 134, 136. - The
other end 242 of theretard connection passage 240 opens at the peripheral surface of thespool 130 between theadvance support land 132 and theadvance switch land 134 at multiple positions. Accordingly, as shown inFIGS. 3 to 6 , thispassage end 242 communicates with the space between theselands spool 130 is positioned. In particular, when thespool 130 is in the spool position shown inFIG. 4 or 5, theretard connection passage 240 communicates with theretard output port 114 as stated above, and theend 242 of theretard connection passage 240 communicates with theadvance output port 112 through the space between thelands spool 130 is in this position, theoutput ports retard connection passage 240. - The retard
connection check valve 230 closes to limit fluid from flowing in a direction from thecommon end 221 of theretard connection passage 240 toward theother end 242. Also, the retardconnection check valve 230 opens to allow fluid to flow in the opposite direction opposite from the above. The retardconnection check valve 230 is similar in structure to the advanceconnection check valve 210. Specifically, the retardconnection check valve 230 includes aretard valve seat 232, aretard valve member 234, aretard retainer 235, and theelastic member 216. - The
retard valve seat 232 is a conical wall of theretard connection passage 240, and the conical wall has a diameter that becomes smaller toward theend 242 of this passage. Theretard retainer 235 is positioned between theretard valve seat 232 and thecommon passage end 221. Theretard valve member 234 is positioned between theretard valve seat 232 and theretard retainer 235. Theelastic member 216 is interposed between theretard retainer 235 and theadvance retainer 215. Theretard valve member 234 is axially movable in theretard connection passage 240 such that theretard valve member 234 is brought into and out of contact with theretard valve seat 232. Theretard retainer 235 has aperipheral wall part 235 a and a bottom. Theperipheral wall part 235 a is supported by an inner peripheral wall of theretard connection passage 240 and receives theretard valve member 234 therein. The restoring force created by the compressive deformation of theelastic member 216 biases theretard retainer 235 together with theretard valve member 234 toward theretard valve seat 232. - When the
end 242 of theretard connection passage 240 is higher in pressure than thecommon end 221, theretard valve member 234 moves toward thecommon end 221 such that theretard valve member 234 becomes out of contact with or disengaged from theretard valve seat 232 as shown inFIG. 4 . As a result, the retardconnection check valve 230 opens and allows hydraulic oil to flow in a direction from thepassage end 242 to thecommon passage end 221. - When the
end 242 of theretard connection passage 240 is lower in pressure than thecommon end 221, theretard valve member 234 moves toward theend 242 such that theretard valve member 234 is brought into contact with or becomes engaged with theretard valve seat 232 as shown inFIGS. 3 , 5 to 9. As a result, the retardconnection check valve 230 closes and limits the hydraulic oil from flowing in a direction from thecommon passage end 221 to theother passage end 242. - The present embodiment is also characterized by a
junction passage 260 formed in thespool 130 so that theadvance output port 112 can communicate with thedrain port 118, as shown inFIGS. 1 , 5. - Specifically, as shown in
FIG. 5 , thejunction passage 260 has anopen end 261 formed at thespool end 130 b inside theadvance support land 132. At least when thespool 130 is in the spool position shown inFIG. 5 , thepassage end 261 communicates with thedrain pod 118 through the space between thespool end 130 b and theadjacent sleeve end 110 b. - The
other end 262 of thejunction passage 260 open to the peripheral wall of thespool 130 at theadvance support land 132 at multiple positions. When thespool 130 is in the spool position shown inFIG. 5 , thepassage end 262 communicates with the space between theadvance support land 132 and theadvance switch land 134 through the space between the inner periphery of thesleeve 110 and the outer periphery of thesupport land 132. When thespool 130 is in the above position, thejunction passage 260 communicates with thedrain port 118, and the space between thelands advance output port 112, as stated above. Accordingly, theseports junction passage 260. When thespool 130 is in the spool position shown inFIG. 3 , 4, or 6, thepassage end 262 is blocked from the space between thelands advance output port 112 is blocked from thedrain port 118. - As shown in
FIGS. 1 , 3, theinput line 80, which communicates with thepump 4 and theinput port 116, is fitted with aninput check valve 280. When one end of theinput line 80 that is connected to thepump 4 is higher in pressure than the other end, which is connected to thespool valve 100, theinput check valve 280 opens, as shown inFIGS. 3 to 6 . This allows hydraulic oil to flow from thepump 4 to theinput port 116. When the other end of theinput line 80 that is connected to thespool valve 100 is higher in pressure than the one end, theinput check valve 280 closes, as shown inFIGS. 7 to 9 . This restrains the flow of hydraulic oil from theinput port 116 to thepump 4. - During the operation of the engine, where the
pump 4 driven, thecontrol circuit 200 calculates the actual engine phase Pr and target engine phase Pt of thecamshaft 2 relative to the crankshaft. Based on the calculated phases Pr and Pt, thecontrol circuit 200 controls the current supply to thesolenoid 120 of thespool valve 100. This controls the position of thespool 130 of thespool valve 100. According to the controlled position, thespool valve 100 supplies hydraulic oil to or discharge hydraulic oil from theadvance chambers 52 to 55 or theretard chambers 56 to 59. This adjusts the engine phase, thereby adjusting the valve timing. The valve timing adjustment through thevalve timing adjuster 1 will be described below in detail. - In the advance operation, the
valve timing adjuster 1 advances the valve timing by varying the engine phase of thecamshaft 2 relative to the crankshaft in the advance direction as follows. - When an operating condition representing the off-state of the accelerator of the engine or representing the low-speed or medium-speed high-load operating state of the engine is satisfied, the
control circuit 200 controls the current to be supplied to thesolenoid 120 at a specified advance value Ia. As a result, thespool 130 is shifted to the advance phase position (first position on the advance side) shown inFIGS. 3 , 7. When thespool 130 is in the advance phase position, theadvance connection passage 220 connects theretard output port 114 with theadvance output port 112 communicating with theinput port 116 and blocked from thedrain port 118. - While negative torque is acting on the
vane rotor 14, in the advance operation, as shown inFIG. 3 , hydraulic oil is input from thepump 4 through theinput line 80 into theinput port 116 and supplied to theadvance chambers 52 to 55 through theadvance output port 112 and theadvance output line 72. Also, in theadvance connection passage 220, the oil input into theinput port 116 flows into thecommon end 221 of thepassage 220, and the oil compressed by the action of the negative torque in theretard chambers 56 to 59 flows into theother end 222 of thepassage 220 through theretard output port 114. The oil flowing into thepassage end 222, which is currently adjacent to theretard output port 114, is higher in pressure than the oil flowing into thecommon passage end 221, which is currently adjacent to theadvance output port 112. As a result, the advanceconnection check valve 210 opens, allowing hydraulic oil to flow from theretard output port 114 to theadvance output port 112. In a case, where the amount of hydraulic oil input from thepump 4 into thespool valve 100 decreases, thevalve 100 is capable of being supplied with hydraulic oil through theretard output port 114. This limits the shortage of hydraulic oil in theadvance chambers 52 to 55 that is increased in volume by the action of the negative torque. - While negative torque is acting on the
vane rotor 14 in the advance operation, the oil from thepump 4 also flows into theretard connection passage 240 communicating with theadvance output port 112 through thecommon passage end 221, but the closure of the retardconnection check valve 230 restrains the flow of hydraulic oil toward theother end 242 of thepassage 240. Also, theadvance output port 112 communicating with theadvance connection passage 220 through thecommon passage end 221 is blocked or discommunicated from thedrain port 118. This restrains the drain of hydraulic oil through thedrain port 118. - While positive torque is acting on the
vane rotor 14 in the advance operation, theadvance chambers 52 to 55 are compressed. As a result, as shown inFIG. 7 , hydraulic oil is forced to flow back through theadvance output port 112 to theconnection passages input line 80. At this time, the closure of theconnection check valves connection passages retard output port 114 and thepassage end 242 respectively. Also, the closure of theinput check valve 280 restrains the flow of hydraulic oil through theinput line 80 toward thepump 4. Thus, hydraulic oil is restrained from flowing back through theadvance output port 112 to theconnection passages input line 80. This not only restrains hydraulic oil from flowing out of theadvance chambers 52 to 55 but also prevents erroneous supply of hydraulic oil to theretard chambers 56 to 59. - The advance operation of advancing the valve timing enables the
connection check valves retard chambers 56 to 59 and supply a sufficient amount of hydraulic oil to theadvance chambers 52 to 55. This enables high advance responsibility. - IN a retard operation of retarding the valve timing, The
valve timing adjuster 1 retards the valve timing by varying the engine phase or phase relation of thecamshaft 2 relative to the crankshaft in the retard direction as follows. - When an operating condition representing the light-load normal operating state is satisfied, the
control circuit 200 controls the current to be supplied to thesolenoid 120 at a retard value Ir that is smaller than the advance value Ia. As a result, thespool 130 is shifted to the retard phase position (first position on the retard side) shown inFIGS. 4 , 8. When thespool 130 is in the above position, theretard connection passage 240 connects theretard output port 114 to theadvance output port 112. In the above, theretard output port 114 communicates with theinput port 116, and theadvance output port 112 is blocked from thedrain port 118. - While positive torque is acting on the
vane rotor 14 in the retard operation, hydraulic oil is input from thepump 4 through theinput line 80 into theinput port 116 and supplied through theretard output port 114 and theretard output line 76 to theretard chambers 56 to 59 as shown inFIG. 4 . Also, the oil input into theinput port 116 flows into thecommon end 221 of theretard connection passage 240, and the oil compressed by the positive torque in theadvance chambers 52 to 55 flows through theadvance output port 112 into theother end 242 of thepassage 240. The oil flowing into thepassage end 242, which is currently adjacent to theadvance output port 112, is higher in pressure than the oil flowing into thecommon passage end 221, which is currently adjacent to theretard output port 114. As a result, the retardconnection check valve 230 opens and allows hydraulic oil to flow in a direction from theadvance output port 112 to theretard output port 114. If the amount of hydraulic oil being input from thepump 4 into thespool valve 100 decreases, thevalve 100 is capable of being supplied with hydraulic oil through theadvance output port 112. This limits the shortage of hydraulic oil in theretard chambers 56 to 59, a volume of each of which has been increased by the positive torque. - While positive torque is acting on the
vane rotor 14 in the retard operation, the oil from thepump 4 also flows into theadvance connection passage 220 communicating with theretard output port 114 through thecommon passage end 221, but the closure of the advanceconnection check valve 210 restrains the flow of hydraulic oil toward theother end 222 of thepassage 220. Also, theadvance output port 112 communicating with theretard connection passage 240 through thepassage end 242 is blocked from thedrain port 118. This restrains the drain of hydraulic oil through thedrain port 118. - While negative torque is acting on the
vane rotor 14 in the retard operation, theretard chambers 56 to 59 are compressed. As a result, as shown inFIG. 8 , hydraulic oil is forced to flow back through theretard output port 114 to theconnection passages input line 80. At this time, the closure of theconnection check valves connection passages advance output port 112 and thepassage end 222, respectively. Also, the closure of theinput check valve 280 restrains the flow of hydraulic oil through theinput line 80 toward thepump 4. Thus, hydraulic oil is restrained from flowing back through theretard output port 114 to theconnection passages input line 80. This not only restrains the flow of hydraulic oil out of theretard chambers 56 to 59 but also prevents erroneous supply of hydraulic oil to theadvance chambers 52 to 55. - The retard operation of the valve timing enables the
connection check valves advance chambers 52 to 55 and supply a sufficient amount of hydraulic oil to theretard chambers 56 to 59. This enables high retard responsibility. - In a full retard operation, the
valve timing adjuster 1 retards the valve timing to the maximum or to the full by holding the engine phase fully retarded as follows. - When an operating condition representing (a) an operational condition immediately after the start of the engine or (b) an operational condition (for example, the off-state of the throttle) for adjusting the engine phase to the full retard phase while the engine is rotating at a speed not higher than a set value R is satisfied, the
control circuit 200 controls the current to be supplied to thesolenoid 120 at a full retard value Ir0 smaller than the retard value Ir. As a result, thespool 130 is driven to the full retard phase position (second position on the retard side) shown inFIGS. 5 , 9, which is a position located in the retard direction away from the retard phase position shown inFIGS. 4 , 8. Thus, the full retard phase position and the retard phase position are arranged adjacent to each other in a direction, in which thespool 130 is displaceable. When thespool 130 is in the full retard phase position, theretard connection passage 240 connects theretard output port 114 communicating with theinput port 116 to theadvance output port 112 communicating with thedrain port 118. The set value R may be a low engine speed (for example, 500 to 1,400 rpm) at which the rotation of thedrive unit 10 less influences the engine phase. - In this case, the latest reference phase is learned when the engine has started. This contributes to the improvement in the accuracy in valve timing adjustment. In this case, because the engine rotates at a relatively low speed when the start of the engine has been completed, it is possible to learn the reference phase while the
housing 12 and thevane rotor 14 rotate with weak or slight vibration. This, too, contributes to the improvement in the adjustment accuracy. - While positive torque is acting on the
vane rotor 14 in the full retard operation, the oil from thepump 4 is supplied continuously to theretard chambers 56 to 59, as is the case with the retard operation. Also, as shown inFIG. 5 , the oil input into theinput port 116 flows into thecommon end 221 of theretard connection passage 240, and the oil compressed by the action of the positive torque in theadvance chambers 52 to 55 flows into theadvance output port 112. The oil flowing into theadvance output port 112 then flows into not only theother end 242 of theretard connection passage 240 but also thedrain port 118, which is open to the atmosphere, so that the pressure of the oil becomes the atmospheric pressure. As a result, the oil flowing into thepassage end 242, which is currently adjacent to theadvance output port 112, is lower in pressure than the oil flowing into thecommon passage end 221, which is currently adjacent to theretard output port 114. This closes the retardconnection check valve 230, restraining not only the flow of hydraulic oil from theretard output port 114 to theadvance output port 112 but also the oil flow in the opposite direction. Accordingly, a substantial part of the oil flowing into theadvance output port 112 is drained through thedrain port 118. This makes it possible to empty theadvance chambers 52 to 55 so that thevanes 14 b to 14 e is capable of being pressed reliably against theshoes 12 b to 12 e respectively. Thus, the fully retarded engine phase is capable of being held reliably and stably. - When the
spool 130 is in the full retard phase position (second position on the retard side), theconnection passage 240 connects theretard output port 114 and the advance output port 112 (first and second output ports) as is the case when thespool 130 is in the retard position (first position on the retard side). In the above connection state, working fluid is discharged from the advance chamber through theadvance output port 112 to theconnection passage 240, and thereby the communication between theadvance output port 112 and thedrain port 118 opening to atmosphere causes pressure at theend 242 of theconnection passage 240 that is adjacent to theadvance output port 112 to be lower than pressure at theother end 221, which is adjacent to theretard output port 114 communicating with theinput port 116. As a result, theconnection check valve 230 closes, and thereby limiting working fluid from flowing through theconnection passage 240 between the advance and retardoutput ports valve timing adjuster 1 in structure by arranging the first position and the second position adjacent to each other and by making theconnection passage 240 commonly provide connection between the advance and retardoutput ports spool 130 is positioned at either of the above first and second positions. This also makes it possible to stabilize the engine phase by draining working fluid quickly from the advance chamber through theoutput port 112 to thedrain port 118. - As is the case with the retard operation, while positive torque is acting on the
vane rotor 14 in the full retard operation, the oil from thepump 4 also flows into theadvance connection passage 220, but the closure of the advanceconnection check valve 210 restrains the flow of hydraulic oil toward theend 222 of thepassage 220. As is the case with the retard operation, while negative torque is acting on thevane rotor 14 in the position full retard operation, hydraulic oil is restrained from flowing back from theretard output port 114 to theconnection passages input line 80, as shown inFIG. 9 . - During the full retard operation, the
control circuit 200 monitors the actual engine phase Pr, which is calculated from the signals from thecrank sensor 202 and thecam sensor 204. Thecontrol circuit 200 learns a stable value of the monitored phase Pr (actual phase) as a reference phase Pr0, which is stored in amemory 200 a of thecontrol circuit 200. The reference phase Pr0 is updated every time thecontrol circuit 200 learns a stable value of the monitored phase Pr. For example, the above operation of learning the reference phase Pr0 using the monitored phase Pr is defined as learning of the reference phase Pr0 in the present embodiment. Accordingly, based on the latest reference phase Pr0 stored in thememory 200 a, thecontrol circuit 200 calculates the present actual engine phase Pr and the present target phase Pt, which are necessary for controlling the current supply to thesolenoid 120. As stated above, the fully retarded engine phase is capable of being held effectively stably when thecontrol circuit 200 learns the reference phase Pr0. This makes it possible to increase the accuracy of valve timing adjustment by realizing current supply control based on accurate reference phase Pr0. - In a normal hold operation, the
valve timing adjuster 1 keeps the valve timing by holding the engine phase within a specified target phase range excluding the full retard phase, as follows. - If an operating condition representing the stable operating state of the engine, such as holding of the accelerator at a certain position, is satisfied, the
control circuit 200 controls the current to be supplied to thesolenoid 120 at a normal hold value In smaller than the advance value la and larger than the retard value Ir. As a result, thespool 130 is shifted to the normal hold operation position shown inFIG. 6 . When thespool 130 is in the above position, both of theoutput ports input port 116 and thedrain port 118. - Accordingly, the oil input from the pump through the
input line 80 to theinput port 116 is not supplied to the advance and retardchambers 52 to 59, and hydraulic oil is restrained from flowing out of the advance and retardchambers 52 to 59. This makes it possible to restrain engine phase changes within the target phase range to hold the valve timing that corresponds to the target phase range. - When the
spool 130 is in the Normal Hold Operation position, the oil from thepump 4 flows through theinput port 116 into thecommon end 221 of theconnection passages connection check valves common end 221 toward the other ends 222, 242. - Thus, the first embodiment enables quick and accurate valve timing adjustment suitable for the engine.
- As shown in
FIG. 10 , a second embodiment of the present invention is a modified form of the first embodiment. Thecontrol unit 1030 of the second embodiment has adrain line 1082 in addition to thedrain line 82. Thedrain line 1082 opens into the atmosphere, and hydraulic oil can be drained through this line to theoil pan 5. - The
spool valve 1100 of thecontrol unit 1030 has adrain port 1118 in addition to thedrain port 118. Thedrain port 1118 is open to the atmosphere through thedrain line 1082, and hydraulic oil is drained through theport 1118 to theline 1082. As shown inFIG. 11 , thedrain port 1118 is positioned between theretard output port 114 and thesleeve end 110 a. - As shown in
FIG. 10 , thespool 1130 of thespool valve 1100 has ajunction passage 1260 in addition to thejunction passage 260. Thejunction passage 1260 enables theretard output port 114 to communicate with thedrain port 1118. As shown inFIG. 11 , thejunction passage 1260 extends through theretard support land 138. The ends 1261, 1262 of thejunction passage 1260 are open on an outer peripheral surface of thespool 1130. The passage ends 1261, 1262 communicate with thedrain port 1118 at least when thespool 1130 is in the spool position shown inFIG. 11 . When thespool 1130 is in this position, the passage ends 1261, 1262 communicate with the space between theretard switch land 136 and theretard support land 138 through the space formed in thesleeve 1110 at the outer peripheral side of thesupport land 138. - When the
spool 1130 is in the spool position shown inFIG. 11 , theretard switch land 136 is supported only on the side of theretard output port 114 that is adjacent to theinput port 116. This makes theoutput port 114 communicate with the space between theswitch land 136 and theretard support land 138. Accordingly, when thespool 1130 is in this position, thedrain port 1118 and theoutput port 114 communicate with each other through thejunction passage 1260. When thespool 1130 is in the spool position shown in one ofFIGS. 12 to 15 , theends junction passage 1260 are blocked from the space between thelands output port 114 is blocked from thedrain port 1118. - When the
spool 1130 is in the spool position shown inFIG. 11 , theadvance switch land 134 is supported only on the side of theadvance output port 112 that is adjacent to thedrain port 118. This makes theoutput port 112 communicate with theinput port 116 through the space between the switch lands 134, 136. - Similarly to the first embodiment, the
valve timing adjuster 1 according to the second embodiment advances the valve timing, retards the valve timing, fully retards the valve timing, and holds the valve timing by locating thespool 1130 at the positions shown inFIGS. 12 to 15 , respectively. In addition, thisadjuster 1 fully advances the valve timing by locating thespool 1130 in the position shown inFIG. 11 . - Specifically, the
valve timing adjuster 1 according to the second embodiment starts to fully advance the valve timing if a certain operating condition for adjusting the engine phase to the fully advanced phase is satisfied during the operation of the engine at a speed not higher than a set value R. The above operating condition may be that the throttle is fully open at an engine speed of 4,000 or less rpm. In the full advance operation of valve timing of theadjuster 1, thecontrol circuit 200 controls the current to be supplied to thesolenoid 120 at a full advance value Ia0 higher than the advance value Ia. As a result, thespool 1130 is driven to the full advance phase position shown (second position on the advance side) inFIGS. 11 , 16, which is a position located in the advance direction away from the advance phase position. Thus, the full advance phase position and the advance phase position are arranged adjacent to each other in a direction, in which thespool 130 is displaceable. When thespool 1130 is in the full advance phase position, theadvance connection passage 220 connects theadvance output port 112 with theretard output port 114. In the above, theadvance output port 112 communicates with theinput port 116, and theretard output port 114 communicates with thedrain port 1118. The set value R may be equal to the set value R for the full retard operation in the first embodiment. - While negative torque is acting on the
vane rotor 14, in the full advance operation, the oil from thepump 4 is supplied continuously to theadvance chambers 52 to 55, as is the case with the advance operation in the first embodiment. Also, as shown inFIG. 11 , the oil input into theinput port 116 flows into theend 221 of theadvance connection passage 220, and the oil in theretard chambers 56 to 59 which is compressed by the action of the negative torque flows into theretard output port 114. The oil flowing into theretard output port 114 flows into not only theother end 222 of theadvance connection passage 220 but also thedrain port 1118, which opens into the atmosphere, so that the pressure of the oil is atmospheric pressure. As a result, the oil flowing into thepassage end 222, which is adjacent to theretard output port 114, is lower in pressure than the oil flowing into thepassage end 221, which is adjacent to theadvance output port 112. This closes the retardconnection check valve 230, restraining not only the flow of hydraulic oil from theadvance output port 112 to theretard output port 114 but also the oil flow in the opposite direction. Consequently, substantially all part of the oil flowing into theretard output port 114 is drained through thedrain port 1118. This makes it possible to empty theretard chambers 56 to 59 so that thevanes 14 b to 14 e are pressed in the advance direction reliably against theshoes 12 b to 12 e. Thus, it is possible to stably hold the engine phase fully advanced. - While negative torque is acting on the
vane rotor 14 in the full advance operation, the oil from thepump 4 also flows into theretard connection passage 240, as is the case with the advance operation in the first embodiment, but the closure of the retardconnection check valve 230 restrains the flow of hydraulic oil toward theend 242 of thepassage 240. While positive torque is acting on thevane rotor 14, with thespool 1130 in the full advance operation, as shown inFIG. 16 , the backflow from theadvance output port 112 to theconnection passages input line 80 is restrained, as is the case with the advance operation in the first embodiment. Thecontrol circuit 200 may alternatively learn the reference phase Pr0 during the full advance operation, instead of learning the reference phase Pr0 during the full retard operation. This makes it possible to increase the accuracy of valve timing adjustment. - The second embodiment, too, can make quick and accurate valve timing adjustment for the engine.
- The present invention should not be interpreted as limited to the above first and second embodiments but may be embodied into various forms without departing from the spirit of the present invention.
- In each of the embodiments, the
drive unit 10 might include an assist spring or another elastic member for biasing thecamshaft 2 in a direction opposite from a direction, in which the average value of variable torque is biased or urged. Thehousing 12 of thedrive unit 10 might be rotated with thecamshaft 2, and thevane rotor 14 of thedrive unit 10 might be rotated with the crankshaft. - Each of the
connection check valves spool valves valve member valve member corresponding connection passage - The
solenoid 120 for actuating each of thespools spool valves port 114 of each of thesleeves spool valves advance chambers 52 to 55 through the correspondingadvance output line 72. Theport 112 of each of thesleeves retard chambers 56 to 59 through the correspondingretard output line 76. In the above alternative case, the relation between the advance operation and the retard operation and the relation between the full advance operation and the full retard operation are reverse to those in the first and second embodiments. - The
spool valve 1100 may, as shown inFIG. 17 , not have thedrain port 118 and thejunction passage 260. In this case, thevalve timing adjuster 1 may not fully retard the valve timing, and thecontrol circuit 200 may learn the reference phase Pr0 when theadjuster 1 fully advances the valve timing. - The present invention can be applied to not only an apparatus for adjusting the valve timing for a intake valve but also an apparatus for adjusting the valve timing for an exhaust valve as a valve and an apparatus for adjusting the valve timing for both a intake valve and an exhaust valve.
- 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 (8)
1. A valve timing adjuster for an internal combustion engine having a crankshaft, a valve, and a camshaft, wherein the adjuster adjusts valve timing of the valve, which is opened and closed by the camshaft through torque transmission from the crankshaft, the adjuster comprising:
a first rotor that is rotatable synchronously with the crankshaft;
a second rotor that is rotatable synchronously with the camshaft, wherein:
the first rotor and the second rotor define therebetween an advance chamber and a retard chamber, which are arranged circumferentially one after another;
the second rotor is adapted to drive the camshaft relative to the crankshaft in an advance direction when working fluid is supplied to the advance chamber; and
the second rotor is adapted to drive the camshaft relative to the crankshaft in a retard direction when working fluid is supplied to the retard chamber;
a spool valve that includes:
an input port, through which working fluid is supplied to the spool valve from an external fluid supply source;
a drain port, through which working fluid is drained;
a first output port, through which working fluid is output to one of the advance chamber and the retard chamber;
a second output port, through which working fluid is output to the other one of the advance chamber and the retard chamber; and
a spool that is adapted to be displaceable to a first position, at which the first rotor is rotated relative to the second rotor in order to shift a phase of the camshaft relative to the crankshaft, wherein:
the spool is adapted to be displaceable to a second position, at which the second rotor is pressed against the first rotor in order to hold the phase of the camshaft at a full phase, at which the phase is fully shifted;
when the spool is positioned at the first position, the spool valve connects the first output port with the input port and disconnects the second output port from the drain port; and
when the spool is positioned at the second position, the spool valve connects the first output port with the input port and connects the second output port with the drain port;
a connection passage that is provided in the spool, wherein the connection passage connects the first output port with the second output port when the spool is positioned at the first position; and
a connection check valve that is provided in the connection passage, wherein:
the connection check valve opens to allow working fluid to flow from the second output port toward the first output port when the spool is positioned at the first position; and
the connection check valve closes to limit working fluid from flowing from the first output port toward the second output port when the spool is positioned at the first position.
2. The valve timing adjuster according to claim 1 , wherein:
the second position is a full retard phase position;
the phase of the camshaft is held fully retarded when the spool is positioned at the full retard phase position; and
when the spool is positioned at the full retard phase position, the first output port acts as a retard output port, through which working fluid is output to the retard chamber, and the second output port acts as an advance output port, through which working fluid is output to the advance chamber.
3. The valve timing adjuster according to claim 1 , wherein:
the second position is a full advance phase position;
the phase of the camshaft is held fully advanced when the spool is positioned at the full advance phase position; and
when the spool is positioned at the full advance phase position, the first output port acts as an advance output port, through which working fluid is output to the advance chamber, and the second output port acts as a retard output port, through which working fluid is output to the retard chamber.
4. The valve timing adjuster according to claim 1 , wherein:
the drain port opens to atmosphere;
the first position and the second position are arranged adjacent to each other in a direction, in which the spool is displaceable;
the connection passage connects the first output port with the second output port also when the spool is positioned at the second position;
the connection check valve opens in a case, where pressure on one side of the connection passage toward the second output port is higher than pressure on the other side of the connection passage toward the first output port when the spool is positioned at the one of the first position and the second position; and
the connection check valve closes in another case, where pressure on the one side of the connection passage is lower than pressure on the other side of the connection passage when the spool is positioned at the one of the first position and the second position.
5. The valve timing adjuster according to claim 1 , further comprising:
an input line that is communicated with the fluid supply source and the input port; and
an input check valve that is provided to the input line, wherein:
the input check valve is adapted to open to allow working fluid to flow from the fluid supply source toward the input port; and
the input check valve is adapted to close to limit working fluid from flowing from the input port toward the fluid supply source.
6. The valve timing adjuster according to claim 1 , further comprising:
a controlling unit that controls displacement of the spool based on a reference phase of the camshaft relative to the crankshaft, wherein the controlling unit is adapted to learn an actual phase of the camshaft relative to the crankshaft as the reference phase under a condition, where the controlling unit controls the spool to be positioned at the second position.
7. The valve timing adjuster according to claim 6 , wherein the controlling unit learns the actual phase as the reference phase by controlling the spool to be positioned at the second position after the engine has started.
8. The valve timing adjuster according to claim 6 , wherein the controlling unit learns the actual phase as the reference phase by controlling the spool to be positioned at the second position in a case, where a condition for adjusting the phase of the camshaft to the full phase is satisfied while the engine rotates at a speed not higher than a set value.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2008003604A JP4518149B2 (en) | 2008-01-10 | 2008-01-10 | Valve timing adjustment device |
JP2008-003604 | 2008-01-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20090178635A1 true US20090178635A1 (en) | 2009-07-16 |
Family
ID=40758610
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US12/349,637 Abandoned US20090178635A1 (en) | 2008-01-10 | 2009-01-07 | Valve timing adjuster |
Country Status (3)
Country | Link |
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US (1) | US20090178635A1 (en) |
JP (1) | JP4518149B2 (en) |
DE (1) | DE102008055175A1 (en) |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
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CN102213120A (en) * | 2010-04-10 | 2011-10-12 | 海德里克林有限公司 | Oscillating-motor camshaft adjuster having a hydraulic valve |
US20140311594A1 (en) * | 2013-04-22 | 2014-10-23 | Hilite Germany Gmbh | Central valve for pivot motor actuator |
US20150059671A1 (en) * | 2013-08-27 | 2015-03-05 | Aisin Seiki Kabushiki Kaisha | Control valve |
US20150192042A1 (en) * | 2012-07-13 | 2015-07-09 | Borgwarmer Inc. | Five-way oil control valve with integrated venting spool |
CN104832239A (en) * | 2014-02-06 | 2015-08-12 | 德国海利特有限公司 | Oscillating-motor camshaft adjuster having a hydraulic valve |
US20160230612A1 (en) * | 2013-05-03 | 2016-08-11 | Hilite Germany Gmbh | Hydraulic valve and cam phaser |
CN107191236A (en) * | 2016-03-14 | 2017-09-22 | 伊希欧1控股有限公司 | The hydraulic valve of piston for the hydraulic valve of camshaft phase adjuster and the camshaft phase adjuster for camshaft |
US20190257223A1 (en) * | 2018-02-21 | 2019-08-22 | ECO Holding 1 GmbH | Hydraulic valve for a cam phaser |
CN110173315A (en) * | 2018-02-21 | 2019-08-27 | 伊希欧1控股有限公司 | The hydraulic valve of rotary motor adjuster for camshaft |
US10619524B2 (en) | 2016-06-08 | 2020-04-14 | Scania Cv Ab | Variable cam timing phaser utilizing hydraulic logic element |
US10731520B2 (en) | 2016-06-08 | 2020-08-04 | Scania Cv Ab | Variable cam timing phaser utilizing series-coupled check valves |
US10844755B2 (en) | 2016-06-08 | 2020-11-24 | Scania Cv Ab | Rotational hydraulic logic device and variable cam timing phaser utilizing such a device |
US10927719B2 (en) | 2016-05-24 | 2021-02-23 | Scania Cv Ab | Variable cam timing phaser having two central control valves |
WO2021253337A1 (en) * | 2020-06-18 | 2021-12-23 | 舍弗勒技术股份两合公司 | Camshaft phaser |
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KR101738372B1 (en) | 2010-10-04 | 2017-05-22 | 보르그워너 인코퍼레이티드 | Variable camshaft timing mechanism with a default mode |
WO2012061234A2 (en) | 2010-11-02 | 2012-05-10 | Borgwarner Inc. | Cam torque actuated - torsional assist phaser |
US9115610B2 (en) * | 2013-03-11 | 2015-08-25 | Husco Automotive Holdings Llc | System for varying cylinder valve timing in an internal combustion engine |
US10041385B2 (en) | 2016-03-14 | 2018-08-07 | ECO Holding 1 GmbH | Piston for a hydraulic valve for a cam phaser and hydraulic valve for the cam phaser |
DE102016118962A1 (en) * | 2016-10-06 | 2018-04-12 | Denso Corporation | Camshaft adjuster and associated switch body |
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Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6047674A (en) * | 1997-09-12 | 2000-04-11 | Denso Corporation | Valve timing control apparatus for internal combustion engine |
US7000580B1 (en) * | 2004-09-28 | 2006-02-21 | Borgwarner Inc. | Control valves with integrated check valves |
US7124722B2 (en) * | 2004-12-20 | 2006-10-24 | Borgwarner Inc. | Remote variable camshaft timing control valve with lock pin control |
US7444968B2 (en) * | 2005-11-28 | 2008-11-04 | Mechadyne Plc | Variable phase drive coupling |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6250265B1 (en) * | 1999-06-30 | 2001-06-26 | Borgwarner Inc. | Variable valve timing with actuator locking for internal combustion engine |
DE102005037480A1 (en) * | 2005-08-09 | 2007-02-15 | Schaeffler Kg | Control valve and method of making the same |
JP4463186B2 (en) * | 2005-11-15 | 2010-05-12 | 株式会社デンソー | Valve timing adjustment device |
-
2008
- 2008-01-10 JP JP2008003604A patent/JP4518149B2/en not_active Expired - Fee Related
- 2008-12-29 DE DE102008055175A patent/DE102008055175A1/en not_active Withdrawn
-
2009
- 2009-01-07 US US12/349,637 patent/US20090178635A1/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6047674A (en) * | 1997-09-12 | 2000-04-11 | Denso Corporation | Valve timing control apparatus for internal combustion engine |
US7000580B1 (en) * | 2004-09-28 | 2006-02-21 | Borgwarner Inc. | Control valves with integrated check valves |
US7124722B2 (en) * | 2004-12-20 | 2006-10-24 | Borgwarner Inc. | Remote variable camshaft timing control valve with lock pin control |
US7444968B2 (en) * | 2005-11-28 | 2008-11-04 | Mechadyne Plc | Variable phase drive coupling |
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CN102213120A (en) * | 2010-04-10 | 2011-10-12 | 海德里克林有限公司 | Oscillating-motor camshaft adjuster having a hydraulic valve |
US20150192042A1 (en) * | 2012-07-13 | 2015-07-09 | Borgwarmer Inc. | Five-way oil control valve with integrated venting spool |
US9598986B2 (en) * | 2012-07-13 | 2017-03-21 | Borgwarner Inc. | Five-way oil control valve with integrated venting spool |
US9194506B2 (en) * | 2013-04-22 | 2015-11-24 | Hilite Germany Gmbh | Central valve for pivot motor actuator |
US20140311594A1 (en) * | 2013-04-22 | 2014-10-23 | Hilite Germany Gmbh | Central valve for pivot motor actuator |
US9909463B2 (en) * | 2013-05-03 | 2018-03-06 | Hilite Germany Gmbh | Hydraulic valve and cam phaser |
US20160230612A1 (en) * | 2013-05-03 | 2016-08-11 | Hilite Germany Gmbh | Hydraulic valve and cam phaser |
US9556758B2 (en) * | 2013-08-27 | 2017-01-31 | Aisin Seiki Kabushiki Kaisha | Control valve |
US20150059671A1 (en) * | 2013-08-27 | 2015-03-05 | Aisin Seiki Kabushiki Kaisha | Control valve |
CN104832239A (en) * | 2014-02-06 | 2015-08-12 | 德国海利特有限公司 | Oscillating-motor camshaft adjuster having a hydraulic valve |
CN107191236A (en) * | 2016-03-14 | 2017-09-22 | 伊希欧1控股有限公司 | The hydraulic valve of piston for the hydraulic valve of camshaft phase adjuster and the camshaft phase adjuster for camshaft |
US10927719B2 (en) | 2016-05-24 | 2021-02-23 | Scania Cv Ab | Variable cam timing phaser having two central control valves |
US10731520B2 (en) | 2016-06-08 | 2020-08-04 | Scania Cv Ab | Variable cam timing phaser utilizing series-coupled check valves |
US10619524B2 (en) | 2016-06-08 | 2020-04-14 | Scania Cv Ab | Variable cam timing phaser utilizing hydraulic logic element |
US10844755B2 (en) | 2016-06-08 | 2020-11-24 | Scania Cv Ab | Rotational hydraulic logic device and variable cam timing phaser utilizing such a device |
CN110173317A (en) * | 2018-02-21 | 2019-08-27 | 伊希欧1控股有限公司 | The hydraulic valve of rotary motor adjuster for camshaft |
CN110173315A (en) * | 2018-02-21 | 2019-08-27 | 伊希欧1控股有限公司 | The hydraulic valve of rotary motor adjuster for camshaft |
US20190257223A1 (en) * | 2018-02-21 | 2019-08-22 | ECO Holding 1 GmbH | Hydraulic valve for a cam phaser |
US11111826B2 (en) * | 2018-02-21 | 2021-09-07 | ECO Holding 1 GmbH | Hydraulic valve for a cam phaser |
US11300017B2 (en) * | 2018-02-21 | 2022-04-12 | ECO Holding 1 GmbH | Hydraulic valve for a cam phaser |
WO2021253337A1 (en) * | 2020-06-18 | 2021-12-23 | 舍弗勒技术股份两合公司 | Camshaft phaser |
Also Published As
Publication number | Publication date |
---|---|
JP2009167811A (en) | 2009-07-30 |
DE102008055175A1 (en) | 2009-07-16 |
JP4518149B2 (en) | 2010-08-04 |
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Owner name: DENSO CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TAKENAKA, AKIHIKO;REEL/FRAME:022093/0948 Effective date: 20081218 |
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