JPWO2020084764A1 - Valve timing adjuster - Google Patents

Abstract

The OCV (10) provided in the valve timing adjusting device has a supply port (21) communicating with the oil supply source, an advance port (22) communicating with the advance hydraulic chamber (61), and a retard hydraulic chamber (62). ), And a center bolt (11) having a retard port (23) communicating with the outside of the OCV (10) and a drain port (24) communicating with the outside of the OCV (10), and reciprocating in the center bolt (11) in the axial direction. A spool (12) for supplying and discharging oil via a supply port (21), an advance port (22), a retard port (23), and a drain port (24) is provided according to the stroke amount. , When the spool (12) was placed in the initial position, the supply port (21) was communicated with the advance port (22) and the retard port (23), and the spool (12) was placed in the final position. Occasionally, the advance port (22) and the outside of the OCV (10) are communicated with each other, while the retard port (23) and the drain port (24) are communicated with each other.

Description

The present invention relates to a valve timing adjusting device including an oil control valve.

Conventionally, a valve timing adjusting device for adjusting the opening / closing timing of an engine valve using oil as a working fluid has been provided. This valve timing adjusting device includes a housing and a rotor that can rotate relative to the housing, and a lock member provided in the housing can be fitted into a fitting hole formed in the rotor. It has become. In this way, the valve timing adjusting device can lock the rotor in a predetermined lock phase by fitting the lock member into the fitting hole.

If the engine is started with the rotor arranged in a phase different from the lock phase, the rotor will be used between the time when the engine starts to rotate and the time when oil is supplied to the valve timing adjuster. Due to the reaction force of the camshaft, it swings greatly and generates noise. Therefore, the valve timing adjusting device needs to return the rotor to the lock phase and lock it when the engine is stopped. Then, such a conventional valve timing adjusting device is disclosed in, for example, Patent Document 1.

Japanese Unexamined Patent Publication No. 2016-50576

However, the lock phase in the conventional valve timing adjusting device is limited according to the number of lock members and fitting holes. Therefore, the conventional valve timing adjusting device cannot lock the rotor in an ideal phase with respect to the temperature of the engine oil in the idling start / stop mode of the engine.

The present invention has been made to solve the above problems, and provides a valve timing adjusting device capable of locking the rotor in a phase corresponding to the temperature of oil in the idling start / stop mode of the engine. The purpose is.

The valve timing adjusting device according to the present invention includes a case that rotates synchronously with the crank shaft of the internal combustion engine, a rotor that is arranged coaxially so as to be rotatable relative to the case and opens and closes the valve of the internal combustion engine, and a case. A partition is formed between the rotor and the case, and a partition is formed between the case and the rotor, and the partition is formed between the case and the rotor to rotate the rotor relative to the advance direction with the supply of the working fluid. , A retard hydraulic chamber that rotates the rotor relative to the retard direction and an oil control valve that controls the supply and discharge of the working fluid to the advance hydraulic chamber and the retard hydraulic chamber are provided, and the rotor has the most retard angle. The oil control valve is urged in the advance direction from the phase to the original phase located between the latest retard phase and the most advance phase, and the oil control valve is a supply port and advance angle that communicate with the supply source of the working fluid. A housing with an advance port communicating with the hydraulic chamber, a retard port communicating with the retard hydraulic chamber, and a drain port communicating with the outside of the oil control valve, and reciprocating between the initial position and the final position in the housing. When the spool is placed in the initial position, it is provided with a spool that moves and supplies and discharges the working fluid via a supply port, an advance port, a retard port, and a drain port according to the stroke amount. , The supply port communicates with the advance port and the retard port, and when the spool is placed in the final position, the advance port communicates with the outside of the oil control valve, while the retard port and the drain port communicate with each other. It is characterized by being communicated.

The valve timing adjusting device according to the present invention includes a case that rotates synchronously with the crank shaft of the internal combustion engine, a rotor that is arranged coaxially so as to be rotatable relative to the case and opens and closes the valve of the internal combustion engine, and a case. A partition is formed between the rotor and the case, and a partition is formed between the case and the rotor, and the partition is formed between the case and the rotor to rotate the rotor relative to the advance direction with the supply of the working fluid. , A retard hydraulic chamber that rotates the rotor relative to the retard direction and an oil control valve that controls the supply and discharge of the working fluid to the advance hydraulic chamber and the retard hydraulic chamber are provided, and the rotor has the most retard angle. The oil control valve is urged in the advance direction from the phase to the original phase located between the latest retard phase and the most advance phase, and the oil control valve is a supply port and advance angle that communicate with the supply source of the working fluid. A housing with an advance port communicating with the hydraulic chamber, a retard port communicating with the retard hydraulic chamber, and a drain port communicating with the outside of the oil control valve, and reciprocating between the initial position and the final position in the housing. When the spool is placed in the initial position, it is provided with a spool that moves and supplies and discharges the working fluid via a supply port, an advance port, a retard port, and a drain port according to the stroke amount. , The advance port and the outside of the oil control valve are communicated with each other, while the retard angle port and the drain port are communicated with each other, and when the spool is placed in the final position, the supply port, the advance angle port and the retard angle port are connected. It is characterized by being communicated.

According to the present invention, in the idling start / stop mode of the engine, the rotor can be locked in a phase corresponding to the temperature of the oil.

It is a block diagram of the OCV provided in the valve timing adjustment device which concerns on Embodiment 1. FIG. FIG. 1A is an external view of the OCV. FIG. 1B is a partial vertical sectional view of the OCV. FIG. 1C is a vertical cross-sectional view of the OCV. FIG. 1D is a view when the tip surface of the spool is viewed from the axial direction. It is a figure which showed the transition state of the advance angle port and the retard angle port with respect to the stroke amount of the spool in Embodiment 1. FIG. It is a figure which showed the operation of OCV which concerns on Embodiment 1. FIG. FIG. 3A is a diagram showing an initial state of OCV. FIG. 3B is a diagram showing a retarded angle supply state of OCV. FIG. 3C is a diagram showing an intermediate holding state of OCV. It is a figure which showed the operation of OCV which concerns on Embodiment 1. FIG. FIG. 4A is a diagram showing an advance angle supply state of OCV. FIG. 4B is a diagram showing the final state of OCV. FIG. 5 is a cross-sectional view of the valve timing adjusting device according to the first embodiment. It is a figure which showed how the rotor returns to the original phase. FIG. 6A is a cross-sectional view of the valve timing adjusting device when the rotor returns to the original phase from the retard side. FIG. 6B is a diagram showing a state of the valve timing adjusting device when the rotor returns to the original phase from the advance angle side. It is a figure which showed the operation of the valve timing adjusting apparatus which concerns on Embodiment 1. FIG. FIG. 7A is a cross-sectional view of the valve timing adjusting device in the retarded angle supply state of the OCV. FIG. 7B is a cross-sectional view of the valve timing adjusting device in the advance angle supply state of the OCV. FIG. 7C is a cross-sectional view of the valve timing adjusting device in the final state of the OCV. FIG. 5 is a cross-sectional view showing an operation when the valve timing adjusting device according to the first embodiment is used in an idle state of the engine. FIG. 8A is a diagram showing a state when the vehicle is keyed off in the idle state. FIG. 8B is a diagram showing a state in which the rotor returns to the original phase. FIG. 8C is a diagram showing a state in which the rotor is locked. It is a block diagram of the OCV provided in the valve timing adjusting apparatus which concerns on Embodiment 2. FIG. FIG. 9A is an external view of the OCV. FIG. 9B is a partial vertical sectional view of the OCV. FIG. 9C is a vertical cross-sectional view of the OCV. FIG. 9D is a view when the tip surface of the spool is viewed from the axial direction. FIG. 9E is a view when the stopper surface of the stopper is viewed from the axial direction. It is a figure which showed the transition state of the advance angle port and the retard angle port with respect to the stroke amount of the spool in Embodiment 2. FIG. It is a figure which showed the operation of OCV which concerns on Embodiment 2. FIG. FIG. 11A is a diagram showing an initial state of OCV. FIG. 11B is a diagram showing a retarded angle supply state of OCV. FIG. 11C is a diagram showing an intermediate holding state of OCV. It is a figure which showed the operation of OCV which concerns on Embodiment 2. FIG. FIG. 12A is a diagram showing an advance angle supply state of OCV. FIG. 12B is a diagram showing the final state of OCV.

Hereinafter, in order to explain the present invention in more detail, a mode for carrying out the present invention will be described with reference to the accompanying drawings.

Embodiment 1.
The valve timing adjusting device provided with an oil control valve (hereinafter referred to as OCV) according to the first embodiment will be described in detail with reference to FIGS. 1 to 6.

First, the configuration of the OCV according to the first embodiment will be described with reference to FIG. FIG. 1A is an external view of the OCV. FIG. 1B is a partial vertical sectional view of the OCV. FIG. 1C is a vertical cross-sectional view of the OCV. FIG. 1D is a view when the tip surface of the spool is viewed from the axial direction.

The valve timing adjusting device adjusts the opening / closing timing of the intake valve or the exhaust valve according to the operating state of the engine serving as the internal combustion engine. On the other hand, the OCV 10 controls the supply, discharge, or retention of oil to the advance hydraulic chamber and the retard hydraulic chamber of the valve timing adjusting device. That is, the oil serves as the working fluid of the valve timing adjusting device.

The OCV 10 includes a center bolt 11, a spool 12, a stopper 13, and a spring 14.

The center bolt 11 is a bolt for fixing the valve timing adjusting device to the camshaft. The center bolt 11 has a tubular shape, and has a supply port 21, an advance angle port 22, a retard angle port 23, a drain port 24, and partitions 25 to 29. The center bolt 11 constitutes the housing of the OCV 10.

The supply port 21, the advance angle port 22, and the retard angle port 23 are connected between the outer peripheral surface and the inner peripheral surface of the center bolt 11. Further, the supply port 21 communicates with the oil supply source. The advance port 22 communicates with the advance hydraulic chamber of the valve timing adjusting device, and the retard port 23 communicates with the retard hydraulic chamber of the valve timing adjusting device. Further, the drain port 24 constitutes an opening on the tip end side of the center bolt 11 and always communicates with the outside of the OCV 10. The oil supply source is provided outside the valve timing adjusting device and the OCV 10.

The partitions 25 to 29 are formed in an annular shape along the circumferential direction of the inner peripheral surface of the center bolt 11, and project from the inner peripheral surface inward in the radial direction. The supply port 21 is open between the partitions 26 and 27. Further, the advance angle port 22 is opened between the partitions 25 and 26. Further, the retard port 23 is open between the partitions 27 and 28.

However, the center bolt 11 has a configuration in which the port opened between the partitions 25 and 26 is the advance port 22 and the port opened between the partitions 27 and 28 is the retard port 23. The port opened between the partitions 27 and 26 may be the retard port 23, and the port opened between the partitions 27 and 28 may be the advance port 22. That is, the supply port 21 may be arranged between the advance angle port 22 and the retard angle port 23 in the axial direction of the center bolt 11.

The spool 12 is supported so as to be reciprocally movable in the axial direction of the center bolt 11 inside the partitions 25 to 29 of the center bolt 11 in the radial direction. Further, the spool 12 has a hollow shape, and has a drain port 31, a flow path 32, partitions 33 to 38, and a lateral groove 39. As a result, the OCV 10 supplies oil to the valve timing adjusting device via the supply port 21, the advance angle port 22, the retard angle port 23, and the drain port 24 according to the stroke amount that is the movement amount of the spool 12. Can be discharged.

The drain port 31 connects between the outer peripheral surface and the inner peripheral surface of the spool 12, and always communicates with the outside of the OCV 10, and the flow path 32 is in the spool 12 in the axial direction of the spool 12. The base end side of the flow path communicates with the drain port 31, while the tip thereof communicates with the drain port 24 of the center bolt 11.

The partitions 33 to 38 are formed in an annular shape along the circumferential direction of the outer peripheral surface of the spool 12, and protrude outward from the outer peripheral surface in the radial direction. That is, the partitions 33 to 38 are supported in the partitions 25 to 29 so as to be reciprocally movable in the axial direction of the center bolt 11. The drain port 31 is open on the outer side of the spool 12 in the axial direction with respect to the partition 33.

The lateral groove 39 is provided so as to penetrate the flow path 32 and the partition 38 in the radial direction thereof, and is formed so as to cut out the partition 38.

The stopper 13 regulates the movement of the spool 12. The stopper 13 has an annular shape and is provided in the opening on the base end side of the center bolt 11. Further, the stopper 13 is provided so that the partition 33 arranged on the most proximal side of the spool 12 can come into contact with the spool 12 and face the drain port 31 in the radial direction thereof.

The spring 14 is provided between the inside of the center bolt 11 on the tip end side and the tip of the flow path 32 in the spool 12, and urges the spool 12 toward the stopper 13. As a result, in the spool 12, the partition 33 comes into contact with the stopper 13 from the tip end side of the center bolt 11, so that the spool 12 is restricted from moving to the proximal end side.

At this time, the moving position of the spool 12 when the partition 33 comes into contact with the stopper 13 becomes the initial position, and the stroke amount thereof becomes the minimum. Further, the moving position of the spool 12 when the partition 33 is farthest from the stopper 13 is the final position, and the stroke amount thereof is the maximum. That is, the spool 12 reciprocates between the initial position and the final position.

Further, the base end of the spool 12 is pressed by an external solenoid. As a result, the moving position of the spool 12 is determined by the balance between the urging force of the spring 14 and the pressing force of the external solenoid. In other words, the stroke amount of the spool 12 changes depending on the current value or duty value applied to the external solenoid.

Further, the OCV 10 can shift to five states by changing the stroke amount of the spool 12. Specifically, the OCV 10 can shift to any one of the initial state, the retard angle supply state, the intermediate holding state, the advance angle supply state, and the final state.

Next, the five states of OCV according to the first embodiment will be described with reference to FIG. FIG. 2 is a diagram showing a transition state of the advance port and the retard port with respect to the stroke amount of the spool in the first embodiment.

The OCV 10 shifts in the order of the initial state, the retard angle supply state, the intermediate holding state, the advance angle supply state, and the final state as the stroke amount of the spool 12 increases. At this time, when the stroke amount of the spool 12 is minimized, the OCV 10 is arranged at the initial position of the spool 12 and shifts to the initial state. Further, in the OCV 10, when the stroke amount of the spool 12 is maximized, the spool 12 is arranged at the final position and shifts to the final state.

In the initial state, the supply port 21 and the advance angle port 22 communicate with each other to supply the oil flowing into the supply port 21 to the advance angle hydraulic chamber via the advance angle port 22, while supplying the oil to the advance angle hydraulic chamber 21. This is a state in which the oil flowing into the supply port 21 is supplied to the retard angle hydraulic chamber via the retard angle port 23 by communicating with the retard angle port 23.

In the retarded angle supply state, the advance angle port 22 and the base end side opening of the center bolt 11 communicate with each other, so that the oil stored in the advance angle hydraulic chamber is discharged through the base end side opening. The supply port 21 and the retard angle port 23 communicate with each other, so that the oil flowing into the supply port 21 is supplied to the retard angle hydraulic chamber via the retard angle port 23. That is, the retard angle supply state is a state in which the rotor of the valve timing adjusting device rotates in the retard angle direction.

In the intermediate holding state, the advance angle port 22 is cut off from the supply port 21 and the drain ports 24 and 31, so that the oil pressure in the advance angle hydraulic chamber is maintained as it is, while the retard angle port 23 is the supply port 21. In addition, the flood control in the retard angle hydraulic chamber is maintained as it is by being cut off from the drain ports 24 and 31. That is, the intermediate holding state is a state in which the rotor of the valve timing adjusting device is held in the current phase.

The advance angle supply state means that the supply port 21 and the advance angle port 22 communicate with each other to supply the oil flowing into the supply port 21 to the advance angle hydraulic chamber through the advance angle port 22, while retarding the angle. This is a state in which the oil stored in the retarded hydraulic chamber is discharged through the drain ports 24 and 31 by communicating the port 23 and the drain ports 24 and 31. That is, the advance angle supply state is a state in which the rotor of the valve timing adjusting device rotates in the advance angle direction.

In the final state, the advance angle port 22 and the base end side opening of the center bolt 11 communicate with each other, so that the oil stored in the advance angle hydraulic chamber is discharged through the base end side opening, but is delayed. This is a state in which the corner port 23 and the drain ports 24 and 31 communicate with each other to discharge the oil stored in the retard angle hydraulic chamber through the drain ports 24 and 31.

Next, the operation of the OCV according to the first embodiment will be described with reference to FIGS. 3 and 4. FIG. 3A is a diagram showing an initial state of OCV. FIG. 3B is a diagram showing a retarded angle supply state of OCV. FIG. 3C is a diagram showing an intermediate holding state of the OCV. FIG. 4A is a diagram showing an advance angle supply state of OCV. FIG. 4B is a diagram showing the final state of OCV. The arrows shown in FIGS. 3A, 3B, 4A, and 4B indicate the flow of oil.

In the OCV 10 in the initial state shown in FIG. 3A, the partition 25 and the partition 34 are in contact with each other over the entire circumference and seal between them. The partition 28 and the partition 38 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 passes between the partitions 26, 35, and 36, and is then supplied to the advance port 22 by the seal between the partitions 25 and 34. Further, the oil flowing in from the supply port 21 passes between the partitions 27, 36, and 37, and then is supplied to the retarded port 23 by the seal between the partitions 28 and 29.

In the OCV 10 in the retarded angle supply state shown in FIG. 3B, the partition 26 and the partition 35 are in contact with each other over the entire circumference and seal between them. The partition 28 and the partition 38 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil stored in the advance port 22 passes between the partitions 25, 33, and 34, and then is discharged to the outside of the OCV 10 from the opening on the proximal end side of the center bolt 11. Further, the oil flowing in from the supply port 21 passes between the partitions 27, 36, and 37, and then is supplied to the retarded port 23 by the seal between the partitions 28 and 38. At this time, the oil is not supplied to the advance port 22 by the seal between the partitions 26 and 35.

In the OCV 10 in the intermediate holding state shown in FIG. 3C, the partition 25 and the partition 33 are in contact with each other over the entire circumference and seal between them. The partition 26 and the partition 35 are in contact with each other over the entire circumference and seal between them. The partition 27 and the partition 36 are in contact with each other over the entire circumference and seal between them. The partition 28 and the partition 38 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 is not supplied to the advance port 22 by the seal between the partitions 26 and 35. Further, the oil flowing in from the supply port 21 is not supplied to the retarded port 23 by the seal between the partitions 27 and 36. Further, the oil stored in the advance port 22 is not discharged to the outside of the OCV 10 by the seal between the partitions 25 and 33. On the other hand, the oil stored in the retarded port 23 is not discharged from the drain ports 24 and 31 due to the seal between the partitions 28 and 38.

In the OCV 10 in the lead angle supply state shown in FIG. 4A, the partition 25 and the partition 33 are in contact with each other over the entire circumference and seal between them. The partition 27 and the partition 36 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 passes between the partitions 26, 34, and 35, and is then supplied to the advance port 22 by the seal between the partitions 25 and 33. At this time, the oil is not supplied to the retard port 23 by the seal between the partitions 27 and 36. Further, the oil stored in the retard port 23 passes between the partitions 28, 37, 38, then flows into the flow path 32 from the lateral groove 39, and is discharged from the drain ports 24, 31.

In the OCV 10 in the final state shown in FIG. 4B, the partition 26 and the partition 34 are in contact with each other over the entire circumference and seal between them. The partition 27 and the partition 36 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 is not supplied to the advance port 22 by the seal between the partitions 26 and 34. Further, the oil flowing in from the supply port 21 is not supplied to the retarded port 23 by the seal between the partitions 27 and 36. Further, the oil stored in the advance port 22 passes between the partitions 25 and 33, and then is discharged to the outside of the OCV 10 from the opening on the proximal end side of the center bolt 11. On the other hand, the oil stored in the retarded port 23 passes between the partitions 28, 37, 38, then flows into the flow path 32 from the lateral groove 39, and is discharged from the drain ports 24, 31.

Next, the configuration of the valve timing adjusting device according to the first embodiment will be described with reference to FIG. FIG. 5 is a cross-sectional view of the valve timing adjusting device according to the first embodiment.

The valve timing adjusting device according to the first embodiment shown in FIG. 5 can lock the rotor 52 at an arbitrary phase. Further, although the valve timing adjusting device is integrally provided with the OCV10, the OCV10 may be provided as a separate body. The OCV 10 shown in FIG. 5 is simply shown.

The valve timing adjusting device includes an OCV 10, a case 51, a rotor 52, a spring 53, a holder 54, and lock pins 55a and 55b.

The case 51 has an annular shape and rotates synchronously with the crankshaft of the engine. The case 51 has a plurality of shoes 51a and sprockets 51b. The shoe 51a is provided so as to project inward in the radial direction from the inner peripheral surface of the case 51. The sprocket 51b is provided along the outer peripheral portion of the case 51 and receives the rotational driving force of the crankshaft.

The rotor 52 is arranged coaxially with respect to the case 51 inside the case 51 so as to be coaxial with the case 51, and rotates integrally with the camshaft for opening and closing the valve in the engine. Further, the rotor 52 has a plurality of vanes 52a. The vane 52a is provided so as to protrude outward in the radial direction from the outer peripheral surface of the rotor 52. Further, the vane 52a is arranged so as to enter the hydraulic chamber formed between the adjacent shoes 51a.

As a result, the hydraulic chamber is divided into an advance hydraulic chamber 61 and a retard hydraulic chamber 62 by a vane 52a, and an advance angle is provided between the inner peripheral surface of the case 51 and the outer peripheral surface of the rotor 52. The hydraulic chamber 61 and the retarded hydraulic chamber 62 are partitioned. The advance angle hydraulic chamber 61 communicates with the advance angle port 22 in the OCV 10. Further, the retard angle hydraulic chamber 62 communicates with the retard angle port 23 in the OCV 10.

That is, when oil is supplied from the OCV 10 to the advance hydraulic chamber 61 or the retard hydraulic chamber 62, the vane 52a rotates relative to the case 51 according to the pressure difference between them. When the oil is supplied to the advance hydraulic chamber 61, the rotor 52 rotates ahead of the phase of the case 51 because the phase shifts in the advance direction. On the other hand, when the oil is supplied to the retard angle hydraulic chamber 62, the rotor 52 rotates later than the phase of the case 51 because the phase shifts in the retard angle direction.

The spring 53, the holder 54, and the lock pins 55a and 55b are provided between the inner peripheral surface of the case 51 and the tip surface of the vane 52a. The lock pin 55a constitutes an advance angle side lock pin, and the lock pin 55b constitutes a retard angle side lock pin.

The spring 53 is provided on the tip surface of the vane 52a via the holder 54. Further, the spring 53 is arranged so that the urging direction is substantially orthogonal to the axial directions of the case 51 and the rotor 52.

The lock pins 55a and 55b are provided so as to sandwich the spring 53 from both sides in the urging direction. Further, the lock pins 55a and 55b are arranged so that their axial directions substantially coincide with the axial directions of the case 51 and the rotor 52.

Specifically, the lock pin 55a is arranged on the advance hydraulic chamber 61 side of the spring 53 and in contact with the advance hydraulic chamber 61. As a result, the lock pin 55a is urged by the spring 53 toward the advance hydraulic chamber 61 side, and is sandwiched between the inner peripheral surface of the case 51 and the tip surface of the vane 52a. Become.

On the other hand, the lock pin 55b is arranged on the retard hydraulic chamber 62 side of the spring 53 and in contact with the retard hydraulic chamber 62. As a result, the lock pin 55b is urged toward the retard angle hydraulic chamber 62 side, and is sandwiched between the inner peripheral surface of the case 51 and the tip surface of the vane 52a.

Next, the operation of the valve timing adjusting device according to the first embodiment will be described with reference to FIGS. 6 and 7. FIG. 6A is a cross-sectional view of the valve timing adjusting device when the rotor returns to the original phase from the retard side. FIG. 6B is a cross-sectional view of the valve timing adjusting device when the rotor returns to the original phase from the advance angle side. FIG. 7A is a cross-sectional view of the valve timing adjusting device in the retarded angle supply state of the OCV. FIG. 7B is a cross-sectional view of the valve timing adjusting device in the advance angle supply state of the OCV. FIG. 7C is a cross-sectional view of the valve timing adjusting device in the final state of the OCV.

However, in FIGS. 6A to 7C, the original phase that is the lock phase of the rotor 52 is described as the intermediate phase between the most advanced phase and the latest retard phase, but the original phase is the most. Any phase between the advance phase and the latest retard phase may be used. At this time, the original phase may be the most advanced phase or the latest retard phase.

As shown in FIGS. 6A and 6B, the rotor 52 in the valve timing adjusting device is used when the OCV 10 shifts to the initial state regardless of whether the current phase is located on the advance side or the retard side. , The phase is designed to return to the original phase.

When the OCV 10 shifts to the initial state, the oil flowing in from the supply port 21 continues to be supplied to both the advance angle port 22 and the retard angle port 23, so that the advance angle hydraulic chamber 61 and the retard angle hydraulic chamber 62 Both hydraulic chambers are filled with oil. As a result, hydraulic pressure acts on the rotor 52 from both the advance hydraulic chamber 61 side and the retard hydraulic chamber 62 side, but as a result, these hydraulic pressures act in opposite directions to cancel each other out. , Will be offset.

Therefore, the force acting on the rotor 52 is an assist torque Ta for urging the rotor 52 in the advance direction and a cam torque Tc which is a reaction force of the cam provided on the cam shaft. Further, since the lock pins 55a and 55b receive the hydraulic pressure from the advance hydraulic chamber 61 and the retard hydraulic chamber 62, respectively, they move against each other against the urging force of the spring 53, and the rotor 52 moves to the case 51. On the other hand, the lock is released. The urging range of the assist torque Ta is a range from the most retarded phase to the original phase.

Therefore, as shown in FIG. 6A, when the phase of the rotor 52 is located on the retard side with respect to the original phase, the rotor 52 has an assist torque Ta in the advance direction and an assist torque Ta in the retard direction. The cam torque Tc is acting. As a result, the valve timing adjusting device can return the rotor 52 to the original phase by setting the value of the assist torque Ta to be larger than the average value of the cam torque Tc.

Further, as shown in FIG. 6B, when the phase of the rotor 52 is located on the advance angle side with respect to the original phase, only the cam torque in the retard direction is acting on the rotor 52. As a result, the valve timing adjusting device can return the rotor 52 to the original phase.

In the valve timing adjusting device in the retard angle supply state shown in FIG. 7A, oil is supplied to the retard angle hydraulic chamber 62. As a result, the lock pin 55b is released from between the inner peripheral surface of the case 51 and the tip surface of the vane 52a against the urging force of the spring 53 by the hydraulic pressure acting from the retard angle hydraulic chamber 62, and is released in the retard angle direction. Move towards. Along with this, when the vane 52a starts to rotate in the retard direction, the lock pin 55a escapes from between the inner peripheral surface of the case 51 and the tip surface of the vane 52a and slides in the advance direction. .. Therefore, the rotor 52 rotates in the retard direction with respect to the case 51.

In the valve timing adjusting device in the advance angle supply state shown in FIG. 7B, oil is supplied to the advance angle hydraulic chamber 61. As a result, the lock pin 55a is released from between the inner peripheral surface of the case 51 and the tip surface of the vane 52a against the urging force of the spring 53 by the hydraulic pressure acting from the advance angle hydraulic chamber 61, and is released in the advance angle direction. Move towards. Along with this, when the vane 52a starts to rotate in the advance direction, the lock pin 55b escapes from between the inner peripheral surface of the case 51 and the tip surface of the vane 52a and slides in the retard direction. .. Therefore, the rotor 52 rotates in the advance angle direction with respect to the case 51.

In the valve timing adjusting device in the final state shown in FIG. 7C, oil is not supplied to both the advance hydraulic chamber 61 and the retard hydraulic chamber 62. As a result, the spring 53 urges the lock pin 55a toward the advance hydraulic chamber 61 side and sandwiches the lock pin 55a between the inner peripheral surface of the case 51 and the tip surface of the vane 52a, while the lock pin 55b is inserted. It is urged toward the retarded hydraulic chamber 62 side and sandwiched between the inner peripheral surface of the case 51 and the tip surface of the vane 52a. Therefore, the rotor 52 is restricted from rotating relative to the case 51, and is locked to the case 51. Note that FIG. 7C shows a state in which the rotor 52 is locked in the original phase.

Therefore, in the valve timing adjusting device according to the first embodiment, in the idling start / stop mode of the engine, immediately before shifting to the idling stop, the phase corresponding to the temperature of the oil at that time is obtained in advance, and then the rotor 52 is used. After rotating to the phase, the OCV 10 can be moved to the final state. As a result, the valve timing adjuster can lock the rotor in a phase corresponding to the temperature of the oil that correlates with the temperature of the combustion chamber in the engine immediately before the idling stop, so that noise is generated when the engine is restarted. It is possible to improve fuel efficiency and reduce exhaust gas while suppressing the occurrence. The idling start / stop mode is a mode in which the vehicle speed is zero and the engine is driven.

Also, when the rotor is placed in a phase different from the original phase in the idle state of the engine, the rotor reaches the original phase in a short period from when the vehicle is keyed off until the engine stops. If the valve timing cannot be restored, the conventional valve timing adjuster will discharge oil from its advance and retard hydraulic chambers at the next key-on to the vehicle, so that the rotor will rotate when the engine is started. It collided with the case and noise was generated.

On the other hand, the valve timing adjusting device according to the first embodiment can shift the OCV 10 to the initial state and return the rotor 52 to the original phase even in the short period described above. After that, when the engine is completely stopped, the oil stored in the advance hydraulic chamber and the retard hydraulic chamber is naturally discharged, so that the rotor 52 is locked in the original phase.

Next, the operation when the valve timing adjusting device according to the first embodiment is used in the idle state of the engine will be described with reference to FIG. FIG. 8A is a diagram showing a state when the vehicle is keyed off. FIG. 8B is a diagram showing a state in which the rotor returns to the original phase. FIG. 8C is a diagram showing a state in which the rotor is locked.

The valve timing adjusting device shown in FIG. 8A is used by rotating the rotor 52 to the advance angle side with respect to the original phase in the idle state of the engine. When the vehicle is keyed off from such a usage state, the energization of the external solenoid for driving the OCV 10 is cut off, so that the external solenoid is in the non-energized state. As a result, the stroke amount of the spool 12 becomes the minimum, and the OCV 10 shifts to the initial state accordingly.

Then, as shown in FIG. 8B, the rotor 52 returns to the original phase in a short period of time from when the vehicle is keyed off until the engine is stopped. Then, as shown in FIG. 8C, when the engine is completely stopped, the oil stored in the advance hydraulic chamber 61 and the retard hydraulic chamber 62 is discharged from the advance hydraulic chamber 61 and the retard hydraulic chamber 62. .. As a result, the rotor 52 is locked in the original phase by the action of the lock pins 55a and 55b.

Therefore, the valve timing adjusting device is used when the rotor 52 is arranged in a phase different from the original phase in the idle state of the engine, and in a short period from when the vehicle is keyed off until the engine is stopped. Regardless of the phase in which the rotor 52 is arranged, the rotor 52 can be returned to the original phase. As a result, the valve timing adjusting device locks the rotor 52 even at the next key-on, so that it is possible to prevent the rotor 52 from colliding with the case 51 when the engine is started. Occurrence can be suppressed.

From the above, the rotor 52 in the valve timing adjusting device according to the first embodiment is attached in the advance direction from the latest retard phase to the original phase located between the latest retard phase and the most advance phase. It is being pushed. Further, the OCV 10 in the valve timing adjusting device according to the first embodiment has a supply port 21 that communicates with an oil supply source, an advance port 22 that communicates with an advance hydraulic chamber 61, and a retard angle that communicates with a retard hydraulic chamber 62. The center bolt 11 having the port 23 and the drain port 24 communicating with the outside of the OCV 10 reciprocates between the initial position and the final position in the center bolt 11, and the supply port 21 advances according to the stroke amount. It is provided with a spool 12 for supplying and discharging oil via a square port 22, a retard port 23, and a drain port 24. Then, the OCV 10 communicates the supply port 21, the advance angle port 22, and the retard angle port 23 when the spool 12 is arranged at the initial position. Further, when the spool 12 is arranged at the final position, the OCV 10 communicates the advance angle port 22 with the outside of the OCV 10 while communicating the retard angle port 23 and the drain port 24.

As a result, the valve timing adjusting device can lock the rotor 52 in a phase corresponding to the temperature of the oil in the idling start / stop mode of the engine. As a result, the valve timing adjusting device can improve fuel efficiency and reduce exhaust gas while suppressing the generation of noise when the engine is restarted.

Embodiment 2.
The valve timing adjusting device according to the second embodiment has the oil supply / discharge relationship in the initial state and the final state set in reverse with respect to the valve timing adjusting device according to the first embodiment.

First, the configuration of the OCV according to the second embodiment will be described with reference to FIG. FIG. 9A is an external view of the OCV. FIG. 9B is a partial vertical sectional view of the OCV. FIG. 9C is a vertical sectional view of the OCV. FIG. 9D is a view when the tip surface of the spool is viewed from the axial direction. FIG. 9E is a view when the stopper surface of the stopper is viewed from the axial direction.

The OCV 10A includes a center bolt 11, a spool 12A, a stopper 13, and a spring 14. The center bolt 11 constitutes the housing of the OCV 10A.

The spool 12A is supported so as to be reciprocally movable in the axial direction of the center bolt 11 inside the partitions 25 to 29 of the center bolt 11 in the radial direction. Further, the spool 12A has a hollow shape, and has a drain port 31, a flow path 32, a lateral groove 39, and partitions 41 to 47. As a result, the OCV 10A supplies oil to the valve timing adjusting device via the supply port 21, the advance angle port 22, the retard angle port 23, and the drain port 24 according to the stroke amount that is the movement amount of the spool 12A. Can be discharged.

The partitions 41 to 47 are formed in an annular shape along the circumferential direction of the outer peripheral surface of the spool 12A, and protrude outward from the outer peripheral surface in the radial direction. That is, the partitions 41 to 47 are supported in the partitions 25 to 29 so as to be reciprocally movable in the axial direction of the center bolt 11. The drain port 31 is open on the lateral side of the spool 12A with respect to the partition 41. Further, the lateral groove 39 is formed so as to pass through the center of the flow path 32 and the partition 47.

The stopper 13 has a lateral groove 13a. The lateral groove 13a is formed so as to pass through the center of the stopper 13. Further, the lateral groove 13a faces the partition 41 in the axial direction of the center bolt 11 and communicates with a gap passage formed between the inner peripheral surface of the center bolt 11 and the outer peripheral surface of the spool 12A.

The spring 14 is provided between the inside of the center bolt 11 on the tip end side and the tip of the flow path 32 in the spool 12A, and urges the spool 12A toward the stopper 13. As a result, in the spool 12A, the partition 41 comes into contact with the stopper 13 from the tip end side of the center bolt 11, so that the spool 12A is restricted from moving to the proximal end side.

At this time, the moving position of the spool 12A when the partition 41 comes into contact with the stopper 13 becomes the initial position, and the stroke amount thereof becomes the minimum. Further, the moving position of the spool 12A when the partition 41 is farthest from the stopper 13 is the final position, and the stroke amount thereof is the maximum. That is, the spool 12A reciprocates between the initial position and the final position.

Further, the base end of the spool 12A is pressed by an external solenoid. As a result, the moving position of the spool 12A is determined by the balance between the urging force of the spring 14 and the pressing force of the external solenoid. In other words, the stroke amount of the spool 12A changes depending on the current value or duty value applied to the external solenoid.

Further, the OCV 10A can shift to five states by changing the stroke amount of the spool 12A. Specifically, the OCV10A can shift to any one of the initial state, the retard angle supply state, the intermediate holding state, the advance angle supply state, and the final state.

Next, the five states of OCV according to the second embodiment will be described with reference to FIG. FIG. 10 is a diagram showing a transition state of the advance port and the retard port with respect to the stroke amount of the spool in the second embodiment.

In the initial state, the advance angle port 22 and the base end side opening of the center bolt 11 communicate with each other, so that the oil stored in the advance angle hydraulic chamber is discharged through the base end side opening, but is delayed. This is a state in which the corner port 23 and the drain ports 24 and 31 communicate with each other to discharge the oil stored in the retarded hydraulic chamber through the drain ports 24 and 31.

In the retarded angle supply state, the advance angle port 22 and the base end side opening of the center bolt 11 communicate with each other, so that the oil stored in the advance angle hydraulic chamber is discharged through the base end side opening. The supply port 21 and the retard angle port 23 communicate with each other, so that the oil flowing into the supply port 21 is supplied to the retard angle hydraulic chamber via the retard angle port 23. That is, the retard angle supply state is a state in which the rotor of the valve timing adjusting device rotates in the retard angle direction.

In the intermediate holding state, the advance angle port 22 is cut off from the supply port 21 and the drain ports 24 and 31, so that the oil pressure in the advance angle hydraulic chamber is maintained as it is, while the retard angle port 23 is the supply port 21. In addition, the flood control in the retard angle hydraulic chamber is maintained as it is by being cut off from the drain ports 24 and 31. That is, the intermediate holding state is a state in which the rotor of the valve timing adjusting device is held in the current phase.

The advance angle supply state means that the supply port 21 and the advance angle port 22 communicate with each other to supply the oil flowing into the supply port 21 to the advance angle hydraulic chamber through the advance angle port 22, while retarding the angle. This is a state in which the oil stored in the retarded hydraulic chamber is discharged through the drain ports 24 and 31 by communicating the port 23 and the drain ports 24 and 31. That is, the advance angle supply state is a state in which the rotor of the valve timing adjusting device rotates in the advance angle direction.

The final state is that the supply port 21 and the advance angle port 22 communicate with each other to supply the oil flowing into the supply port 21 to the advance angle hydraulic chamber via the advance angle port 22, while supplying the oil to the advance angle hydraulic chamber 21. This is a state in which the oil flowing into the supply port 21 is supplied to the retard angle hydraulic chamber via the retard angle port 23 by communicating with the retard angle port 23.

Next, the operation of the OCV according to the second embodiment will be described with reference to FIGS. 11 and 12. FIG. 11A is a diagram showing an initial state of OCV. FIG. 11B is a diagram showing a retarded angle supply state of OCV. FIG. 11C is a diagram showing an intermediate holding state of the OCV. FIG. 12A is a diagram showing an advance angle supply state of OCV. FIG. 12B is a diagram showing the final state of OCV. The arrows shown in FIGS. 11A, 11B, 12A, and 12B indicate the flow of oil.

In the OCV 10A in the initial state shown in FIG. 11A, the partition 26 and the partition 42 are in contact with each other over the entire circumference and seal between them. The partition 27 and the partition 44 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 is not supplied to the advance port 22 by the seal between the partitions 26 and 42. Further, the oil flowing in from the supply port 21 is not supplied to the retard port 23 by the seal between the partitions 27 and 44. Further, the oil stored in the advance angle port 22 passes between the partitions 25 and 41, and then is discharged from the base end side opening of the center bolt 11 through the lateral groove 13a. On the other hand, the oil stored in the retarded port 23 passes between the partitions 28, 46, 47, then flows into the flow path 32 from the lateral groove 39, and is discharged from the drain ports 24, 31.

In the OCV 10A in the retarded angle supply state shown in FIG. 11B, the partition 26 and the partition 42 are in contact with each other over the entire circumference and seal between them. The partition 28 and the partition 46 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil stored in the advance port 22 is discharged to the outside of the OCV 10 from the base end side opening of the center bolt 11 after passing between the partitions 25 and 41. Further, the oil flowing in from the supply port 21 passes between the partitions 27, 43, and 44, and then is supplied to the retarded port 23 by the seal between the partitions 28 and 46. At this time, the oil is not supplied to the advance port 22 by the seal between the partitions 26 and 42.

In the OCV 10A in the intermediate holding state shown in FIG. 11C, the partition 25 and the partition 41 are in contact with each other over the entire circumference and seal between them. The partition 26 and the partition 42 are in contact with each other over the entire circumference and seal between them. The partition 27 and the partition 43 are in contact with each other over the entire circumference and seal between them. The partition 28 and the partition 46 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 is not supplied to the advance port 22 by the seal between the partitions 26 and 42. Further, the oil flowing in from the supply port 21 is not supplied to the retard port 23 by the seal between the partitions 27 and 43. Further, the oil stored in the advance port 22 is not discharged to the outside of the OCV 10A by the seal between the partitions 25 and 41. On the other hand, the oil stored in the retarded port 23 is not discharged from the drain ports 24 and 31 due to the seal between the partitions 28 and 46.

In the OCV 10A in the lead angle supply state shown in FIG. 12A, the partition 25 and the partition 41 are in contact with each other over the entire circumference and seal between them. The partition 27 and the partition 43 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 passes between the partitions 26 and 42, and then is supplied to the advance port 22 by the seal between the partitions 25 and 41. At this time, the oil is not supplied to the retard port 23 by the seal between the partitions 27 and 43. Further, the oil stored in the retard port 23 passes between the partitions 28, 45, 46, then flows into the flow path 32 from the lateral groove 39, and is discharged from the drain ports 24, 31.

In the OCV 10A in the final state shown in FIG. 12B, the partition 25 and the partition 41 are in contact with each other over the entire circumference and seal between them. The partition 28 and the partition 45 are in contact with each other over the entire circumference and seal between them.

Therefore, the oil flowing in from the supply port 21 passes between the partitions 26 and 42, and then is supplied to the advance port 22 by the seal between the partitions 25 and 41. Further, the oil flowing in from the supply port 21 passes between the partitions 27, 42, and 43, and is then supplied to the supply port 21 by the seal between the partitions 28 and 45.

From the above, the rotor 52 in the valve timing adjusting device according to the second embodiment is attached in the advance direction from the latest retard phase to the original phase located between the latest retard phase and the most advance phase. It is being pushed. Further, the OCV 10A in the valve timing adjusting device according to the second embodiment has a supply port 21 that communicates with an oil supply source, an advance port 22 that communicates with an advance hydraulic chamber 61, and a retard angle that communicates with a retard hydraulic chamber 62. The center bolt 11 having the port 23 and the drain port 24 communicating with the outside of the OCV 10A reciprocates between the initial position and the final position in the center bolt 11, and the supply port 21 advances according to the stroke amount. It includes a spool 12A for supplying and draining oil via a square port 22, a retard port 23, and a drain port 24. Then, when the spool 12A is arranged at the initial position, the OCV 10A communicates the advance angle port 22 with the outside of the OCV 10A, while communicating the retard angle port 23 and the drain port 24. Further, the OCV 10A communicates the supply port 21, the advance angle port 22, and the retard angle port 23 when the spool 12A is arranged at the final position.

As a result, the valve timing adjusting device can lock the rotor 52 in a phase corresponding to the temperature of the oil in the idling start / stop mode of the engine. As a result, the valve timing adjusting device can improve fuel efficiency and reduce exhaust gas while suppressing the generation of noise when the engine is restarted.

In the present invention, within the scope of the invention, any combination of embodiments, modification of any component in each embodiment, or omission of any component in each embodiment can be omitted. It is possible.

The valve timing adjusting device according to the present invention is provided with a supply port, an advance angle port, a retard angle port, and a drain port to a center bolt for accommodating the spool so as to be reciprocally movable, and supplies oil through these ports. Since it can be discharged, it is suitable for use in a valve timing adjusting device or the like equipped with an oil control valve.

10,10A oil control valve (OCV), 11 center bolt, 12,12A spool, 13 stopper, 13a lateral groove, 14 spring, 21 supply port, 22 advance port, 23 retard port, 24 drain port, 25-29 partition , 31 drain port, 32 flow path, 33-38 partition, 39 lateral groove, 41-47 partition, 51 case, 51a shoe, 51b sprocket, 52 rotor, 52a vane, 53 spring, 54 holder, 55a, 55b lock pin, 61 Advance hydraulic chamber, 62 retard hydraulic chamber.

The valve timing adjusting device according to the present invention includes a case that rotates synchronously with the crank shaft of the internal combustion engine, a rotor that is arranged coaxially so as to be rotatable relative to the case and opens and closes the valve of the internal combustion engine, and a case. A partition is formed between the rotor and the case and the rotor, and a partition is formed between the case and the rotor, and the partition is formed between the case and the rotor to rotate the rotor relative to the advance direction with the supply of the working fluid. , A retard hydraulic chamber that rotates the rotor relative to the retard direction, an oil control valve that controls the supply and discharge of working fluid to the advance hydraulic chamber and the retard hydraulic chamber, and a radial outside from the outer peripheral surface of the rotor The vane that protrudes toward the surface and separates the advance hydraulic chamber and the retard hydraulic chamber, the spring provided on the tip surface of the vane, and the advance of the spring between the inner peripheral surface of the case and the tip surface of the vane. The retard angle of the spring between the advance lock pin provided on the angular hydraulic chamber side and urged toward the advance hydraulic chamber side by the spring, the inner peripheral surface of the case and the tip surface of the vane. A retard angle side lock pin provided on the hydraulic chamber side and urged toward the retard angle hydraulic chamber side by a spring is provided, and the rotor has a retardation angle phase to the latest retardation angle phase and the most advanced angle phase. The oil control valve is urged in the advance direction to the original phase located between them, and the oil control valve has a supply port that communicates with the supply source of the working fluid, an advance port that communicates with the advance hydraulic chamber, and a retard hydraulic chamber. It reciprocates between the initial position and the final position in the housing and the housing having a retard port that communicates and a drain port that communicates with the outside of the oil control valve, and the supply port and advance angle are adjusted according to the stroke amount. It includes a spool that supplies and discharges working fluid via a port, a retard port, and a drain port, and communicates the supply port with the advance port and the retard port when the spool is placed in the initial position. When the spool is placed at the final position, the advance angle port and the outside of the oil control valve are communicated with each other, while the retard angle port and the drain port are communicated with each other.

The valve timing adjusting device according to the present invention includes a case that rotates synchronously with the crank shaft of the internal combustion engine, a rotor that is arranged coaxially so as to be rotatable relative to the case and opens and closes the valve of the internal combustion engine, and a case. A partition is formed between the rotor and the case and the rotor, and a partition is formed between the case and the rotor, and the partition is formed between the case and the rotor to rotate the rotor relative to the advance direction with the supply of the working fluid. , A retard hydraulic chamber that rotates the rotor relative to the retard direction, an oil control valve that controls the supply and discharge of working fluid to the advance hydraulic chamber and the retard hydraulic chamber, and a radial outside from the outer peripheral surface of the rotor. The vane that protrudes toward the surface and separates the advance hydraulic chamber and the retard hydraulic chamber, the spring provided on the tip surface of the vane, and the advance of the spring between the inner peripheral surface of the case and the tip surface of the vane. The retard angle of the spring between the advance lock pin provided on the angular hydraulic chamber side and urged toward the advance hydraulic chamber side by the spring, the inner peripheral surface of the case and the tip surface of the vane. A retard angle side lock pin provided on the hydraulic chamber side and urged toward the retard angle hydraulic chamber side by a spring is provided, and the rotor has a retardation angle phase to the latest retardation angle phase and the most advanced angle phase. The oil control valve is urged in the advance direction to the original phase located between them, and the oil control valve has a supply port that communicates with the supply source of the working fluid, an advance port that communicates with the advance hydraulic chamber, and a retard hydraulic chamber. It reciprocates between the initial position and the final position in the housing and the housing having a retard port that communicates and a drain port that communicates with the outside of the oil control valve, and the supply port and advance angle are adjusted according to the stroke amount. It is provided with a spool for supplying and discharging the working fluid through a port, a retard port, and a drain port, and when the spool is placed in the initial position, the advance port and the outside of the oil control valve are communicated with each other. On the other hand, the retard angle port and the drain port are communicated with each other, and when the spool is arranged at the final position, the supply port and the advance angle port and the retard angle port are communicated with each other.

Claims (3)

A case that rotates synchronously with the crankshaft of an internal combustion engine,
A rotor that is coaxially arranged so as to rotate relative to the case and opens and closes a valve of the internal combustion engine.
An advance hydraulic chamber, which is partitioned between the case and the rotor and rotates the rotor relative to the advance direction as the working fluid is supplied.
A retarded hydraulic chamber, which is partitioned between the case and the rotor and rotates the rotor relative to the retard direction as the working fluid is supplied.
An oil control valve for controlling the supply and discharge of the working fluid is provided in the advance angle hydraulic chamber and the retard angle hydraulic chamber.
The rotor
It is urged in the advance direction from the latest retard phase to the original phase located between the latest retard phase and the most advanced phase.
The oil control valve
It has a supply port that communicates with the supply source of the working fluid, an advance port that communicates with the advance hydraulic chamber, a retard port that communicates with the retard hydraulic chamber, and a drain port that communicates with the outside of the oil control valve. With the housing
It reciprocates between the initial position and the final position in the housing, and supplies the working fluid via the supply port, the advance angle port, the retard angle port, and the drain port according to the stroke amount. Equipped with a spool for discharging
When the spool is placed in the initial position, the supply port communicates with the advance port and the retard port.
When the spool is arranged at the final position, the valve timing adjustment is characterized in that the advance port and the outside of the oil control valve communicate with each other, while the retard port and the drain port communicate with each other. apparatus. A case that rotates synchronously with the crankshaft of an internal combustion engine,
A rotor that is coaxially arranged so as to rotate relative to the case and opens and closes a valve of the internal combustion engine.
An advance hydraulic chamber, which is partitioned between the case and the rotor and rotates the rotor relative to the advance direction as the working fluid is supplied.
A retarded hydraulic chamber, which is partitioned between the case and the rotor and rotates the rotor relative to the retard direction as the working fluid is supplied.
An oil control valve for controlling the supply and discharge of the working fluid is provided in the advance angle hydraulic chamber and the retard angle hydraulic chamber.
The rotor
It is urged in the advance direction from the latest retard phase to the original phase located between the latest retard phase and the most advanced phase.
The oil control valve
It has a supply port that communicates with the supply source of the working fluid, an advance port that communicates with the advance hydraulic chamber, a retard port that communicates with the retard hydraulic chamber, and a drain port that communicates with the outside of the oil control valve. With the housing
It reciprocates between the initial position and the final position in the housing, and supplies the working fluid via the supply port, the advance angle port, the retard angle port, and the drain port according to the stroke amount. Equipped with a spool for discharging
When the spool is placed in the initial position, the advance port and the outside of the oil control valve are communicated with each other, while the retard port and the drain port are communicated with each other.
A valve timing adjusting device that communicates the supply port with the advance port and the retard port when the spool is arranged at the final position. A vane that protrudes radially outward from the outer peripheral surface of the rotor and separates the advance hydraulic chamber from the retard hydraulic chamber.
A spring provided on the tip surface of the vane and
An advance provided between the inner peripheral surface of the case and the tip surface of the vane and on the advance hydraulic chamber side of the spring, and urged by the spring toward the advance hydraulic chamber side. With the corner lock pin,
A delay that is provided between the inner peripheral surface of the case and the tip surface of the vane and on the retard hydraulic chamber side of the spring, and is urged toward the retard hydraulic chamber side by the spring. The valve timing adjusting device according to claim 1 or 2, further comprising a square lock pin.

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