JP4518149B2 - Valve timing adjustment device - Google Patents

Valve timing adjustment device Download PDF

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JP4518149B2
JP4518149B2 JP2008003604A JP2008003604A JP4518149B2 JP 4518149 B2 JP4518149 B2 JP 4518149B2 JP 2008003604 A JP2008003604 A JP 2008003604A JP 2008003604 A JP2008003604 A JP 2008003604A JP 4518149 B2 JP4518149 B2 JP 4518149B2
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phase
output port
advance
spool
retard
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JP2009167811A (en
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昭彦 竹中
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株式会社デンソー
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34426Oil control valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34426Oil control valves
    • F01L2001/3443Solenoid driven oil control valves

Description

  The present invention relates to a valve timing adjusting device that adjusts the valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine.

  2. Description of the Related Art Conventionally, a fluid-driven valve timing adjusting device including a housing as a driving rotating body that rotates in conjunction with a crankshaft and a vane rotor as a driven rotating body that rotates in conjunction with a camshaft has been widely used. As a kind of such valve timing adjusting device, Patent Document 1 discloses that a camshaft is cranked by supplying a working fluid to an advance chamber or a retard chamber partitioned in a rotational direction between a shoe of a housing and a vane of a vane rotor. An apparatus that adjusts the valve timing by driving to an advance side or a retard side with respect to an axis is disclosed.

Specifically, the device of Patent Document 1 moves the spool of the spool valve to a phase change position for changing the phase of the camshaft relative to the crankshaft (hereinafter referred to as “engine phase”). The input working fluid is supplied to the advance chamber or the retard chamber. In this apparatus, when the working fluid is supplied to one of the advance chamber and the retard chamber, the working fluid discharged from the other of the advance chamber and the retard chamber is reused for supply to the one fluid chamber. I have to. According to this, even if the fluid supply side of the advance chamber and the retard chamber is expanded in volume by the fluctuating torque transmitted from the camshaft, the volume expansion is supplemented by the reused working fluid, and the response is made. It becomes possible to improve the nature. Here, the fluctuation torque is torque that acts so as to alternately urge the camshaft toward the advance side and the retard side with respect to the crankshaft.
JP 2006-177344 A

  In the device of Patent Document 1, check valves are individually arranged in the advance angle output passage and the retard angle output passage for communicating the advance angle output port and the retard angle output port of the spool valve with the advance angle chamber and the retard angle chamber, respectively. Further, midway portions of these output passages are respectively connected to the advance return port and the retard return port of the spool valve.

  In such a configuration, for example, when the engine phase is changed to the retard side, the spool moves to the phase change position on the retard side, so that the space between the advance return port and the retard output port is within the spool valve. Connected at. As a result, together with the working fluid input from the fluid input source to the spool valve input port, the working fluid discharged from the advance chamber to the advance return port is output from the retard output port to the retard output passage. . At this time, the check valve in the retard output passage is opened by the pressure of the output fluid, so that the working fluid from the fluid input source and the advance chamber is supplied to the retard chamber. However, such working fluid supply can be realized when a positive torque that biases the camshaft toward the retarded angle with respect to the crankshaft of the variable torque is applied, but the camshaft is applied to the advanced angle with respect to the crankshaft among the variable torque. It becomes difficult to realize at the time of acting negative torque. This is because the volume of the advance chamber is expanded by the action of the latter fluctuation torque, and the input fluid to the input port flows backward from the advance output port to the advance chamber.

  As described above, the fluid backflow to the advance chamber in the retarded angle drive is the response when changing the phase and the phase stability when the engine phase is held at the most retarded phase by pressing the vane against the shoe. It becomes a factor to reduce the sex. Further, such a decrease in responsiveness and phase stability at the time of phase change also occurs when the camshaft is driven to the advance side with respect to the crankshaft, and therefore an improvement is desired.

  Accordingly, an object of the present invention is to provide a valve timing adjusting device that enhances responsiveness and phase stability at the time of phase change.

The invention according to claim 1 is a valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine, and has a shoe protruding radially inward. And a drive rotator that rotates in conjunction with the crankshaft and a vane that protrudes radially outward, rotates in conjunction with the camshaft, and advances between the vane and the shoe of the drive rotator, A driven rotating body that divides the retard chamber in the rotation direction and drives the cam shaft to the advance side or the retard side with respect to the crankshaft by supplying the working fluid to the advance chamber or the retard chamber; and a fluid input source An input port through which the working fluid is input, a drain port for discharging the working fluid, a first output port for outputting the working fluid to one of the advance chamber and the retard chamber, and the other of the advance chamber and the retard chamber Output working fluid Second output port, and having a spool, with the movement position of the spool for the driven rotor to change the relative rotation is allowed by the engine phase is set as the phase change position relative to the drive rotor, shoe drive rotor input movement position of the spool for retaining the vanes of the driven rotating body pressed against with engine phase in the endmost phase is set as an endmost phase position, the phase change position of the spool, a first output port for The second output port is closed to the drain port, and the first output port is connected to the input port and the second output port is connected to the drain port at the endmost phase position of the spool. A spool valve that communicates with the first output port, and is connected to the first output port and the second output port at the phase change position of the spool. A connecting passage and a valve that is disposed in the connecting passage and opens at the phase change position of the spool, thereby allowing a working fluid flow from the second output port side to the first output port side, while at the spool phase change position. And a connection check valve for restricting a working fluid flow from the first output port side to the second output port side by closing the valve.

According to such an invention, when the engine rotor phase is changed by rotating the driven rotor relative to the drive rotor, the spool is moved to the phase change position as the movement position, so that the advance chamber and the delay chamber are moved. The first output port and the second output port communicating with one and the other of the corner chambers are connected by a connection passage. At the same time, in the phase change position, the first output port communicates with the input port, while the second output port is closed with respect to the drain port for discharging the working fluid. Therefore, in the phase change position, when the working fluid is discharged from the advance chamber or retard chamber compressed by the action of the variable torque to the second output port, the connection check valve disposed in the connection passage By opening the valve, a working fluid flow from the second output port side toward the first output port side is allowed. Thus, the position phase change position, even as a working fluid amount supplied to the retarded angle chamber or the advanced angle chamber from the fluid input source is low through the first output port which communicates with the input port, a correspondingly second output Can be replenished from the port side. Therefore, even if the retarded angle chamber or the advanced angle chamber from which the working fluid is output from the first output port is expanded in volume by the action of the varying torque, the shortage of working fluid can be suppressed.

  In addition, in the phase change position, even if the retarding chamber or the advance chamber from which the working fluid is output from the first output port is compressed by the action of the variable torque, the working fluid flows back to the first output port. By closing the connection check valve disposed in the passage, the working fluid flow from the first output port side to the second output port side is restricted. Thereby, it is possible to avoid a situation in which the working fluid is erroneously supplied to the advance chamber or the retard chamber on the fluid discharge side to the second output port.

  According to the above, while supplying a sufficient amount of working fluid to one of the advance chamber and the retard chamber, the working fluid is quickly discharged from the other of the advance chamber and the retard chamber, and at the time of phase change Responsiveness can be improved.

In addition, according to the first aspect of the invention, when the vane of the driven rotating body is pressed against the shoe of the driving rotating body to keep the engine phase at the extreme end phase, the spool is at the end as the moving position. By moving to the end phase position, the first output port and the second output port communicate with the input port and the drain port, respectively. Therefore, at the extreme end phase position, the working fluid is discharged from the advance chamber or retard chamber compressed by the action of the varying torque to the second output port, and the retard chamber or advance angle whose volume is enlarged by the action of the varying torque. The input fluid from the fluid input source is supplied to the chamber through the input port and the first output port. At this time, since the working fluid is discharged from the second output port to the drain port communicating therewith, the advance chamber or retard chamber on the fluid discharge side is emptied and the driven rotor is pushed against the drive rotor. Reliance can be ensured. According to this, the phase stability at the extreme end phase is improved.

In the invention according to claim 2, the spool valve has a spool in which the most retarded angle phase position, which is a moving position for maintaining the engine phase at the most retarded phase on the retarded angle side , is set as the most end phase position. At the most retarded phase position of the spool, the retard output port that outputs the working fluid to the retard chamber functions as the first output port and the advance output port that outputs the working fluid to the advance chamber is the second. Functions as an output port.

According to such an invention, when the engine phase is held at the most retarded phase on the retard side, the spool moves to the most retarded phase position as the most end phase position among the moved positions, so that the input port and A retard angle output port as a first output port and an advance angle output port as a second output port communicate with the drain port, respectively. Therefore, at the most retarded phase position, the fluid input source is supplied to the retarded chamber whose volume is expanded by the action of the varying torque while the working fluid is discharged from the advanced chamber compressed by the action of the varying torque to the advance output port. From the input port and the retarded angle output port. At this time, since the working fluid is discharged from the advance output port to the drain port communicating therewith, the advance chamber on the fluid discharge side is emptied and the vane of the driven rotor is pushed against the shoe of the drive rotor. Reliance can be ensured. According to this, the phase stability at the extreme end phase on the retard side is improved.

According to a third aspect of the present invention, the spool valve has a spool in which the most advanced angle phase position, which is a movement position for maintaining the engine phase at the most advanced phase on the advance angle side , is set as the most extreme phase position. At the most advanced angle phase position of the spool, the advance output port that outputs the working fluid to the advance chamber functions as the first output port, and the retard output port that outputs the working fluid to the retard chamber serves as the second output port. Functions as an output port.

According to such an invention, when the engine phase is held at the most advanced phase on the advance angle side, the spool moves to the most advanced angle phase position as the most end phase position among the movement positions, so that the input port and An advance angle output port as a first output port and a retard angle output port as a second output port communicate with the drain port, respectively. Therefore, at the most advanced angle phase position, the fluid input source is supplied to the advance chamber whose volume is expanded by the action of the varying torque while the working fluid is discharged from the retard chamber compressed by the action of the varying torque to the retardation output port. Is supplied through the input port and the advance output port. At this time, since the working fluid is discharged from the retard output port to the drain port communicating therewith, the retard chamber on the fluid discharge side is emptied and the vane of the driven rotor is pushed against the shoe of the drive rotor. Reliance can be ensured. According to this, the phase stability at the most advanced phase on the advance side is improved.

  In the invention according to claim 4, the spool valve has a drain port opened to the atmosphere, and a spool in which the phase change position and the extreme end phase position are set adjacent to each other in the moving direction, and the phase change position of the spool And the connection passage connects between the first output port and the second output port at the endmost phase position, and the connection check valve at the phase change position and the endmost phase position of the spool is connected to the first output port at the connection passage. The valve is opened when the second output port side is at a higher pressure than the first output port, while the valve is closed when the second output port side is at a lower pressure than the first output port side in the connection passage.

  According to such an invention, in the connection passage where the working fluid is discharged from the advance chamber or the retard chamber through the second output port at the phase change position, the second output is more than the first output port side communicating with the input port. When the port side is at a high pressure, the connection check valve is opened and the effect of supplying the working fluid can be exhibited.

  Similarly to the phase change position, the working fluid is discharged from the advance chamber or the retard chamber through the second output port at the extreme phase position where the connection between the first output port and the second output port is established. In the connection path, the second output port side is at a lower pressure than the first output port side communicating with the input port due to the communication between the drain port opened to the atmosphere and the second output port. Thereby, since the connection check valve is closed, the working fluid flow is restricted between the second output port and the first output port in the connection passage. Therefore, the phase change position and the endmost phase position are set next to each other, and the connection state between the output ports by the connection passage is made common at the movement position, thereby simplifying the configuration, while the advance angle chamber or the delay position is set. The fluid can be quickly discharged from the corner chamber to the drain port through the second output port to ensure phase stability.

  Further, in the connection passage when the working fluid flows backward from the retard chamber or the advance chamber through the first output port at the phase change position and the extreme phase position, the first output port side has a higher pressure than the second output port side. As a result, the connection check valve is closed, and the effect of suppressing the shortage of the working fluid is exhibited.

  In the invention according to claim 5, while the input passage communicating with the fluid input source and the input port, and the working fluid flow from the fluid input source side toward the input port side is permitted by opening the valve, An input check valve that restricts the flow of the working fluid from the input port side toward the fluid input source side by closing the valve is provided.

  According to such an invention, even if the working fluid flows backward from the retard chamber or the advance chamber on the fluid supply side to the input port through the first output port, it is disposed in the input passage communicating with the input port. The input check valve can regulate the working fluid flow from the input port side to the fluid input source side, that is, the backflow by closing the valve. Therefore, it is possible to reliably suppress a situation where the working fluid is insufficient in the retard chamber or the advance chamber on the fluid supply side.

  7. The control unit according to claim 6, wherein the control unit controls the moving position of the spool based on a reference phase among the engine phases, and the actual engine phase is controlled while the moving position of the spool is controlled to the extreme end phase position. Is provided as a reference phase.

  According to such an invention, the actual engine phase, that is, the extreme end phase is learned as the reference phase under the state where the spool has moved to the extreme end phase position that realizes the extreme end phase with improved stability as described above. Therefore, the learning accuracy can be increased. Therefore, by controlling the moving position of the spool based on the learned reference phase, it is possible to accurately adjust the engine phase according to the moving position, and hence the valve timing.

  In the seventh aspect of the present invention, the control means learns the reference phase by controlling the moving position of the spool to the extreme end phase position when the start of the internal combustion engine is completed.

  In such an invention, when the start of the internal combustion engine is completed, the latest reference phase is learned, which can contribute to an improvement in valve timing adjustment accuracy. Also, since the internal combustion engine speed is relatively low when the start of the internal combustion engine is completed, the reference phase is learned in a state where there is little rotational vibration of the drive rotor and the driven rotor that rotate in conjunction with the crankshaft and camshaft. Therefore, it can contribute to the improvement of the adjustment accuracy.

  In the invention according to claim 8, the control means sets the moving position of the spool to the most extreme phase position when a condition for adjusting the engine phase to the most extreme phase is established at a rotational speed equal to or lower than the set value of the internal combustion engine. To learn the reference phase.

  According to such an invention, the latest reference phase can be learned each time the condition for adjusting the engine phase to the extreme end phase is satisfied, which can contribute to the improvement of the valve timing adjustment accuracy. In addition, since the reference phase is learned in a state where the rotational vibration of the drive rotating body and the driven rotating body that rotate in conjunction with the crankshaft and the camshaft is low under the low rotation speed of the internal combustion engine that the rotation speed is equal to or less than the set value, This can also contribute to improvement in adjustment accuracy.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description is abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment.

(First embodiment)
FIG. 1 shows an example in which a valve timing adjusting device 1 according to a first embodiment of the present invention is applied to an internal combustion engine of a vehicle. The valve timing adjusting device 1 is a fluid drive type that uses hydraulic oil as the “working fluid”, and adjusts the valve timing of the intake valve as the “valve”.

(Basic configuration)
Hereinafter, a basic configuration of the valve timing adjusting device 1 will be described. The valve timing adjusting device 1 is installed in a driving force transmission system that transmits a driving force of a crankshaft (not shown) of an internal combustion engine to a camshaft 2 of the internal combustion engine, and is driven by hydraulic oil. And a control unit 30 that controls the supply of hydraulic oil to 10.

(Drive part)
In the drive unit 10, the housing 12 as a “drive rotator” includes a cylindrical sprocket portion 12 a and a plurality of shoes 12 b, 12 c, 12 d, and 12 e as partition portions.

  The sprocket portion 12a is connected to the crankshaft via a timing chain (not shown). As a result, during operation of the internal combustion engine, driving force is transmitted from the crankshaft to the sprocket portion 12a, so that the housing 12 rotates in the clockwise direction in FIG. 1 in conjunction with the crankshaft.

  Each of the shoes 12b to 12e protrudes radially inward from a portion that is substantially equidistant in the rotational direction in the sprocket portion 12a. The protruding side end surfaces of the shoes 12b to 12e have an arcuate concave shape when viewed from the direction perpendicular to the plane of FIG. 1 and are in sliding contact with the outer peripheral wall surface of the boss portion 14a of the vane rotor 14. A storage chamber 50 is formed between the shoes 12b to 12e adjacent to each other in the rotation direction.

  The vane rotor 14 as a “driven rotor” is accommodated in the housing 12 and is in sliding contact with the housing 12 in the axial direction. The vane rotor 14 includes a cylindrical boss portion 14a and vanes 14b, 14c, 14d, and 14e.

  The boss portion 14 a is bolted coaxially with the cam shaft 2. As a result, the vane rotor 14 rotates in the clockwise direction of FIG. 1 in conjunction with the camshaft 2 and can rotate relative to the housing 12.

  Each of the vanes 14b to 14e protrudes radially outward from a portion that is substantially equidistant in the rotational direction in the boss portion 14a, and is accommodated in the corresponding accommodating chamber 50. The protruding side end surfaces of the vanes 14b to 14d are formed in an arcuate convex shape when viewed from the direction perpendicular to the plane of FIG. 1, and are in sliding contact with the inner peripheral wall surface of the sprocket portion 12a.

  Each of the vanes 14 b to 14 e divides the advance chamber and the retard chamber from the housing 12 by dividing the corresponding storage chamber 50 in the rotational direction. Specifically, the advance chamber 52 is between the shoe 12b and the vane 14b, the advance chamber 53 is between the shoe 12c and the vane 14c, and the advance chamber 54 is between the shoe 12d and the vane 14d. An advance chamber 55 is formed between each of them. Also, the retard chamber 56 is between the shoe 12c and the vane 14b, the retard chamber 57 is between the shoe 12d and the vane 14c, the retard chamber 58 is between the shoe 12e and the vane 14d, and the retard chamber 58 is between the shoe 12b and the vane 14e. Each corner chamber 59 is formed.

  In the drive unit 10 having such a configuration, the vane rotor 14 is rotated relative to the housing 12 with respect to the housing 12 by supplying hydraulic oil to the advance chambers 52 to 55, whereby the camshaft 2 is advanced relative to the crankshaft. Driven by. Therefore, at this time, the engine phase that determines the valve timing changes to the advance side. Further, by continuing the supply of hydraulic oil to the advance chambers 52 to 55, when the vanes 14b, 14c, 14d, and 14e are pressed against the advance shoes 12c, 12d, 12e, and 12b, the engine phase is changed. It is held at the most advanced phase on the advance angle side (most advanced angle hold).

  In the drive unit 10, the vane rotor 14 rotates relative to the housing 12 toward the retard side by supplying hydraulic oil to the retard chambers 56 to 59, thereby driving the cam shaft 2 toward the retard side with respect to the crankshaft. The Therefore, at this time, the engine phase changes to the retard side. Furthermore, when the hydraulic oil supply to the retard chambers 56 to 59 is continued, when the vanes 14b, 14c, 14d, and 14e are pressed against the retard-side shoes 12b, 12c, 12d, and 12e, the engine phase is changed. It is held at the endmost phase on the retard side (most retarded angle hold).

(Control part)
In the control unit 30, the advance angle output passage 72 provided through the cam shaft 2 and its bearing (not shown) communicates with the advance angle chambers 52 to 55 regardless of the operating state of the drive unit 10. The retard output passage 76 provided through the camshaft 2 and its bearing communicates with the retard chambers 56 to 59 regardless of the operating state of the drive unit 10.

  The input passage 80 communicates with a discharge port of the pump 4 that is a “fluid input source” so that hydraulic oil pumped up from the oil pan 5 by the pump 4 is discharged and supplied at a pressure higher than atmospheric pressure. It has become. Here, the pump 4 of the present embodiment is a mechanical pump that is driven by a crankshaft. Therefore, hydraulic oil is continuously input to the input passage 80 during the operation of the internal combustion engine. The drain passage 82 is open to the atmosphere, and is provided in the oil pan 5 so that the hydraulic oil can be discharged.

  The spool valve 100 is an electromagnetic control valve that drives the spool 130 in a reciprocating linear manner using the electromagnetic driving force generated by the solenoid 120. The spool valve 100 has an advance output port 112 that outputs hydraulic oil to the advance chambers 52 to 55 through the advance output passage 72, and a retard output that outputs the hydraulic oil to the retard chambers 56 to 59 through the retard output passage 76. A port 114, an input port 116 through which hydraulic oil from the pump 4 is input through the input passage 80, and a drain port 118 that is opened to the atmosphere through the drain passage 82 and discharges the hydraulic oil to the passage 82. The spool valve 100 reciprocates the spool 130 in response to the energization of the solenoid 120, so that the port communicating with the input port 116 and the drain port 118 is connected between the advance output port 112 and the retard output port 114. Set.

  The control circuit 200 is mainly composed of a microcomputer having a memory 200 a and is electrically connected to the solenoid 120 of the spool valve 100. The control circuit 200 has a function of controlling the operation of the internal combustion engine as well as a function of controlling energization to the solenoid 120. Here, in particular, the control circuit 200 of the present embodiment is electrically connected to a crank sensor 202 that detects the rotation of the crankshaft and a cam sensor 204 that detects the rotation of the camshaft 2. This detection result is used for energization control to the solenoid 120 and operation control of the internal combustion engine.

  In the control unit 30 having such a configuration, the spool valve 100 controls the movement position of the spool 130 (hereinafter simply referred to as “spool position”) in accordance with the energization from the control circuit 200 to the solenoid 120. As a result, at the spool position where the advance output port 112 communicates with the input port 116, the hydraulic fluid supplied from the pump 4 to the input passage 80 is output to the advance output passage 72 and supplied to the advance chambers 52 to 55. It becomes possible. Further, at the spool position where the retard output port 114 communicates with the input port 116, the supply hydraulic oil from the pump 4 to the input passage 80 can be output to the retard output passage 76 and supplied to the retard chambers 56 to 59. It becomes. Further, at the spool position where the advance angle output port 112 communicates with the drain port 118, the hydraulic oil in the advance angle chambers 52 to 54 can be discharged to the oil pan 5 through the advance angle output passage 72 and the drain passage 82.

(Characteristic)
Hereinafter, features of the valve timing adjusting device 1 will be described in detail.

(Variable torque)
During the operation of the internal combustion engine, fluctuating torque caused by a spring reaction force or the like from an intake valve driven to open and close by the camshaft 2 acts on the vane rotor 14 of the drive unit 10 through the camshaft 2. Here, as shown in FIG. 2, the fluctuation torque includes a negative torque that urges the camshaft 2 toward the advance side with respect to the crankshaft, and a positive torque that urges the camshaft 2 toward the retard side with respect to the crankshaft. It fluctuates alternately with the torque periodically. The fluctuating torque may be, for example, that the average torque becomes substantially zero when the peak torque T + of the positive torque becomes substantially equal to the peak torque T− of the negative torque, The average torque may be biased toward the positive torque side when the peak torque T + becomes larger than the peak torque T− of the negative torque.

(Spool valve)
As shown in FIG. 3, the spool valve 100 of this embodiment includes a sleeve 110, a solenoid 120, a spool 130, a drive shaft 139, a return spring 140, and the like.

  The metal sleeve 110 has a cylindrical shape, and a solenoid 120 is fixed to one end 110a. The sleeve 110 is provided with a retard output port 114, an input port 116, an advance output port 112, and a drain port 118 in this order in the axial direction from the one end 110a side to the other end 110b side.

  The metal spool 130 has a substantially skewer shape and is accommodated coaxially in the sleeve 110. A drive shaft 139 that is electromagnetically driven by the solenoid 120 is coaxially connected to the one end portion 130 a of the spool 130, so that the spool 130 can move in the axial direction together with the drive shaft 139. The spool 130 is provided with an advance support land 132, an advance switch land 134, a retard switch land 136, and a retard support land 138 in the reverse order in the axial direction from the one end portion 130a to the other end portion 130b. ing.

  The advance angle support land 132 is always slidably supported by the sleeve 110 on the drain port 118 side of the advance angle output port 112. The advance angle switching land 134 is slidably supported by the sleeve 110 on at least one of the drain port 118 side and the input port 116 side across the advance angle output port 112. Here, in the spool position of FIG. 3 in which the advance angle switching land 134 is supported only on the drain port 118 side of the advance angle output port 112, the advance angle output port 112 is connected to the advance angle switching land 134 and the retard angle switching land 136. It communicates with the input port 116 through a gap therebetween. 4 and 5 in which the advance angle switching land 134 is supported only on the input port 116 side of the advance angle output port 112, the advance angle output port 112 has the advance angle support land 132 and the advance angle switching land 134. Communicate with the gap between. Further, in the spool position of FIG. 6 where the advance angle switching land 134 is supported on both the end portion 110b of the advance angle output port 112 and the input port 116 side, the advance angle output port 112 is blocked from the other ports. It is.

  As shown in FIG. 3, the retard support land 138 is always slidably supported by the sleeve 110 on the end 110 a side of the retard output port 114. The retard switching land 136 is slidably supported by the sleeve 110 on at least one of the input port 116 side and the end portion 110a side across the retard output port 114. Here, in the spool position of FIGS. 4 and 5 in which the retard switching land 136 is supported only on the end 110a side of the retard output port 114, the retard output port 114 is connected to the advance switching land 134 and the retard switching land. The input port 116 communicates through a gap between 136. 3 is supported only on the input port 116 side of the retard output port 114, the retard output port 114 is located between the retard switch land 136 and the retard support land 138. Communicate with the gap. Further, in the spool position of FIG. 6 where the retard switching land 136 is supported on both the end 110a side and the input port 116 side of the retard output port 114, the retard output port 114 is blocked from the other ports. It is done.

  In this embodiment, as shown in FIGS. 3 to 6, the input port 116 communicates with the gap between the advance angle switching land 134 and the retard angle switching land 136 regardless of the spool position.

  The return spring 140 is made of a metal compression coil spring and is accommodated coaxially in the sleeve 110. The return spring 140 is interposed between the end 110 b of the sleeve 110 opposite to the solenoid 120 and the advance support land 132 of the spool 130. The return spring 140 urges the spool 130 toward the solenoid 120 in the axial direction by generating a restoring force by compressive deformation. On the other hand, the solenoid 120 urges the spool 130 together with the drive shaft 139 toward the return spring 140 in the axial direction by generating an electromagnetic driving force by energization. Therefore, in the spool valve 100, the spool 130 is driven in accordance with the balance between the restoring force generated by the return spring 140 and the electromagnetic driving force generated by the solenoid 120.

  1 and 3, the present embodiment is characterized in that the connection check valves 210 and 230 are provided in the connection passages 220 and 240 formed in the spool 130, respectively, as shown in FIGS.

  Specifically, as shown in FIG. 3, one end portion 221 of the advance angle connection passage 220 opens at a plurality of locations on the outer peripheral surface of the spool 130 between the advance angle switching land 134 and the retard angle switching land 136. . As a result, the end portion 221 of the advance angle connecting passage 220 communicates with the gap between the advance angle switching land 134 and the retard angle switching land 136 regardless of the spool position, as shown in FIGS. Therefore, particularly in the spool position of FIG. 3, the end 221 of the advance connection passage 220 communicates with the advance output port 112 and the input port 116 through the gap between the lands 134 and 136.

  The other end 222 of the advance connection passage 220 opens at a plurality of locations on the outer peripheral surface of the spool 130 between the retard switching land 136 and the retard support land 138. As a result, the end portion 222 of the advance connection passage 220 communicates with the gap between the retard switch land 136 and the retard support land 138 regardless of the spool position, as shown in FIGS. Therefore, particularly at the spool position of FIG. 3, the end portion 222 of the advance connection passage 220 that communicates with the advance output port 112 communicates with the retard output port 114 through the gap between the lands 136 and 138 as described above. That is, at the spool position in FIG. 3, the output ports 112 and 114 are connected via the advance connection passage 220.

  The advanced angle connection check valve 210 is disposed in the advanced angle connection passage 220 such that the direction from the one end 221 to the other end 222 is the valve closing direction and the reverse direction is the valve opening direction. Here, the advance connection check valve 210 of this embodiment is configured by combining 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 formed by a conical surface whose diameter decreases toward the end 222 side of the inner peripheral wall surface of the advance connection passage 220. The advance valve member 214 made of metal has a ball shape, and is disposed closer to the end portion 221 than the advance valve seat 212 in the advance connection passage 220, and is separated from the advance valve seat 212 in the axial direction. It can be seated. The metal advance retainer 215 has a bottomed cylindrical shape, and is disposed on the opposite side of the advance valve seat 212 with the advance valve member 214 sandwiched in the advance connection passage 220. The peripheral wall portion 215a of the advance retainer 215 is supported by the inner peripheral wall surface of the advance connection passage 220 so as to be slidable in the axial direction, and holds the advance valve member 214 by the inner peripheral surface. ing. The elastic member 216 is made of a metal compression coil spring, and is disposed on the opposite side of the advance valve member 214 with the advance retainer 215 sandwiched in the advance connection passage 220. The elastic member 216 is interposed between the retarded connection check valve 230 that is disposed to face the advance valve seat 212 in the axial direction and the advance retainer 215. The elastic member 216 urges the advance valve member 214 toward the advance valve seat 212 via the advance retainer 215 by generating a restoring force by compressive deformation.

  In such an advance connection check valve 210, when the end portion 222 side is higher than the end portion 221 side in the advance connection passage 220, the advance valve member 214 is moved to the end portion 221 side as shown in FIG. Moving. As a result, the advance valve member 214 is opened from the advance valve seat 212 so that the hydraulic oil flow from the end 222 side toward the end 221 is allowed.

  Further, in the advance connection check valve 210, when the end 222 side is lower than the end 221 side in the advance connection passage 220, the advance valve member 214 is on the end 222 side as shown in FIGS. Move to. As a result, the advance valve member 214 sits on the advance valve seat 212 and closes, so that the hydraulic fluid flow from the end 221 side toward the end 222 side is restricted.

  Now, as shown in FIG. 3, the retard connection passage 240 shares an end portion 221 communicating with the gap between the advance switch land 134 and the retard switch land 136 with the advance connection passage 220. That is, the end portion 221 is a common end portion 221 common to the advance connection passage 220 and the retard connection passage 240. 4 and 5, the common end 221 communicates with the retard output port 114 and the input port 116 through the gap between the advance switch land 134 and the retard switch land 136.

  The other end portion 242 of the retard connection passage 240 opens at a plurality of locations on the outer peripheral surface of the spool 130 between the advance support land 132 and the advance switching land 134. As a result, the end portion 242 of the retard connection passage 240 communicates with the gap between the advance support land 132 and the advance switching land 134 regardless of the spool position, as shown in FIGS. 4 and 5, the end portion 242 of the retard connection passage 240 communicating with the retard output port 114 as described above communicates with the advance output port 112 through the gap between the lands 132 and 134. That is, at the spool position of FIGS. 4 and 5, the output ports 112 and 114 are connected via the retard connection passage 240.

  The retarded connection check valve 230 is disposed in the retarded connection passage 240 such that the direction from the common end 221 to the other end 242 is the valve closing direction and the reverse direction is the valve opening direction. Here, the retard connection check valve 230 of the present embodiment has a configuration according to the advance connection check valve 210, that is, a retard valve seat 232, a retard valve member 234, a retard retainer 235, and an elastic member 216. It is a combined configuration.

  However, in the retarded connection check valve 230, the retarded valve seat 232 is formed by a conical surface whose diameter decreases toward the end 242 side of the inner peripheral wall surface of the retarded connection passage 240. The retard valve member 234 is disposed on the common end 221 side of the retard valve seat 232 in the retard connection passage 240, and can be attached to and detached from the retard valve seat 232 in the axial direction. The retard retainer 235 is disposed on the opposite side to the retard valve seat 232 across the retard valve member 234 in the retard connection passage 240, and the outer peripheral surface is supported by the inner peripheral wall surface of the retard connection passage 240. The retard valve member 234 is held by the inner peripheral surface of the portion 235a. The elastic member 216 common to the advance connection check valve 210 is disposed on the opposite side of the retard valve member 234 across the retard retainer 235 in the retard connection passage 240. The elastic member 216 is interposed between the valve members 234 and 214 via retainers 235 and 215. The elastic member 216 urges the retard valve member 234 toward the retard valve seat 232 via the retard retainer 235 by generating a restoring force by compressive deformation.

  In such a retard connection check valve 230, when the end portion 242 side is higher than the end portion 221 side in the retard connection passage 240, the retard valve member 234 is moved to the end portion 221 side as shown in FIG. Moving. As a result, the retard valve member 234 opens from the retard valve seat 232 so that the hydraulic oil flow from the end 242 side toward the end 221 side is allowed.

  Further, in the retard connection check valve 230, when the end portion 242 side is lower than the end portion 221 side in the retard connection passage 240, the retard valve member 234 has an end portion as shown in FIGS. Move to the 242 side. As a result, the retard valve member 234 sits on the retard valve seat 232 and closes, so that the hydraulic oil flow from the end 221 side to the end 242 side is restricted.

  In addition to such a feature, the present embodiment is also characterized in that a relay passage 260 for allowing the advance output port 112 to communicate with the drain port 118 is formed in the spool 130 as shown in FIGS. There is.

  Specifically, as shown in FIG. 5, the one end portion 261 of the relay passage 260 opens at the end face of the end portion 130 b opposite to the drive shaft 139 in the advance support land 132 of the spool 130. Accordingly, at least at the spool position in FIG. 5, the end portion 261 of the relay passage 260 communicates with the drain port 118 through between the end portion 130 b of the spool 130 and the end portion 110 b of the sleeve 110 facing the spool 130. ing.

  The other end portion 262 of the relay passage 260 opens at a plurality of locations on the outer peripheral surface of the spool 130 in the advance support land 132. 5, the end portion 262 of the relay passage 260 communicates with the gap between the advance support land 132 and the advance switching land 134 through the outer peripheral space of the advance support land 132 in the sleeve 110. It is like that. Here, at the spool position in FIG. 5, the relay passage 260 is in communication with the drain port 118 as described above, and the gap between the lands 132 and 134 is in communication with the advance output port 112. 118 and 112 communicate with each other through the relay passage 260. On the other hand, in the spool position of FIGS. 3, 4, and 6, the end portion 262 of the relay passage 260 is blocked by the gap between the lands 132 and 134, so The port 112 is blocked.

(Input check valve)
As shown in FIGS. 1 and 3, an input check valve 280 is disposed in the input passage 80 communicating with the pump 4 and the input port 116. The input check valve 280 opens as shown in FIGS. 3 to 6 when the pump 4 side in the input passage 80 has a higher pressure than the spool valve 100 side, and operates from the pump 4 side toward the input port 116 side. Allow oil flow. On the other hand, the input check valve 280 closes as shown in FIGS. 7 to 9 when the spool valve 100 side is higher than the pump 4 side in the input passage 80, and moves from the input port 116 side to the pump 4 side. It regulates the hydraulic fluid flow.

(Valve timing adjustment operation)
During operation of the internal combustion engine in which the pump 4 is driven, the control circuit 200 calculates the actual phase Pr and the target phase Pt for the engine phase of the camshaft 2 with respect to the crankshaft, and spools based on the calculation results of the phases Pr and Pt. The energization current to the solenoid 120 of the valve 100 is controlled. As a result, the spool position of the spool valve 100 is controlled, and hydraulic oil supply and hydraulic oil discharge corresponding to the control position are realized for the advance chambers 52 to 55 and the retard chambers 56 to 59. As a result, the valve timing is adjusted. Hereinafter, the valve timing adjustment operation by the valve timing adjustment device 1 of the present embodiment will be described in detail.

(1) Advance angle operation Hereinafter, an operation in a case where the valve timing is advanced by changing the engine phase toward the advance side of the camshaft 2 with respect to the crankshaft will be described.

  When an operating condition indicating an accelerator off state or a low / medium speed / high load operating state is established in the internal combustion engine, the control circuit 200 controls the energization current to the solenoid 120 to a predetermined advance operation value Ia. As a result, the spool 130 is driven to the position shown in FIGS. 3 and 7 as the phase change position on the advance side. In such an advance angle side phase change position, an advance angle connection path is formed between the advance angle output port 112 communicating with the input port 116 and closed with respect to the drain port 118 and the retard angle output port 114. 220 is connected.

  Therefore, when negative torque is applied to the vane rotor 14, the hydraulic oil is input from the pump 4 to the input passage 80 and the input port 116 as shown in FIG. 3, and is passed through the advance output port 112 and the advance output passage 72. Supplied to advance chambers 52-55. In the advance connection passage 220, the input hydraulic oil to the input port 116 flows into the end portion 221, and the hydraulic oil in the retard chambers 56 to 59 compressed by the action of negative torque passes through the retard output port 114. It flows into the end 222. At this time, since the hydraulic fluid flowing into the end portion 222 on the retarded angle output port 114 side becomes higher than the hydraulic fluid flowing into the end portion 221 on the advanced angle output port 112 side, the advanced angle connection check valve 210. Is opened, so that the hydraulic oil flow from the retard output port 114 side to the advance output port 112 side is allowed. Therefore, when the input amount of the hydraulic oil from the pump 4 decreases, the hydraulic oil can be replenished from the retarded output port 114 side, so that it operates in the advance chambers 52 to 55 whose volume is expanded by the action of the negative torque. Oil shortage will be suppressed.

  When the negative torque is applied, the input hydraulic oil from the pump 4 flows into the retard connection passage 240 that communicates with the advance output port 112 at the common end 221, but the retard connection check valve 230 The hydraulic fluid flow toward the end 242 side is restricted by the valve closing. Further, since the advance angle output port 112 communicating with the advance angle connection passage 220 at the common end 221 is closed with respect to the drain port 118, the discharge of hydraulic oil from the drain port 118 is also restricted.

  On the other hand, when positive torque acts on the vane rotor 14 and the advance chambers 52 to 55 are compressed, the hydraulic oil flows from the advance output port 112 to the connection passages 220 and 240 and the input passage 80 as shown in FIG. Try to backflow. However, at this time, in the advance connection passage 220 and the retard connection passage 240, the hydraulic fluid flows toward the retard output port 114 side and the end portion 242 side respectively lead the advance connection check valve 210 and the retard connection check valve 230. And, at the same time, in the input passage 80, the hydraulic oil flow toward the pump 4 is restricted by closing the input check valve 280. That is, the backflow from the advance output port 112 to the connection passages 220 and 240 and the input passage 80 is restricted. Therefore, not only the hydraulic oil outflow from the advance chambers 52 to 55 is suppressed, but the situation where the hydraulic oil supply to the retard chambers 56 to 59 is erroneously realized is avoided.

  According to such an advance operation, the functions of the connection check valves 210 and 230 are properly performed in a timely manner, the hydraulic oil is discharged from the retard chambers 56 to 59, and sufficient for the advance chambers 52 to 55. Since a sufficient amount of hydraulic fluid can be supplied, it is possible to ensure a high advance angle response.

(2) Delay angle operation Hereinafter, the operation in the case where the valve timing is retarded by changing the engine phase to the retard side of the camshaft 2 with respect to the crankshaft will be described.

  When an operating condition representing a light load normal operating state or the like is satisfied in the internal combustion engine, the control circuit 200 controls the energization current to the solenoid 120 to a retard operating value Ir smaller than the advance operating value Ia. As a result, the spool 130 is driven to the position shown in FIGS. 4 and 8 as the phase change position on the retard side. At the phase change position on the retard angle side, the retard angle connection path is connected between the retard angle output port 114 communicating with the input port 116 and the advance angle output port 112 blocked with respect to the drain port 118. 240 is connected.

  Therefore, when positive torque is applied to the vane rotor 14, hydraulic oil is input from the pump 4 to the input passage 80 and the input port 116 as shown in FIG. 4, and then through the retard output port 114 and the retard output passage 76. It is supplied to the retarding chambers 56-59. Further, in the retard connection passage 240, input hydraulic oil to the input port 116 flows into the end 221, and hydraulic oil in the advance chambers 52 to 55 compressed by the action of positive torque passes through the advance output port 112. It flows into the end 242. At this time, since the hydraulic fluid flowing into the end portion 242 on the advanced output port 112 side becomes higher than the hydraulic fluid flowing into the end portion 221 on the retarded angle output port 114 side, the retarded connection check valve 230. Is opened, thereby allowing hydraulic fluid flow from the advance output port 112 side to the retard output port 114 side. Therefore, when the amount of hydraulic oil input from the pump 4 decreases, the hydraulic oil can be replenished from the advance output port 112 side, so that it operates in the retard chambers 56 to 59 whose volume is expanded by the action of positive torque. Oil shortage will be suppressed.

  When the positive torque is applied, the input hydraulic oil from the pump 4 flows into the advance connection passage 220 that communicates with the retard output port 114 at the common end 221, but the advance connection check valve 210 The hydraulic fluid flow toward the end 222 side is restricted by the valve closing. Further, since the advance output port 112 communicating with the retard connection passage 240 at the end 242 is closed with respect to the drain port 118, the hydraulic oil discharge from the drain port 118 is also restricted.

  On the other hand, when the negative torque acts on the vane rotor 14 and the retard chambers 56 to 59 are compressed, the hydraulic oil flows from the retard output port 114 to the connection passages 240 and 220 and the input passage 80 as shown in FIG. Try to backflow. However, at this time, in the retard connection passage 240 and the advance connection passage 220, the hydraulic fluid flows toward the advance output port 112 side and the end portion 222 side respectively, and the retard connection check valve 230 and the advance connection check valve 210. And, at the same time, in the input passage 80, the hydraulic oil flow toward the pump 4 is restricted by closing the input check valve 280. That is, the backflow from the retarded angle output port 114 to each of the connection passages 240 and 220 and the input passage 80 is restricted. Therefore, not only is the hydraulic oil outflow from the retard chambers 56 to 59 suppressed, but a situation in which the hydraulic oil supply to the advance chambers 52 to 55 is erroneously realized is avoided.

  According to such retarding operation, the functions of the connection check valves 230 and 210 are properly performed in a timely manner, the hydraulic oil is discharged from the advance chambers 52 to 55, and sufficient for the retard chambers 56 to 59. Since a sufficient amount of hydraulic fluid can be supplied, it is possible to ensure a high retardation response.

(3) Most retarded angle operation Hereinafter, the operation when the valve timing is most retarded while maintaining the engine phase at the most retarded phase on the retard side will be described.

  When an operating condition representing immediately after the start of the internal combustion engine is satisfied, or an operating condition for adjusting the engine phase to the most retarded phase on the retarded side at a rotational speed equal to or lower than the set value R of the internal combustion engine (throttle off, etc.) The control circuit 200 controls the energization current to the solenoid 120 to the maximum retardation operating value Ir0 that is smaller than the retardation operating value Ir. As a result, the spool 130 is driven to the most retarded phase position in FIGS. 5 and 9 as the most retarded phase position adjacent to the retarded phase change position in the moving direction. At such a most retarded phase position, the retard connection passage 240 connects between the retard output port 114 that communicates with the input port 116 and the advance output port 112 that communicates with the drain port 118. It becomes a state. The set value R is set to a low rotation value (500 to 1400 rpm or the like) that has a small influence on the engine phase due to the rotation of the drive unit 10, for example.

  Therefore, when positive torque is acting on the vane rotor 14, the input hydraulic oil from the pump 4 is continuously supplied to the retard chambers 56 to 59 according to the retard operation. Further, as shown in FIG. 5, the input hydraulic oil to the input port 116 flows into the end 221 of the retard connection passage 240, and the hydraulic oil in the advance chambers 52 to 55 compressed by the action of the positive torque. It flows into the advance angle output port 112. At this time, the hydraulic fluid flowing into the advance angle output port 112 flows into not only the end portion 242 of the retard angle connection passage 240 but also the drain port 118 opened to the atmosphere, thereby becoming atmospheric pressure. As a result, the hydraulic fluid flowing into the end 242 on the advance output port 112 side is lower in pressure than the hydraulic fluid flowing into the end 221 on the retard output port 114 side, so that the retard connection check valve 230 is The valve is closed, and not only the hydraulic fluid flow from the retard output port 114 side to the advance output port 112 side but also the hydraulic fluid flow from the advance output port 112 side to the retard output port 114 side is restricted. Become. Therefore, substantially all of the hydraulic fluid flowing into the advance angle output port 112 is discharged from the drain port 118. Therefore, the advance chambers 52 to 55 are emptied and the vanes 14b to 14e are moved to the retard side shoe 12b. It can be surely pressed to ~ 12e. That is, the state where the engine phase is most retarded can be stabilized.

  When the positive torque is applied, the input hydraulic oil from the pump 4 flows into the advance connection passage 220 as in the case of the retard operation, but the end connection 222 is closed by closing the advance connection check valve 210. The hydraulic fluid flow toward is restricted. In addition, when the negative torque is applied, the backflow from the retard output port 114 to each of the connection passages 240 and 220 and the input passage 80 is restricted as shown in FIG. .

  During the most retarded angle operation, the control circuit 200 monitors the actual phase Pr of the engine phase calculated from the detection results of the crank sensor 202 and the cam sensor 204, and learns the stable value as the reference phase Pr0. This reference phase Pr0 is stored in the memory 200a of the control circuit 200 and is updated each time learning is performed. Therefore, in the present embodiment, the current actual phase Pr and the current target phase Pt necessary for energization control of the solenoid 120 are calculated based on the latest reference phase Pr0 stored in the memory 200a. . In addition, as described above, in the present embodiment, since the most retarded angle holding state of the engine phase at the time of learning of the reference phase Pr0 can be stabilized, the energization control based on the accurate reference phase Pr0 is realized and the valve timing adjustment accuracy is achieved. Can be increased.

(4) Normal holding operation Hereinafter, the operation in the case where the engine phase is held in a predetermined target phase region excluding the retarded endmost phase phase to hold the valve timing will be described.

  When an operation condition representing a stable operation state such as an accelerator holding state is established in the internal combustion engine, the control circuit 200 causes the energization current to the solenoid 120 to be smaller than the advance operation value Ia and greater than the retard operation value Ir. The holding operation value In is controlled. As a result, the spool 130 is driven to the normal holding position in FIG. In the normal holding position, both the output ports 112 and 114 are closed with respect to the input port 116 and the drain port 118.

  Accordingly, the input hydraulic oil from the pump 4 to the input passage 80 and the input port 116 is not supplied to any of the advance chambers 52 to 55 and the retard chambers 56 to 59, and the advance chambers 52 to 55 and the retard angle are not supplied. The hydraulic oil outflow from any of the chambers 56 to 59 is restricted. Therefore, the change of the engine phase can be suppressed in the target phase region and can be held at the valve timing corresponding to the region.

  In the normal holding position, the input hydraulic oil from the pump 4 flows from the input port 116 into the common end 221 of the connection passages 220 and 240, but the other end is closed by closing the connection check valves 210 and 230. The hydraulic oil flow toward the 222, 242 side is restricted.

  According to the first embodiment described above, valve timing adjustment suitable for an internal combustion engine can be performed quickly and accurately.

(Second embodiment)
As shown in FIG. 10, the second embodiment of the present invention is a modification of the first embodiment. In the control unit 1030 of the second embodiment, a drain passage 1082 that is open to the atmosphere and that can discharge hydraulic oil to the oil pan 5 is provided separately from the drain passage 82.

  Further, in the control unit 1030 of the second embodiment, the spool valve 1100 has a drain port 1118 that is opened to the atmosphere through the drain passage 1082 and discharges hydraulic oil to the passage 1082, separately from the drain port 118. As shown in FIG. 11, the drain port 1118 is provided in the sleeve 1110 closer to the end 110 a than the retard output port 114.

  Further, as shown in FIG. 10, in the control unit 1030 of the second embodiment, the spool valve 1100 has a relay passage 1260 for enabling the retard output port 114 to communicate with the drain port 1118, separately from the relay passage 260. The spool 1130 is formed. As shown in FIG. 11, the relay passage 1260 passes through the retarded angle support land 138, and both end portions 1261 and 1262 are open on the outer peripheral surface of the spool 1130. Thus, at least at the spool position in FIG. 11, both end portions 1261 and 1262 of the relay passage 1260 communicate with the drain port 1118. 11, both end portions 1261 and 1262 of the relay passage 1260 communicate with the gap between the retard switching land 136 and the retard support land 138 through the outer peripheral space of the retard support land 138 in the sleeve 1110. It is supposed to be.

  Here, in the spool position of FIG. 11, the retard switching land 136 is supported only on the input port 116 side of the retard output port 114, so that the retard output port 114 and the retard support land 136 are supported. It communicates with the gap between the lands 138. Therefore, at the spool position in FIG. 11, the drain port 1118 and the retard output port 114 communicate with each other through the relay passage 1260. On the other hand, in the spool positions shown in FIGS. 12 to 15, the end portions 1261 and 1262 of the relay passage 1260 are blocked by the gap between the lands 136 and 138, so that the retard angle output to the drain port 1118. The port 114 is blocked.

  In the spool position of FIG. 11 according to the second embodiment, the advance angle switching land 134 is supported only on the drain port 118 side of the advance angle output port 112, so that the advance angle output port 112 is moved to the advance angle switching land 134. In addition, the input port 116 is communicated through a gap between the retard angle switching land 136.

  In such a second embodiment, the advance operation by the spool position of FIG. 12, the retard operation by the spool position of FIG. 13, the most retarded operation by the spool position of FIG. 14, and the holding operation by the spool position of FIG. Implemented according to one embodiment. In addition, in the second embodiment, the most advanced angle operation according to the spool position of FIG. 11 is performed.

  Specifically, the most advanced angle operation is performed when an operating condition (such as fully opening the throttle at 4000 rpm or less) for adjusting the engine phase to the most advanced phase at the advance angle side at a rotational speed equal to or lower than the set value R of the internal combustion engine, Be started. In this most advanced operation, the control circuit 200 controls the energization current to the solenoid 120 to the most advanced operation value Ia0 that is larger than the advance operation value Ia. As a result, the spool 1130 is driven to the most advanced phase position in FIGS. 11 and 16 as the most advanced phase position adjacent to the advanced phase change position in the moving direction. At the most advanced phase position, the advance connection passage 220 connects between the advance output port 112 that communicates with the input port 116 and the retard output port 114 that communicates with the drain port 1118. It becomes a state. In addition, about the said setting value R, it sets to the same value as the time of the most retarded angle operation | movement demonstrated in 1st embodiment, for example.

  Therefore, when negative torque is acting on the vane rotor 14, the input hydraulic oil from the pump 4 is continuously supplied to the advance chambers 52 to 55 in accordance with the advance operation described in the first embodiment. Further, as shown in FIG. 11, the input hydraulic oil to the input port 116 flows into the end 221 of the advance connection passage 220 and the hydraulic oil in the retard chambers 56 to 59 compressed by the action of the negative torque. It flows into the retarded angle output port 114. At this time, the hydraulic fluid flowing into the retarded angle output port 114 flows into not only the end portion 222 of the advanced angle connecting passage 220 but also the drain port 1118 opened to the atmosphere, thereby becoming atmospheric pressure. As a result, the hydraulic fluid flowing into the end portion 222 on the retarded angle output port 114 side is lower in pressure than the hydraulic fluid flowing into the end portion 221 on the advanced angle output port 112 side. The valve is closed, and not only the hydraulic oil flow from the advance output port 112 side to the retard output port 114 side but also the hydraulic oil flow from the retard output port 114 side to the advance output port 112 side is restricted. Become. Therefore, substantially all of the hydraulic fluid flowing into the retard output port 114 is discharged from the drain port 1118. Therefore, the retard chambers 56 to 59 are emptied and the vanes 14b to 14e are moved to the advance shoe 12b. It can be surely pressed to ~ 12e. That is, the most advanced angle holding state of the engine phase can be stabilized.

  It should be noted that the input hydraulic oil from the pump 4 flows into the retard connection passage 240 as in the advance operation described in the first embodiment when the negative torque is applied. The hydraulic fluid flow toward the end 242 side is restricted by the valve closing. Further, when the positive torque is applied, the reverse flow from the advance output port 112 to each of the connection passages 240 and 220 and the input passage 80 is performed as in the advance operation described in the first embodiment, as shown in FIG. Will be regulated. Further, during the above-described most advanced angle operation, the learning of the reference phase Pr0 described in the first embodiment may be performed instead of the learning during the most retarded angle operation. In this case, the valve timing is adjusted. The accuracy can be increased.

  According to the second embodiment described above, the valve timing adjustment suitable for the internal combustion engine can be performed quickly and accurately.

(Other embodiments)
A plurality of embodiments of the present invention have been described so far. However, the present invention is not construed as being limited to these embodiments, and can be applied to various embodiments without departing from the scope of the present invention. Can do.

  Specifically, in the drive unit 10, for example, an elastic body such as an assist spring that biases the cam shaft 2 may be provided on the side opposite to the bias side of the average torque of the variable torque. As for the drive unit 10, the housing 12 may be rotated in conjunction with the camshaft 2, and the vane rotor 14 may be rotated in conjunction with the crankshaft.

  In each of the connection check valves 210 and 230 in the spool valves 100 and 1100 of the control units 30 and 1030, elastic members for urging the valve members 214 and 234 may be provided individually. In this case, the ends of the elastic members of the connection check valves 210 and 230 opposite to the valve members 214 and 234 are locked by the inner wall surfaces of the connection passages 220 and 240, respectively.

  The solenoid 120 that drives the spools 130 and 1130 in the spool valves 100 and 1100 may be replaced with, for example, a piezo actuator or a hydraulic actuator. Further, regarding the sleeves 110 and 1110 in the spool valves 100 and 1100, the port 114 is communicated with the advance chambers 52 to 55 via the advance output passage 72 and the port 112 is retarded via the retard output passage 76. You may form so that it may communicate with the chambers 56-59. In this case, the relationship between the advance angle operation and the retard angle operation, and the relationship between the most advance angle operation and the most retarded angle operation are opposite to those in the above-described embodiment.

  In the spool valve 1100, the drain port 118 and the relay passage 260 may not be provided as shown in FIG. In this case, the most retarded angle operation is not performed, and learning of the reference phase Pr0 is performed in the most advanced angle operation.

  In addition to the device that adjusts the valve timing of the intake valve, the present invention provides a device that adjusts the valve timing of the exhaust valve as a “valve”, and a device that adjusts the valve timing of both the intake valve and the exhaust valve. It can also be applied.

It is a block diagram which shows the valve timing adjustment apparatus by 1st embodiment of this invention. It is a schematic diagram for demonstrating the fluctuation | variation torque which acts on the drive part of FIG. It is sectional drawing which shows typically the detailed structure and the operating state of the spool valve of FIG. It is sectional drawing which shows the operating state of the spool valve of FIG. 1 typically. It is sectional drawing which shows the operating state of the spool valve of FIG. 1 typically. It is sectional drawing which shows the operating state of the spool valve of FIG. 1 typically. It is sectional drawing which shows the operating state of the spool valve of FIG. 1 typically. It is sectional drawing which shows the operating state of the spool valve of FIG. 1 typically. It is sectional drawing which shows the operating state of the spool valve of FIG. 1 typically. It is a block diagram which shows the valve timing adjustment apparatus by 2nd embodiment of this invention. It is sectional drawing which shows typically the detailed structure and the operating state of the spool valve of FIG. It is sectional drawing which shows typically the operating state of the spool valve of FIG. It is sectional drawing which shows typically the operating state of the spool valve of FIG. It is sectional drawing which shows typically the operating state of the spool valve of FIG. It is sectional drawing which shows typically the operating state of the spool valve of FIG. It is sectional drawing which shows typically the operating state of the spool valve of FIG. It is sectional drawing which shows typically the modification of the spool valve of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve timing adjusting device, 2 cam shaft, 4 pump (fluid input source), 5 oil pan, 10 drive part, 12 housing (drive rotary body), 12a sprocket part, 12b, 12c, 12d, 12e shoe, 14 vane rotor ( Driven rotor), 14a boss portion, 14b, 14c, 14d, 14e vane, 30, 1030 control unit, 50 storage chamber, 52, 53, 54, 55 advance chamber, 56, 57, 58, 59 retard chamber, 72 advance output passage, 76 retard output passage, 80 input passage, 82,1082 drain passage, 100, 1100 spool valve, 110, 1110 sleeve, 112 advance output port, 114 retard output port, 116 input port, 118 , 1118 Drain port, 120 Solenoid, 130, 1130 Spool, 132 Angular support land, 134 advance angle switching land, 136 retard angle switching land, 138 retard angle support land, 139 drive shaft, 140 return spring, 200 control circuit (control means), 200a memory, 202 crank sensor, 204 cam sensor, 210 advance Angular connection check valve, 212 advance valve seat, 214 advance valve member, 215 advance retainer, 216 elastic member, 220 advance connection passage, 221 common end, 222,242 end, 230 retard connection check Valve, 232 retard valve seat, 234 retard valve member, 235 retard retainer, 240 retard connection passage, 260, 1260 relay passage, 261, 262, 1261, 1262 end, 280 input check valve

Claims (8)

  1. A valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine,
    A drive rotating body having a shoe protruding radially inward and rotating in conjunction with the crankshaft;
    A vane that protrudes radially outward, rotates in conjunction with the camshaft, divides an advance chamber and a retard chamber in the rotational direction between the vane and the shoe of the drive rotor, and A driven rotor for driving the camshaft to the advance side or the retard side with respect to the crankshaft by supplying a working fluid to the advance chamber or the retard chamber;
    An input port through which a working fluid is input from a fluid input source, a drain port for discharging the working fluid, a first output port for outputting the working fluid to one of the advance chamber and the retard chamber, the advance chamber, and A second output port for outputting a working fluid to the other of the retard chamber and a spool are provided, and the driven rotor is rotated relative to the drive rotor to change the phase of the camshaft relative to the crankshaft. wherein for moving the position of the spool for the holding together is set as the phase change position, the against press the vanes of the driven rotor phase endmost phase relative to the shoe of the drive rotor movement position of the spool is set as an endmost phase position, in the phase change position of the spool, said second output with communicating the first output port to the input port The port is closed with respect to the drain port, and the first output port is communicated with the input port and the second output port is communicated with the drain port at the extreme end phase position of the spool. A spool valve;
    A connection passage formed in the spool and connecting the first output port and the second output port at the phase change position of the spool;
    The working fluid flow that is disposed in the connection passage and opens at the phase change position of the spool allows the working fluid flow from the second output port side to the first output port side, while the phase of the spool A connection check valve that regulates the flow of working fluid from the first output port side to the second output port side by closing the valve at the change position;
    A valve timing adjusting device comprising:
  2. The spool valve includes the spool in which a most retarded phase position, which is a movement position for maintaining the phase at the most retarded phase on the retarded angle side , is set as the most end phase position. In the most retarded phase position, the retard output port that outputs the working fluid to the retard chamber functions as a first output port, and the advance output port that outputs the working fluid to the advance chamber serves as the second output port. The valve timing adjusting device according to claim 1, wherein
  3. The spool valve has the spool in which a most advanced angle phase position, which is a movement position for maintaining the phase at the most advanced phase on the advance side , is set as the most end phase position, In the most advanced phase position, the advance output port that outputs the working fluid to the advance chamber functions as a first output port, and the retard output port that outputs the working fluid to the retard chamber serves as the second output port. The valve timing adjusting device according to claim 1 or 2, characterized by functioning as
  4. The spool valve has the drain port that is opened to the atmosphere, and the spool in which the phase change position and the endmost phase position are set adjacent to each other in the movement direction,
    The connecting passage connects the first output port and the second output port at the phase change position and the endmost phase position of the spool,
    In the phase change position and the endmost phase position of the spool, the connection check valve opens when the second output port side is higher than the first output port side in the connection passage, 4. The valve timing adjusting device according to claim 1, wherein the valve timing adjusting device closes when the second output port side is at a lower pressure than the first output port side in the connection passage. 5.
  5. An input passage communicating with the fluid input source and the input port;
    The working fluid flow that is disposed in the input passage and that is allowed to open from the fluid input source side toward the input port side is allowed by opening the valve, while the working fluid flow that is directed from the input port side toward the fluid input source side is allowed to be closed. The valve timing adjusting device according to any one of claims 1 to 4, further comprising an input check valve to be regulated.
  6.   Control means for controlling the movement position of the spool based on a reference phase of the phases, and control for learning the actual phase as the reference phase in a state where the movement position is controlled to the extreme end phase position. The valve timing adjusting device according to any one of claims 1 to 5, further comprising means.
  7.   7. The valve timing adjusting device according to claim 6, wherein when the start of the internal combustion engine is completed, the control means learns the reference phase by controlling the moving position to the endmost phase position. .
  8.   The control means controls the moving position to the endmost phase position and controls the reference position when the condition for adjusting the phase to the endmost phase is satisfied at a rotational speed equal to or lower than a set value of the internal combustion engine. The valve timing adjusting device according to claim 6 or 7, wherein the phase is learned.
JP2008003604A 2008-01-10 2008-01-10 Valve timing adjustment device Active JP4518149B2 (en)

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JP2008003604A JP4518149B2 (en) 2008-01-10 2008-01-10 Valve timing adjustment device
DE200810055175 DE102008055175A1 (en) 2008-01-10 2008-12-29 Valve timing adjuster
US12/349,637 US20090178635A1 (en) 2008-01-10 2009-01-07 Valve timing adjuster

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CN103168152B (en) * 2010-11-02 2015-10-21 博格华纳公司 Cam torque actuation-torsion assist phaser
JP6236444B2 (en) * 2012-07-13 2017-11-22 ボーグワーナー インコーポレーテッド 5-way oil control valve with integrated vent spool
US9115610B2 (en) * 2013-03-11 2015-08-25 Husco Automotive Holdings Llc System for varying cylinder valve timing in an internal combustion engine
EP2796673B1 (en) * 2013-04-22 2018-03-07 Hilite Germany GmbH Central valve for a pivotable motor adjuster
DE102013104573B4 (en) * 2013-05-03 2018-05-17 Hilite Germany Gmbh Hydraulic valve and Schwenkmotorversteller
JP6171731B2 (en) * 2013-08-27 2017-08-02 アイシン精機株式会社 Control valve
US9341090B2 (en) * 2014-02-06 2016-05-17 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
CN107191236B (en) * 2016-03-14 2019-11-08 伊希欧1控股有限公司 The hydraulic valve of the piston of hydraulic valve for camshaft phase adjuster and the camshaft phase adjuster for camshaft
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
SE539977C2 (en) 2016-06-08 2018-02-20 Scania Cv Ab Variable cam timing phaser Utilizing hydraulic logic elements
SE539980C2 (en) 2016-06-08 2018-02-20 Scania Cv Ab Variable cam timing phaser Utilizing series-coupled check valves
DE102016118962A1 (en) * 2016-10-06 2018-04-12 Denso Corporation Camshaft adjuster and associated switch body
DE102019101159A1 (en) * 2018-02-21 2019-08-22 ECO Holding 1 GmbH Hydraulic valve for a Schwenkmotorversteller a camshaft
EP3530892A1 (en) * 2018-02-21 2019-08-28 ECO Holding 1 GmbH Hydraulic valve for a pivoting engine adjuster of a camshaft
EP3530891A1 (en) * 2018-02-21 2019-08-28 ECO Holding 1 GmbH Hydraulic valve for a pivoting engine adjuster of a camshaft

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US20090178635A1 (en) 2009-07-16
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