JP2012219767A - Valve timing adjustment device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a valve timing adjustment device that prevents an unlocking failure of a vane rotor due to an operation failure of a stopper pin at the start of an engine.SOLUTION: The valve timing adjustment device restrains a housing and the vane rotor by engaging the stopper pin stored in a storage hole of the vane rotor with an engagement hole of the housing at engine start-up. After the engine start-up, an ECU inputs to a hydraulic control valve, a holding duty ratio at which hydraulic fluids of the same pressure are supplied to an advance angle chamber and a delay angle chamber (S106). It is determined whether the time needed for 720° rotation of a crankshaft has passed after the time when the holding duty ratio is input (S107). In the time, the direction of combined torque of advance angle hydraulic torque, delay angle hydraulic torque, and cam torque acting on the vane rotor becomes a delay angle direction, so that the stopper pin and engagement hole do not come in contact with each other.

Description

  The present invention relates to a valve timing adjusting device.

  Conventionally, a driving force is transmitted from a crankshaft as a drive shaft of an engine to a camshaft as a driven shaft that opens and closes an intake valve and an exhaust valve via a chain as a power transmission member, and at least one of the intake valve and the exhaust valve is transmitted. A valve timing adjusting device for adjusting the opening / closing timing is known. In the valve timing adjusting device, cam torque that swings the vane of the vane rotor connected to the camshaft in the positive direction (retard direction) and the negative direction (advance direction) alternately acts. For this reason, the valve timing adjusting device includes a vane and a housing that are oscillated in a forward / reverse direction by a cam torque at a low oil pressure such as when starting an engine by fitting a stopper pin provided on the vane into a fitting hole of the housing. Prevents the sound of hitting.

  In the valve timing adjusting device, the lock of the vane rotor by the stopper pin is released after a certain time has elapsed since the low oil pressure at the time of engine start or the like, and the opening / closing timing of at least one of the intake valve and the exhaust valve is adjusted. When releasing the lock of the vane rotor by the stopper pin, the stopper pin is released from fitting by the hydraulic pressure adjusted by the hydraulic control valve acting on the stopper pin. At this time, the lock of the vane rotor may not be released because the stopper pin is not released due to an abnormality of the valve timing adjusting device. Patent Document 1 describes a variable valve timing control device that removes foreign matter caught by a hydraulic control valve by reciprocating a valve body of the hydraulic control valve to eliminate an abnormality of the hydraulic control valve.

JP 2001-152888 A

  However, the variable valve timing control device described in Patent Document 1 can solve the abnormality in the hydraulic control valve, but cannot solve the abnormality in the valve timing adjusting device due to the malfunction of the stopper pin.

  An object of the present invention is to provide a valve timing adjusting device that prevents the occurrence of unlocking failure of a vane rotor due to malfunction of a stopper pin during engine start.

  According to the first aspect of the present invention, the valve timing adjusting device that adjusts the opening / closing timing of at least one of the intake valve and the exhaust valve of the internal combustion engine includes a housing and a vane rotor. The housing rotates together with either the drive shaft of the internal combustion engine or the driven shaft that opens and closes at least one of the intake valve and the exhaust valve. The vane rotor has a vane that partitions the interior of the housing into a retard chamber and an advance chamber, and can rotate relative to the housing. The hydraulic oil is supplied to the retard chamber and the advance chamber inside the housing, thereby changing the phase of the vane rotor. The hydraulic oil is generated in the pressure generating means. The hydraulic pressure generated by the pressure generating means is controlled by the control means. The restricting member that restrains the relative rotation of the vane rotor with respect to the housing is slidably accommodated in an accommodation hole formed in the vane rotor, and is fitted into a fitting hole formed in one inner wall in the rotation axis direction of the housing. The rotation angle of the driven shaft is detected by the driven shaft angle detecting means.

  According to a first aspect of the present invention, there is provided a valve timing adjusting device including first determination means for determining whether or not a predetermined time has elapsed from a first time which is a time when the control means inputs the holding duty ratio to the pressure generation means. Here, the holding duty ratio is a duty ratio for operating the pressure generating means so that the pressure of the hydraulic oil in the advance chamber and the pressure of the hydraulic oil in the retard chamber are the same. When the valve timing adjustment device determines that the predetermined time has elapsed from the first time by the first determination means, the control means sets the pressure of the hydraulic oil at which the vane rotor reaches the target phase to at least one of the advance chamber and the retard chamber. The duty ratio to be supplied to is input to the pressure generating means.

  In the valve timing adjusting device, when releasing the restraint of the relative rotation of the vane rotor with respect to the housing, hydraulic oil having the same pressure is supplied to the advance chamber and the retard chamber formed in the housing. Further, the control means holds the holding duty ratio for the pressure generating means for a predetermined time. During the predetermined time, the direction of the cam torque acting on the vane rotor periodically changes in the positive direction, which is the retard direction, or in the negative direction, which is the advance direction. At this time, an advance hydraulic torque acting by the hydraulic pressure of the advance chamber and a retard hydraulic torque acting by the hydraulic pressure of the retard chamber act on the vane rotor. That is, three torques of advance hydraulic torque, retard hydraulic torque, and cam torque act on the vane rotor. When the synthesis direction of the three torques is the positive direction, the regulating member accommodated in the accommodation hole of the vane rotor is not in contact with the inner wall surface of the fitting hole, so that the fitting is easily released. Therefore, it is possible to prevent the occurrence of unlocking failure of the vane rotor due to the malfunction of the restricting member.

  According to the second aspect of the present invention, the predetermined time in the valve timing adjusting device is that the rotation angle of the drive shaft is 720 degrees from the first time when the control means inputs the holding duty ratio to the pressure generating means. It is longer than the time until When the drive shaft rotates twice, that is, 720 degrees, the driven shaft rotates once, that is, 360 degrees. While the driven shaft makes one rotation, there is a time during which the combined torque of the advance hydraulic torque, the retard hydraulic torque, and the cam torque is in the positive direction. Therefore, in the valve timing adjusting device, the vane rotor can be unlocked by maintaining the holding duty ratio from the time when the holding duty ratio is first input until the time when the drive shaft rotates 720 degrees.

  According to the third aspect of the present invention, the valve timing adjusting device uses the pressure correction means for adjusting the advance angle correction holding duty ratio in which the control means increases the pressure of the hydraulic oil in the advance chamber as compared with the pressure of the hydraulic oil in the retard chamber. A second determination unit that determines whether or not a predetermined time has elapsed from a second time that is a time input to the time, and when the second determination unit determines that the elapsed time from the second time is less than the predetermined time, Third determination means is provided for determining whether the phase of the vane rotor has changed from the most retarded position or the most advanced position.

In the valve timing adjusting apparatus according to claim 3, when the third determining means determines that the phase of the vane rotor has changed from the most retarded angle position or the most advanced angle position, the control means is a hydraulic pressure at which the vane rotor becomes the target phase. Is input to the pressure generating means.
In the valve timing adjusting device, when the restriction of the relative rotation of the vane rotor with respect to the housing is released, the hydraulic oil is supplied to the advance chamber and the retard chamber formed in the housing. At this time, the control means inputs an advance correction holding duty ratio for supplying hydraulic oil to the pressure generating means so that the advance hydraulic pressure is higher than the retard hydraulic pressure. Thereby, the restricting member moves in the advance direction as compared with the case where the above-described holding duty ratio is input. Further, when the second determination means determines that the predetermined time has not elapsed since the second time, the third determination means determines the phase of the vane rotor. When the third determining means determines that the phase of the vane rotor has changed from the most retarded position or the most advanced angle position, the control means assumes that the vane rotor is unlocked, and the vane rotor is advanced to the target phase. Retard. Thereby, the valve timing adjusting device can advance or retard the vane rotor before the predetermined time elapses.
A valve timing adjusting device according to a fourth aspect is the same as the valve timing device according to the second aspect.

According to the fifth aspect of the present invention, the valve timing adjusting device includes the fourth determining means for determining whether or not the acting direction of the cam torque is the advance direction from the angle of the driven shaft detected by the driven shaft angle detecting means. I have.
When the control means of the valve timing adjusting device determines that the cam torque action direction is the advance direction by the fourth determination means, the control means determines that the retard pressure is higher in the retard chamber than in the advance chamber. The corrected holding duty ratio is input to the pressure generating means. Further, when the fourth determining means determines that the cam torque acting direction is the retarding direction or the cam torque is not acting, the control means maintains the hydraulic pressure in the advance chamber and the retarded chamber at the same pressure. The duty ratio is input to the pressure generating means.

  In the valve timing adjusting apparatus according to the fifth aspect, the duty ratio input to the pressure generating means is changed according to the direction of the cam torque. When determining that the acting direction of the cam torque is the advance direction, the control means inputs the retard correction holding duty ratio to the pressure generating means. When the acting direction of the cam torque is the advance direction, a torque that changes the phase in the advance direction acts on the vane rotor. At this time, the control means inputs the retardation correction holding duty ratio to the pressure generating means. As a result, the hydraulic pressure in the retarded angle chamber becomes higher than the hydraulic pressure in the advanced angle chamber, so that the vane rotor remains in the vicinity of the most retarded angle position. Thereby, even if the fitting of the regulating member is released, the vane rotor does not advance. Therefore, unexpected movement of the vane rotor in a state where the lock of the vane rotor is released can be prevented, and generation of noise due to rotation of the vane rotor can be prevented.

According to the sixth aspect of the present invention, the valve timing adjusting device sets the predetermined time from the third time, which is the time when the holding duty ratio or the retardation correction holding duty ratio is first input to the pressure generating means by the control means. 5th determination means which determines whether it passed has been provided.
When the fifth determination means determines that a predetermined time has elapsed from the third time, the control means sets a duty ratio for supplying the hydraulic oil pressure at which the vane rotor reaches the target phase to at least one of the advance chamber and the retard chamber. Input to the pressure generator. Accordingly, the lock of the vane rotor can be released at the timing when the direction of the resultant force of the cam torque, the advance hydraulic torque, and the retard hydraulic torque becomes positive.
A valve timing adjusting device according to a seventh aspect is the same as the valve timing device according to the second and fourth aspects.

According to the invention described in claim 8, the valve timing adjusting device detects the rotation angle of the drive shaft, and determines whether or not the rotational speed of the internal combustion engine detected by the drive shaft angle detection means is low. The direction of cam torque acting on the driven shaft by opening / closing at least one of the intake valve and the exhaust valve is the advance direction based on the angle of the driven shaft detected by the sixth determining means and the driven shaft angle detecting means. A seventh determination means for determining whether or not.
When the sixth determining means determines that the rotational speed of the internal combustion engine is low and the seventh determining means determines that the direction of cam torque action is the direction of the advance chamber, the control means determines the hydraulic pressure in the advance chamber. The retard correction holding duty ratio at which the hydraulic pressure in the retard chamber becomes higher than that is input to the pressure generating means. On the other hand, when it is determined by the sixth determining means that the rotational speed of the internal combustion engine is low, and the seventh determining means determines that the cam torque is acting in the retarded direction or the cam torque is not acting, The control means inputs a holding duty ratio for making the hydraulic pressure in the advance chamber and the hydraulic pressure in the retard chamber equal to the pressure generating means.

  In the valve timing adjusting apparatus according to the eighth aspect, the unlocking procedure of the vane rotor is properly used based on the rotational speed of the internal combustion engine detected by the drive shaft angle detecting means. When the rotational speed of the internal combustion engine is low, either one of the above-mentioned retard correction holding duty ratio or holding duty ratio is input to the pressure generating means according to the direction of cam torque action. Thereby, generation | occurrence | production of the noise by rotation of a vane rotor within predetermined time is prevented. On the other hand, when the rotational speed of the internal combustion engine is high, the aforementioned advance angle correction holding duty ratio is input to the pressure generating means. Thereby, the advance angle of the vane rotor is started before the predetermined time elapses. That is, in the valve timing adjusting apparatus according to the eighth aspect of the invention, the vane rotor is unlocked with an emphasis on quietness when the rotational speed of the internal combustion engine is low, and the vane rotor with an emphasis on responsiveness in the phase change of the vane at high speed. Unlock.

In the valve timing adjusting apparatus according to claim 9, whether or not a predetermined time has elapsed from a fourth time, which is a time at which the holding duty ratio or the retardation correction holding duty ratio is first input to the pressure generating means by the control means. Eighth determining means for determining whether or not. When it is determined by the eighth determination means that a predetermined time has elapsed from the fourth time, the control means sets a duty ratio for supplying the hydraulic oil pressure at which the vane rotor reaches the target phase to at least one of the advance chamber and the retard chamber. Input to the pressure generator.
In the valve timing adjusting apparatus according to claim 10, when the sixth determination means determines that the rotational speed of the internal combustion engine is high, the control means has a higher hydraulic pressure in the advance chamber than in the retard chamber. The advance angle correction holding duty ratio is input to the pressure generating means.

In the valve timing adjusting apparatus according to claim 11, the controller determines whether or not a predetermined time has elapsed from a fifth time which is a time when the advance correction correction holding duty ratio is first input to the pressure generating means. Nine determination means are provided. When it is determined by the ninth determining means that a predetermined time has elapsed from the fifth time, the control means sets a duty ratio for supplying the hydraulic oil pressure at which the vane rotor reaches the target phase to at least one of the advance chamber and the retard chamber. Input to the pressure generator.
In the valve timing adjusting device according to claim 12, when the ninth determination means determines that the elapsed time from the fifth time is less than the predetermined time, the phase of the vane rotor changes from the most retarded position or the most advanced position. A tenth determination means for determining whether or not When the tenth determining means determines that the phase of the vane rotor has changed from the most retarded position or the most advanced position, the control means determines the hydraulic pressure at which the vane rotor reaches the target phase as at least one of the advance chamber and the retard chamber. The duty ratio to be supplied to is input to the pressure generating means.
A valve timing adjusting device according to a thirteenth aspect is the same as the valve timing device according to the second, fourth and seventh aspects.

According to the fourteenth aspect of the present invention, the control means is configured such that the pressure of the hydraulic fluid generated by the pressure generating means from the input time when the control means inputs a duty ratio for generating the predetermined pressure value to the pressure generating means is the predetermined pressure. The duty ratio is input retroactively from the time when the pressure of the hydraulic oil generated by the pressure generating means is controlled to a predetermined pressure value until the time when the value is reached.
In the pressure generating means, when a duty ratio for generating a predetermined pressure is input from the control means, it takes time to generate the predetermined pressure. Therefore, the control means calculates in advance the time from the input time when the predetermined duty ratio is input to the pressure generating means to the pressure generation time when the predetermined pressure is generated in the pressure generating means. The control means inputs the predetermined duty ratio retroactively from the time when the duty ratio for generating the predetermined pressure is input. As a result, the vane rotor can be unlocked with certainty because there is no difference between the time when the cam torque is applied in the positive direction and the time when the pressure generating means generates the predetermined pressure.

1 is a schematic diagram of an internal combustion engine using a valve timing adjustment device according to a first embodiment of the present invention. It is sectional drawing of the valve timing adjustment apparatus by 1st Embodiment of this invention. It is sectional drawing of the III-III line of FIG. It is a flowchart of the procedure which performs lock release of the vane rotor using the valve timing adjustment apparatus by 1st Embodiment of this invention. (A) The figure which shows the relationship between engine speed and oil temperature in the valve timing adjustment apparatus by 1st Embodiment of this invention, (b) The figure which shows the relationship between a vane, a stopper pin, and a fitting hole. It is a figure explaining the valve timing adjustment device by a 1st embodiment of the present invention, (a) time change of cam torque, (b) time change of duty ratio, (c) time change of hydraulic torque, (d) stopper (E) Time variation of the phase of the vane rotor. 5A is a diagram showing a relationship between a vane, a stopper pin, and a fitting hole in the valve timing adjusting device according to the first embodiment of the present invention, and FIG. It is a flowchart of the procedure which performs the lock release of the vane rotor using the valve timing adjustment apparatus by 2nd Embodiment of this invention. It is a figure explaining the valve timing adjustment apparatus by 2nd Embodiment of this invention, Comprising: (a) Time change of cam torque, (b) Time change of duty ratio, (c) Time change of hydraulic torque, (d) Stopper (E) Time variation of the phase of the vane rotor. It is a flowchart of the procedure which performs the lock release of the vane rotor using the valve timing adjustment apparatus by 3rd Embodiment of this invention. It is a figure explaining the valve timing adjustment apparatus by 3rd Embodiment of this invention, Comprising: (a) Time change of cam torque, (b) Time change of duty ratio, (c) Time change of hydraulic torque, (d) Stopper (E) Time variation of the phase of the vane rotor. It is a flowchart of the procedure which performs the lock release of the vane rotor using the valve timing adjustment apparatus by 4th Embodiment of this invention. It is a figure which shows the relationship between the engine speed and oil temperature in the valve timing adjustment apparatus by 4th Embodiment of this invention.

Hereinafter, a valve timing adjusting device according to an embodiment of the present invention will be described with reference to the drawings.
(First embodiment)
A valve timing adjusting apparatus according to a first embodiment of the present invention is shown in FIGS. The valve timing adjusting device of this embodiment is a hydraulic control type that uses hydraulic oil as a hydraulic fluid.
In the driving force transmission system provided with the valve timing adjusting device of the first embodiment, as shown in FIG. 1, the gear 3 fixed to the crankshaft 2 as the “driving shaft” of the engine 1 and the “driven shaft” A chain 7 is wound around gears 6 and 191 fixed to the camshafts 4 and 5, and a driving force is transmitted from the crankshaft 2 to the camshafts 4 and 5. One camshaft 4 opens and closes an intake valve 8 via a cam mechanism, and the other camshaft 5 opens and closes an exhaust valve 9 via a cam mechanism. The valve timing adjusting device 10 of the first embodiment adjusts the opening / closing timing of the intake valve 8 by connecting the gear 191 to the chain 7 and the vane rotor to the camshaft 4. A cam angle sensor 4 a that detects the rotation angle of the cam shaft 4 is attached to the cam shaft 4. A crank angle sensor 2 a that detects the rotation angle of the crankshaft 2 is attached to the crankshaft 2.

As shown in FIGS. 2 and 3, the valve timing adjustment device 10 includes a housing 11, a vane rotor 20, a stopper pin 30 as a “regulating member”, and the like.
The housing 11 includes an annular peripheral wall 12 and a Shu housing 17 formed integrally from Shu 13, 14, 15, and 16 as partition members, a front plate 18, a sprocket 19 and the like. Shu 13, 14, 15, 16 formed in a substantially trapezoidal shape extends radially inward from the peripheral wall 12, and is provided at substantially equal intervals in the peripheral direction of the peripheral wall 12. A substantially fan-shaped pressure chamber 50 is formed in a gap between the adjacent shoes in the circumferential direction.

The sprocket 19 includes a gear 191 on the radially outer side, and is provided on one side of the peripheral wall 12 in the rotation axis direction. The sprocket 19 has an axial hole 192 through which the camshaft 4 is passed in the axial direction.
The front plate 18 is formed in a substantially disk shape and is provided on the other side of the peripheral wall 12 in the rotation axis direction. The front plate 18 has a circular hole 181 that communicates with the center of the disk in the thickness direction.
The shoe housing 17, the front plate 18 and the sprocket 19 are coaxially fixed by bolts 111.

The vane rotor 20 is provided substantially coaxially with the housing 11 and is accommodated inside the housing 11 so as to be relatively rotatable. The vane rotor 20 includes a substantially cylindrical rotor 21 and four vanes 22, 23, 24, and 25 that protrude from the rotor 21 in a radially outward direction.
The vane rotor 20 and the camshaft 4 are fixed by bolts 26. The vane rotor 20 and the camshaft 4 are positioned in the circumferential direction by a knock pin 27. Thereby, the vane rotor 20 rotates with the camshaft 4.
Each vane 22, 23, 24, 25 partitions each pressure chamber 50 into retard chambers 51, 52, 53, 54 and advance chambers 55, 56, 57, 58, respectively.

  The retard passages 61 and 62 for supplying hydraulic pressure to the retard chambers 51, 52, 53 and 54 are formed in the rotor 21 of the vane rotor 20. The advance passages 63 and 64 for supplying hydraulic pressure to the advance chambers 55, 56, 57 and 58 are formed in the outer wall of the rotor 21 on the sprocket 19 side. The retard passages 61 and 62 and the advance passages 63 and 64 communicate with a retard passage 65 and an advance passage 66 formed in the camshaft 4, respectively.

  The seal members 28 and 29 are made of, for example, resin, and are fitted to the radially outer walls of the vanes 22, 23, 24, and 25 and the radially inner walls of the shoes 13, 14, 15, and 16. ing. The sealing member 28 fitted to the outer radial wall of each vane 22, 23, 24, 25 is pressed against the peripheral wall 12 by the elastic force of the leaf spring 281. The seal member 29 fitted to the inner wall in the radially inner direction of each of the shoes 13, 14, 15, 16 is pressed against the rotor 21 by the elastic force of the leaf spring 291. For this reason, the seal members 28 and 29 suppress the leakage of hydraulic oil between the retard chambers 51, 52, 53, 54 and the advance chambers 55, 56, 57, 58.

The stopper pin 30 is formed in a cylindrical shape with a bottom and is accommodated in an accommodation hole 221 that communicates with the vane 22 in the rotation axis direction so as to be reciprocally movable in the axial direction.
As shown in FIG. 3, the sprocket 19 is formed with a fitting hole 31 at a position corresponding to the stopper pin 30 in a state where the vane rotor 20 is phase-controlled at the most retarded position. A bush 32 is provided in the fitting hole 31. The stopper pin 30 has a fitting portion 33 that fits inside the diameter of the bush 32 at one end.
A concave portion 34 that is recessed toward the fitting hole 31 is provided at the other end of the stopper pin 30. The recess 34 accommodates a coil spring 35 as an urging member. The coil spring 35 is a compression coil spring having one end abutting against the inner wall of the recess 34 and the other end abutting against the inner wall of the front plate 18, and biases the stopper pin 30 toward the sprocket 19.

Next, the operation of the valve timing adjusting device 10 will be described.
<When starting the engine>
When the engine 1 is stopped, the stopper pin 30 is fitted in the bush 32 of the fitting hole 31 as shown in FIG. In the state immediately after starting the engine 1, the hydraulic oil is not sufficiently supplied from the hydraulic pump 90 to the retard chambers 51, 52, 53, 54 and the advance chambers 55, 56, 57, 588. For this reason, the stopper pin 30 is maintained in a state of being fitted to the bush 32, and the camshaft 4 is held at the most retarded position with respect to the crankshaft 2.

<After starting the engine>
After the engine is started, the vane rotor 20 is unlocked according to the procedure shown in FIG.
In the first step (hereinafter, “step” is omitted, and is simply indicated by symbol S) 101, the operating condition of the vehicle on which the valve timing adjusting device 10 is mounted is detected. Specifically, the rotational speed of the engine 1, the magnitude of the torque output from the engine 1, the water temperature of a radiator that cools the engine 1, and the like. These operating conditions are detected by various sensors and input to an electronic control unit (hereinafter referred to as “ECU”) 91. The ECU 91 corresponds to “control means” and “first determination means” recited in the claims.

Next, in S102, the ECU 91 calculates a target phase of the vane rotor 20. At this time, the ECU 901 calculates the optimum phase of the vane rotor 20 after engine startup as the target phase based on the operating condition detected in S101.
Next, in S103, in order to realize the target phase of the vane rotor 20 calculated in S102, a target duty ratio input to the hydraulic control valve 92 as “pressure generating means” is calculated.

  Next, in S <b> 104, it is determined whether or not the stopper pin 30 is fitted to the bush 32. When the stopper pin 30 is fitted to the bush 32, the vane rotor 20 is positioned at the most retarded angle with respect to the housing 11. In S104, the relative phase of the vane rotor 20 with respect to the housing 11 is detected by the cam angle sensor 4a installed on the camshaft 4. Thereby, it can be determined whether or not the stopper pin 30 is fitted to the bush 32. When it determines with the stopper pin 30 fitting to the bush 32, it transfers to S105. If it is determined that the stopper pin 30 is not fitted to the bush 32, the process proceeds to S108.

Next, in S105, it is determined whether a condition for unlocking the vane rotor 20 is satisfied. Here, the conditions for releasing the lock of the vane rotor 20 will be described with reference to FIG.
FIG. 5A shows a region for controlling the unlocking of the vane rotor 20 derived from the relationship between the rotational speed of the engine 1 and the oil temperature of the hydraulic control valve 92 (hereinafter referred to as “unlocking control execution region”). FIG. 5B shows the relationship of forces acting on the vane rotor 20 that houses the stopper pins 30. As shown in FIG. 5 (b), the vane rotor 20 has a retarded hydraulic pressure generated by the cam torque Tc generated by opening / closing of the intake valve 8 and the pressure of hydraulic oil supplied to the retarded chambers 51, 52, 53, 54. The torque Trtd and the advance hydraulic torque Tadv generated by the pressure of the hydraulic oil supplied to the advance chambers 55, 56, 57, and 58 act. At this time, the retarded hydraulic torque Trtd acts in the retarded direction, that is, in the left direction in FIG. The advance hydraulic torque Tadv acts in the advance direction, that is, in the right direction in FIG. Further, the cam torque Tc acts in either the advance direction or the retard direction depending on the operating state of the intake valve 8.

When the vane rotor 20 is unlocked, the hydraulic oil is supplied to the advance chambers 55, 56, 57, 58. At this time, if the rotational speed of the engine 1 is high, the driving force of the pump 90 that discharges the hydraulic oil to the hydraulic control valve 92 increases, so the pressure of the hydraulic oil supplied to the advance chambers 55, 56, 57, 58 is Get higher. This increases the advance hydraulic torque Tadv. When the advance hydraulic torque Tadv increases, the side wall 331 of the stopper pin 30 comes into contact with the inner wall surface 321 of the bush 32, so that the fitting between the stopper pin 30 and the bush 32 is difficult to release. That is, it becomes difficult to unlock the vane rotor 20. Moreover, since the viscosity of hydraulic fluid will become high when the oil temperature which is the temperature of hydraulic fluid is low, hydraulic pressure becomes high. This also increases the advance hydraulic torque Tadv, making it difficult to unlock the vane rotor 20. Therefore, there is a region where it is difficult to unlock the vane rotor 20 in a region where the rotational speed of the engine 1 is high or a region where the oil temperature is low. Therefore, as shown in FIG. 5A, the lock release control execution region is set as a region where it is difficult to unlock the vane rotor 20 in the relationship between the rotational speed of the engine 1 and the oil temperature of the hydraulic control valve 92.
In S105, when the relationship between the rotation speed of the engine 1 and the oil temperature of the hydraulic oil in the hydraulic pump 90 is in the lock release control execution region, the process proceeds to S106. When the relationship between the rotational speed of the engine 1 and the oil temperature of the hydraulic oil in the hydraulic pump 90 is not in the lock release control execution region, the process proceeds to S108.

  Next, in S <b> 106, the holding duty ratio D <b> 1 is input to the hydraulic control valve 92. As shown in FIG. 6C, the holding duty ratio D1 is a duty that is input to the hydraulic control valve 92 so that the advance hydraulic torque Tadv and the retard hydraulic torque Trtd are the same at a constant value larger than zero. Is the ratio. The ECU 91 inputs the holding duty ratio D1 to the hydraulic control valve 92 at time t1 as “first time”. As a result, the hydraulic control valve 92 supplies hydraulic oil, and the advance hydraulic torque Tadv and the retard hydraulic torque Trtd become torques of the same magnitude greater than 0 at time t2. At this time, the ECU 91 calculates the advance hydraulic torque Tadv and the retard hydraulic torque Trtd by calculating the hydraulic pressure from the rotational speed of the engine 1 and the oil temperature of the hydraulic oil. Further, the ECU 91 may store a value learned when holding the phase of the vane rotor 20 at the previous valve timing adjustment as the holding duty ratio D1.

  Next, in S107, it is determined whether or not a predetermined time has elapsed from time t1 when the holding duty ratio D1 is input to the hydraulic control valve 92. Here, as the predetermined time, as shown in FIG. 6A, two rotations of the crankshaft 2, that is, 720 degrees correspond to one rotation of the camshaft 4, that is, 360 degrees, so the crankshaft 2 rotates 720 degrees. More than the time required to do. When it is determined that the predetermined time has elapsed from time t1, the process proceeds to S108. When it is determined that the predetermined time has not elapsed since time t1, the process returns to S106 and the holding duty ratio D1 is maintained.

  Next, in S108, the target duty ratio is input to the hydraulic control valve 92. Specifically, as shown in FIG. 6B, the ECU 91 inputs the target duty ratio to the hydraulic control valve 92 at time t3. As a result, the advance hydraulic torque Tadv increases and the retard hydraulic torque Trtd decreases at time t4. In the valve timing adjusting device 10, the stopper pin 30 is disengaged at time t5 as shown in FIG. 6 (d) by the hydraulic pressure supplied to the fitting hole 31 before time t3. Since the fitting of the stopper pin 30 is released at time t4, the vane rotor 20 advances as shown in FIG. Thereby, the vane rotor 20 and the housing 11 can be rotated relative to each other. Thereafter, the phase difference of the camshaft 4 with respect to the crankshaft 2 can be adjusted by controlling the hydraulic pressure of the retarding chambers 51, 52, 53, 54 and the advance chambers 55, 56, 57, 58.

<Advance angle operation>
When the valve timing adjusting device 10 is advanced, the ECU 91 controls the drive current supplied to the hydraulic control valve 92. The hydraulic control valve 92 connects the hydraulic pump 90 and the advance passage 93 and connects the retard passage 94 and the oil pan 95. The hydraulic oil discharged from the hydraulic pump 90 is supplied to the advance chambers 55, 56, 57, 58 via the advance passages 93, 66, 63, 64. On the other hand, the hydraulic oil in the retard chambers 51, 52, 53, 54 is discharged to the oil pan 95 via the retard passages 61, 62, 65, 94. The hydraulic pressure in the advance chambers 55, 56, 57, 58 acts on the vanes 22, 23, 24, 25, and generates torque that urges the vane rotor 20 in the advance direction. Thereby, the vane rotor 20 rotates in the advance direction with respect to the housing 11.

<At retarded angle operation>
When the valve timing adjusting device 10 is retarded, the ECU 91 controls the drive current supplied to the hydraulic control valve 92. The hydraulic control valve 92 connects the hydraulic pump 90 and the retard passage 94, and connects the advance passage 93 and the oil pan 95. The hydraulic oil discharged from the hydraulic pump 90 is supplied to the retard chambers 51, 52, 53, 54 via the retard passages 94, 65, 61, 62. On the other hand, the hydraulic oil in the advance chambers 55, 56, 57 and 58 is discharged to the oil pan 95 via the advance passages 63, 64, 66 and 93. The hydraulic pressure in the retard chambers 51, 52, 53, 54 acts on the vanes 22, 23, 24, 25, and generates torque that biases the vane rotor 20 in the retard direction. As a result, the vane rotor 20 rotates in the retard direction with respect to the housing 11.

<Intermediate holding operation>
When the vane rotor 20 reaches the target phase, the ECU 91 controls the duty ratio of the drive current supplied to the hydraulic control valve 92. The hydraulic control valve 92 cuts off the connection between the hydraulic pump 90 and the retard passage 94 and the advance passage 93, and oil is supplied from the retard chambers 51, 52, 53, 54 and the advance chambers 55, 56, 57, 58. The hydraulic oil is restricted from being discharged to the pan 95. For this reason, the vane rotor 20 is held at the target phase.
Note that the hydraulic pressure supplied from the hydraulic pump 90 to the retard side pressure chamber 37 and the advance side pressure chamber 38 of the valve timing adjusting device 10 is released when the advance angle operation, the retard angle operation, or the intermediate holding operation is performed. Since the pressure and the advance angle release pressure are higher, the fitting between the stopper pin 30 and the fitting hole 31 is released.

<Operation when the engine is stopped>
When the engine stop is instructed during the operation of the valve timing adjusting device 10, the vane rotor 20 rotates in the retard direction with respect to the housing 11 as in the case of the retard operation, and the most retarded position that is the lock phase. Phase controlled. Further, after the engine stop instruction, the hydraulic pressure supplied to the valve timing adjusting device 10 gradually decreases as the engine speed decreases, and the retard side pressure chamber 37 and the advance side pressure chamber 38 applied to the stopper pin 30. The pressure will also decrease.

(effect)
Next, the effect of the valve timing adjusting device 10 in the first embodiment will be described.
(A) In the valve timing adjusting device 10, before changing the vane rotor 20 to the target phase, the advance hydraulic torque Tadv and the retard hydraulic torque Trtd are held to be the same. As described above, the cam torque Tc, the retarded hydraulic pressure Trtd, and the advanced hydraulic pressure Tadv act on the vane rotor 20 that houses the stopper pin 30. The relative position of the vane rotor 20 with respect to the housing 11 changes depending on the magnitudes of these three forces. FIG. 7 shows changes in the relative position of the vane rotor 20 with respect to the housing 11 when the cam torque Tc, the retarded hydraulic torque Trtd, and the advanced hydraulic torque Tadv act on the vane rotor 20. The horizontal axis of FIG. 7B indicates the magnitude and direction of the combined torque T, which is the sum of the cam torque Tc, the retard hydraulic torque Trtd, and the advance hydraulic torque Tadv. Here, when the combined torque T is in the retard direction, it is positive, and when it is in the advance direction, it is negative. When the combined torque T is positive, the central axis 30 a of the stopper pin 30 is shifted in the retarding direction with respect to the central axis 32 a of the bush 32. Thereby, since the side wall 331 and the inner wall surface 321 do not contact, it is easy to release the fitting between the stopper pin 30 and the bush 32. On the other hand, when the combined torque T is negative, the central axis 30a of the stopper pin 30 is shifted in the advance direction with respect to the central axis 32a of the bush 32 as shown in FIG. At this time, since the side wall 331 and the inner wall surface 321 come into contact with each other, it is difficult to release the fitting between the stopper pin 30 and the bush 32.

  Here, when the holding duty ratio D1 at which the retarded hydraulic torque Trtd and the advanced hydraulic torque Tadv are the same is input to the hydraulic control valve 92, a time during which the combined torque T becomes positive due to fluctuations in the cam torque Tc occurs. . As described above, when the combined torque T is positive, the engagement between the stopper pin 30 and the bush 32 is easily released. The hydraulic control valve 92 to which the holding duty ratio D1 is input holds the advanced hydraulic torque Tadv and the retarded hydraulic torque Trtd so as to be the same (see FIG. 6C). At this time, as shown in FIG. 6A, the direction of the cam torque Tc periodically changes between positive and negative depending on the operating state of the intake valve 8. Therefore, when the advance hydraulic torque Tadv and the retard hydraulic torque Trtd are held to be the same and the cam torque Tc is positive, the stopper pin 30 and the bush 32 are released from the fitting. It becomes easy to do. At this time, when the hydraulic pressure acts on the stopper pin 30, the fitting between the stopper pin 30 and the bush 32 is released. Thereby, it is possible to prevent the occurrence of unlocking failure of the vane rotor 20 due to the malfunction of the stopper pin 30 at the time of starting the engine.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS. The second embodiment is partially different from the first embodiment in the procedure for unlocking the vane rotor. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st Embodiment, and description is abbreviate | omitted.

  FIG. 8 shows a procedure for unlocking the vane rotor 20 in the valve timing adjusting apparatus according to the second embodiment. As shown in FIG. 8, the ECU 91 inputs the advance angle correction holding duty ratio D <b> 2 to the hydraulic control valve 92 in S <b> 206 following the Yes determination in S <b> 105. Here, the advance angle correction holding duty ratio D2 is a duty ratio at which the vane rotor 20 can maintain a phase in the advance angle direction as compared with the above-described holding duty ratio D1. Specifically, as shown in FIG. 9C, when the advance angle correction holding duty ratio D2 is input, the advance hydraulic torque Tadv becomes higher than the retard hydraulic torque Trtd. When the advance angle correction holding duty ratio D2 is input, the side wall 331 of the stopper pin 30 and the inner wall surface 321 of the bush 32 are not in contact with each other. The ECU 91 corresponds to “control means”, “second determination means”, and “third determination means” described in the claims.

  Next, in S207, it is determined whether or not a predetermined time has elapsed since time t6 when the advance angle correction holding duty ratio D2 was input to the pressure control valve 92. As the predetermined time, two rotations of the crankshaft 2 correspond to one rotation of the camshaft 4, and therefore, the predetermined time or more is set to a time required for the crankshaft 2 to rotate 720 degrees. When the predetermined time has elapsed from time t6, the process proceeds to S108. If the predetermined time has not elapsed since time t6, the process proceeds to S208. The time t6 corresponds to the “second time” recited in the claims.

  Next, in S208, it is determined whether or not the vane rotor 20 has advanced. In the valve timing adjusting device of the second embodiment, when the stopper pin 30 is disengaged at time t7 before a predetermined time has elapsed from time t6, the vane rotor 20 advances as shown in FIG. Horn. Whether the phase of the vane rotor 20 has changed can be determined based on the cam angle detected by the cam angle sensor 4a. Thereby, it can be determined whether the stopper pin 30 is fitted. When it is determined that the vane rotor 20 is advanced, the process proceeds to S108. When it is determined that the vane rotor 20 is not advanced, the process returns to S206, and the advanced angle correction holding duty ratio D2 is input again.

  In the valve timing adjusting device of the second embodiment, the advance angle correction holding duty ratio D2 for advancing the vane rotor 20 is input so that the side wall 33 of the stopper pin 30 and the inner wall surface 321 of the bush 32 do not contact each other. When the advance angle correction holding duty ratio D2 is input, the vane rotor 20 advances when the stopper pin 30 is disengaged. As a result, the vane rotor 20 advances before a predetermined time elapses at time t7 when the advance angle correction holding duty ratio D2 is input. Therefore, in addition to the effect (A) of the first embodiment, the vane rotor 20 can be advanced faster than the first embodiment in which the advance is made after a predetermined time has elapsed. By advancing the advance angle of the vane rotor 20, the target phase of the vane rotor 20 can be reached quickly.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. The third embodiment is partially different from the first embodiment in the procedure for unlocking the vane rotor. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 1st Embodiment, and description is abbreviate | omitted.

  As shown in FIG. 10, the ECU 91 calculates the rise delay of the hydraulic pressure at the hydraulic control valve 92 at S306 after the Yes determination at S105. In the hydraulic control valve 92, it takes time until the predetermined pressure is generated in response to the input of the duty ratio for generating the predetermined pressure from the ECU 91. In S306, the time from the input time, which is the time when the ECU 91 inputs the duty ratio for generating a predetermined pressure, to the pressure generation time, which is the time when the hydraulic pressure commanded by the hydraulic control valve 92 is actually generated, is calculated. The ECU 91 corresponds to “control means”, “fourth determination means”, and “fifth determination means” recited in the claims.

  Next, in S307, it is determined whether or not the direction of cam torque acting on the vane rotor 20 is negative. As described above, the direction in which the cam torque acts is periodically positive or negative depending on the operating state of the intake valve 8. Here, it is determined whether or not the acting direction of the cam torque is negative based on the cam angle detected by the cam angle sensor 4a. When it is determined that the direction of cam torque action is negative, the process proceeds to S308. When it is determined that the direction of cam torque action is positive, the process proceeds to S106.

  Next, in S <b> 308, the ECU 91 inputs the retardation correction holding duty ratio D <b> 3 to the hydraulic control valve 92. The retard angle correction holding duty ratio D3 is a duty ratio at which the vane rotor 20 holds the phase in the retard angle direction as compared with the aforementioned holding duty ratio. Specifically, as shown in FIG. 11C, when the retard correction holding duty ratio D3 is input, the retard hydraulic torque Trtd becomes higher than the advance hydraulic torque Tadv. As a result, the vane rotor 20 changes the phase in the retarding direction only when the direction of cam torque action is negative.

  Next, in S309, it is determined whether or not a predetermined time has elapsed from time t8 when either the holding duty ratio D1 in S106 or the retard correction holding duty ratio D3 in S308 is first input to the hydraulic control valve 92. judge. As the predetermined time, two rotations of the crankshaft 2 correspond to one rotation of the camshaft 4, and therefore, the predetermined time or more is set to a time required for the crankshaft 2 to rotate 720 degrees. When the predetermined time has elapsed from time t8, the process proceeds to S108. If the predetermined time has not elapsed since time t8, the process returns to S306 to calculate the hydraulic pressure rising delay. The time t8 corresponds to the “third time” recited in the claims.

  In the valve timing adjusting apparatus according to the third embodiment, when the direction of cam torque acting on the vane rotor 20 is negative, the ECU 91 causes the hydraulic control valve 92 to change the phase of the vane rotor 20 to the retard direction. Enter D3. When the retard correction holding duty ratio D3 is input, the retard hydraulic torque Tadv increases with respect to the advance hydraulic torque Trtd. This prevents the cam torque from acting in the negative direction and changing the phase of the vane rotor 20 in the advance direction. This prevents an unexpected movement of the vane rotor 20 when the lock of the vane rotor 20 is released before a predetermined time elapses from time t8. Therefore, in addition to the effect (A) of the first embodiment, it is possible to prevent the generation of abnormal noise by the vane rotor 20.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described with reference to FIGS. The fourth embodiment is partially different from the second and third embodiments in the procedure for unlocking the vane rotor. In addition, the same code | symbol is attached | subjected to the site | part substantially the same as 2nd Embodiment and 3rd Embodiment, and description is abbreviate | omitted.

  As shown in FIG. 12, next to Yes determination in S105, in S406, it is determined whether or not the rotational speed of the engine 1 is low. When it determines with the rotation speed of the engine 1 being low rotation, it transfers to S306. When it determines with the rotation speed of the engine 1 not being low rotation, it transfers to S206. At this time, the ECU 91 determines “control means”, “sixth determination means”, “seventh determination means”, “eighth determination means”, “ninth determination means” and “tenth determination” described in the claims. It corresponds to “means”.

  In the valve timing adjusting device 10 of the fourth embodiment, the procedure for unlocking the vane rotor 20 is properly used in accordance with the rotational speed of the engine 1. FIG. 13 shows a lock release control execution region indicated by the relationship between the rotational speed of the engine 1 and the oil temperature. In the lock release control execution region, in a region where the engine 1 has a low number of revolutions, the vane rotor 20 is unlocked by the procedure of the valve timing adjusting device 10 in the third embodiment. In the unlocking procedure of the vane rotor 20 in the third embodiment, it is possible to prevent the generation of abnormal noise in the vane rotor 20 due to the action of the cam torque. That is, the vane rotor 20 is unlocked by a procedure that emphasizes quietness in which no abnormal noise is generated in a region where the rotational speed of the engine 1 is low. On the other hand, in the region where the rotational speed of the engine 1 is high, the vane rotor 20 is unlocked by the procedure in the valve timing adjusting device 10 of the second embodiment. In the unlocking procedure of the vane rotor 20 in the second embodiment, when the fitting of the stopper pin 30 is released before a predetermined time elapses after the advance angle correction holding duty ratio D2 is input, the vane rotor 20 is advanced. To start. That is, the advance angle of the vane rotor 20 can be quickly started in a region where the rotational speed of the engine 1 is high. Thereby, the lock | rock of the vane rotor 20 can be cancelled | released in the optimal procedure according to the rotation speed of the engine 1. FIG.

(Other embodiments)
(A) In the above-described embodiment, the valve timing adjusting device is applied to the intake valve. However, the valve to which the valve timing adjusting device of the present invention is applied is not limited to this. You may apply to an exhaust valve, and may apply to both an intake valve and an exhaust valve simultaneously. When the valve timing adjusting device of the present invention is applied to an exhaust valve, when it is determined whether or not the stopper pin is fitted to the bush, it is determined whether or not the vane rotor is at the most advanced position. Alternatively, the determination may be made based on whether or not the vehicle is at an intermediate position that is neither the most retarded angle nor the most advanced angle.

  (A) In the above-described third embodiment, when the retardation correction holding duty ratio is input, the retardation hydraulic torque increases with respect to the advance hydraulic torque that does not change as shown in FIG. However, the relationship of torque change is not limited to this. Although the retarded hydraulic torque does not change, the advanced hydraulic torque may be decreased, the retarded hydraulic torque may be increased, and the advanced hydraulic torque may be decreased.

  As mentioned above, this invention is not limited to such embodiment, It can implement with a various form in the range which does not deviate from the summary.

1 ... Engine (internal combustion engine),
2 ... Crankshaft (drive shaft),
2a ... crank angle sensor (drive shaft angle detection means),
4, 5 ... camshaft (driven shaft),
4a... Cam angle sensor (driven shaft angle detecting means),
8 ・ ・ ・ Intake valve,
9 ... exhaust valve,
10: Valve timing adjusting device,
11 ・ ・ ・ Housing,
20 ・ ・ ・ Vane rotor,
221... Accommodation hole,
30 ・ ・ ・ Stopper pin (regulating member),
31 ... fitting hole,
51, 52, 53, 54 ... retardation chamber,
55, 56, 57, 58 ... advance chamber,
92 ・ ・ ・ Hydraulic control valve (pressure generating means),
91... ECU (control means, first determination means, second determination means, third determination means, fourth determination means, fifth determination means, sixth determination means, seventh determination means, eighth determination means, eighth determination means, 9 determination means, 10th determination means),
D1 ... holding duty ratio,
D2 ... Advance angle correction holding duty ratio,
D3 ... Delay angle correction holding duty ratio,
t1 time (first time),
t6 time (second time),
t8 Time (third time).

Claims (14)

A valve timing adjusting device that transmits a driving force of a driving shaft of an internal combustion engine to a driven shaft and makes a rotational phase of the driving shaft and the driven shaft variable to adjust an opening / closing timing of at least one of an intake valve and an exhaust valve. And
A housing that rotates with one of the drive shaft or the driven shaft;
A vane rotor that rotates together with the other of the drive shaft or the driven shaft and has a vane that partitions the interior of the housing into a retard chamber and an advance chamber, and is rotatable relative to the housing;
Pressure generating means for generating pressure of hydraulic oil supplied to the advance chamber or the retard chamber;
The vane rotor is slidably received in the receiving hole formed in the vane rotor, and is fitted into a fitting hole formed in one inner wall in the rotation axis direction of the housing, thereby restraining the relative rotation of the vane rotor with respect to the housing. A regulating member,
Control means for controlling the pressure value of the hydraulic oil generated by the pressure generating means;
A predetermined time elapses from the first time when the control means inputs the holding duty ratio that makes the pressure of the hydraulic oil in the advance chamber and the pressure of the hydraulic oil in the retard chamber equal to each other. First determination means for determining whether or not
With
When it is determined by the first determination means that a predetermined time has elapsed from the first time, the control means sets the pressure of the hydraulic oil at which the vane rotor reaches a target phase to at least one of the advance chamber and the retard chamber. A valve timing adjusting device, wherein a duty ratio supplied to the pressure generating means is input to the pressure generating means. Drive shaft angle detecting means for detecting the rotation angle of the drive shaft;
2. The valve timing according to claim 1, wherein the predetermined time is longer than a time from the first time to a time at which a rotation angle of the drive shaft detected by the drive shaft angle detection means becomes 720 degrees. Adjustment device. A valve timing adjusting device that transmits a driving force of a driving shaft of an internal combustion engine to a driven shaft and makes a rotational phase of the driving shaft and the driven shaft variable to adjust an opening / closing timing of at least one of an intake valve and an exhaust valve. And
A housing that rotates with one of the drive shaft or the driven shaft;
A vane rotor that rotates together with the other of the drive shaft or the driven shaft and has a vane that partitions the interior of the housing into a retard chamber and an advance chamber, and is rotatable relative to the housing;
Pressure generating means for generating pressure of hydraulic oil supplied to the advance chamber or the retard chamber;
The vane rotor is slidably received in the receiving hole formed in the vane rotor, and is fitted into a fitting hole formed in one inner wall in the rotation axis direction of the housing, thereby restraining the relative rotation of the vane rotor with respect to the housing. A regulating member,
Control means for controlling the pressure value of the hydraulic oil generated by the pressure generating means;
Predetermined from a second time which is a time when the control means inputs to the pressure generating means an advance correction correction duty ratio at which the pressure of the hydraulic oil in the advance chamber becomes higher than the pressure of the hydraulic oil in the retard chamber. Second determination means for determining whether or not time has passed;
When the second determination means determines that the elapsed time from the second time is less than a predetermined time, the second determination means determines whether the phase of the vane rotor has changed from the most retarded position or the most advanced position. 3 determination means;
With
When the third determining means determines that the phase of the vane rotor has changed from the most retarded angle position or the most advanced angle position, the control means determines the pressure of the hydraulic oil at which the vane rotor becomes the target phase in the advance angle chamber. And a duty ratio supplied to at least one of the retard chambers is input to the pressure generating means. Drive shaft angle detecting means for detecting the rotation angle of the drive shaft;
4. The valve timing according to claim 3, wherein the predetermined time is longer than a time from the second time to a time at which the rotation angle of the drive shaft detected by the drive shaft angle detection means becomes 720 degrees. Adjustment device. A valve timing adjusting device that transmits a driving force of a driving shaft of an internal combustion engine to a driven shaft and makes a rotational phase of the driving shaft and the driven shaft variable to adjust an opening / closing timing of at least one of an intake valve and an exhaust valve. And
A housing that rotates with one of the drive shaft or the driven shaft;
A vane rotor that rotates together with the other of the drive shaft or the driven shaft and has a vane that partitions the interior of the housing into a retard chamber and an advance chamber, and is rotatable relative to the housing;
Pressure generating means for generating pressure of hydraulic oil supplied to the advance chamber or the retard chamber;
The vane rotor is slidably received in the receiving hole formed in the vane rotor, and is fitted into a fitting hole formed in one inner wall in the rotation axis direction of the housing, thereby restraining the relative rotation of the vane rotor with respect to the housing. A regulating member,
Control means for controlling the pressure value of the hydraulic oil generated by the pressure generating means;
Driven shaft angle detection means for detecting a rotation angle of the driven shaft;
It is determined from the angle of the driven shaft detected by the driven shaft angle detection means whether the direction of cam torque acting on the driven shaft by opening / closing at least one of the intake valve and the exhaust valve is an advance direction. Fourth determining means for
With
When the fourth determining means determines that the cam torque action direction is the advance angle direction, the control means is a delay in which the hydraulic oil pressure in the retard chamber is higher than the hydraulic oil pressure in the advance chamber. Input the angle correction holding duty ratio to the pressure generating means,
When it is determined by the fourth determination means that the cam torque is acting in the retarded direction or the cam torque is not acting, the control means determines the hydraulic oil pressure in the advance chamber and the hydraulic oil in the retard chamber. A valve timing adjusting device, wherein a holding duty ratio for making the pressure equal to the input pressure is input to the pressure generating means. Fifth determining means for determining whether or not a predetermined time has elapsed from a third time which is a time when the holding duty ratio or the retarded angle corrected holding duty ratio is first input to the pressure generating means by the control means. With
When it is determined by the fifth determination means that a predetermined time has elapsed from the third time, the control means sets the pressure of the hydraulic oil at which the vane rotor reaches a target phase to at least one of the advance chamber and the retard chamber. 6. The valve timing adjusting device according to claim 5, wherein a duty ratio supplied to the pressure is input to the pressure generating means. Drive shaft angle detecting means for detecting the rotation angle of the drive shaft;
The valve timing according to claim 6, wherein the predetermined time is longer than a time from the third time to a time at which the rotation angle of the drive shaft detected by the drive shaft angle detection means becomes 720 degrees. Adjustment device. A valve timing adjusting device that transmits a driving force of a driving shaft of an internal combustion engine to a driven shaft and makes a rotational phase of the driving shaft and the driven shaft variable to adjust an opening / closing timing of at least one of an intake valve and an exhaust valve. And
A housing that rotates with one of the drive shaft or the driven shaft;
A vane rotor that rotates together with the other of the drive shaft or the driven shaft and has a vane that partitions the interior of the housing into a retard chamber and an advance chamber, and is rotatable relative to the housing;
Pressure generating means for generating pressure of hydraulic oil supplied to the advance chamber or the retard chamber;
The vane rotor is slidably received in the receiving hole formed in the vane rotor, and is fitted into a fitting hole formed in one inner wall in the rotation axis direction of the housing, thereby restraining the relative rotation of the vane rotor with respect to the housing. A regulating member,
Control means for controlling the pressure value of the hydraulic oil generated by the pressure generating means;
Drive shaft angle detection means for detecting the rotation angle of the drive shaft;
Driven shaft angle detection means for detecting a rotation angle of the driven shaft;
Sixth determination means for determining whether or not the rotational speed of the internal combustion engine detected by the drive shaft angle detection means is low;
It is determined from the angle of the driven shaft detected by the driven shaft angle detection means whether the direction of cam torque acting on the driven shaft by opening / closing at least one of the intake valve and the exhaust valve is an advance direction. A seventh determination means for
With
When the sixth determining means determines that the rotational speed of the internal combustion engine is low and the seventh determining means determines that the operating direction of the cam torque is an advance angle, the control means A retard correction holding duty ratio at which the pressure of the hydraulic oil in the retard chamber becomes higher than the pressure of the hydraulic oil in the chamber is input to the pressure generating means,
When it is determined by the sixth determining means that the rotational speed of the internal combustion engine is low, and the seventh determining means determines that the operating direction of the cam torque is the retard direction or the cam torque is not acting The valve timing adjusting device is characterized in that the control means inputs a holding duty ratio that makes the pressure of the hydraulic oil in the advance chamber and the pressure of the hydraulic oil in the retard chamber equal to the pressure generating means. Eighth determining means for determining whether or not a predetermined time has elapsed from a fourth time, which is the time when the holding duty ratio or the retarded angle corrected holding duty ratio is first input to the pressure generating means by the control means. With
When it is determined by the eighth determination means that a predetermined time has elapsed from the fourth time, the control means determines the hydraulic oil pressure at which the vane rotor reaches a target phase at least one of the advance chamber and the retard chamber. 9. The valve timing adjusting device according to claim 8, wherein a duty ratio supplied to the pressure generator is input to the pressure generating means.   When it is determined by the sixth determination means that the rotational speed of the internal combustion engine is high, the control means increases the pressure of the hydraulic oil in the advance chamber as compared with the pressure of the hydraulic oil in the retard chamber. The valve timing adjusting device according to claim 8 or 9, wherein an advance angle correction holding duty ratio is input to the pressure generating means. A ninth determination means for determining whether or not a predetermined time has elapsed from a fifth time, which is a time when the advance angle correction holding duty ratio is first input to the pressure generation means by the control means;
When it is determined by the ninth determination means that a predetermined time has elapsed from the fifth time, the control means determines the pressure of the hydraulic oil at which the vane rotor reaches a target phase at least one of the advance chamber and the retard chamber. The valve timing adjusting device according to claim 10, wherein a duty ratio to be supplied to the pressure is input to the pressure generating means. When the ninth determining means determines that the elapsed time from the fifth time is less than a predetermined time, the ninth determining means determines whether the phase of the vane rotor has changed from the most retarded position or the most advanced position. 10 determination means,
When the tenth determining means determines that the phase of the vane rotor has changed from the most retarded position or the most advanced angle position, the control means determines the pressure of the hydraulic oil at which the vane rotor reaches the target phase as the advance chamber. The valve timing adjusting device according to claim 11, wherein a duty ratio supplied to at least one of the retard chambers is input to the pressure generating means.   9. The predetermined time is longer than the time from the fourth time or the fifth time to the time when the rotation angle of the drive shaft detected by the drive shaft angle detecting means becomes 720 degrees. To 12. The valve timing adjusting device according to any one of claims 12 to 12.   The control means measures the time from the input time when the control means inputs a predetermined duty ratio to the pressure generating means to the time when the pressure of the hydraulic oil generated by the pressure generating means reaches the predetermined pressure value. The predetermined duty ratio is input to the pressure generation means retroactively from the time when the pressure of the hydraulic oil generated by the generation means is controlled to the predetermined pressure value. The valve timing adjusting device described.

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