JP2015105643A - Valve timing adjusting device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To compatibly enhance the responsiveness of valve timing and robust performance.SOLUTION: A control system 50 comprises: reflow passages 742, 744 which make working fluids reflow to an introduction chamber side from a discharge chamber side out of a plurality of operation chambers 22, 24 in an advance position Pa and a retardant position Pr; drain passages 746, 747 which drain the working fluids discharged to the reflow passage 742, 744 sides from the discharge chamber to the outside in a communication state with the reflow passages 742, 744; and control valve bodies 780, 790 which reciprocate in a radial direction in a sleeve 73 which rotates integrally with a vane rotor 14, and being the control bodies 780, 790 which move in accordance with an increase of a centrifugal force F to communication regions Aac, Arc which make the reflow passages 742, 744 communicate with drain passages 746, 747 from block regions Aai, Ari for blocking the reflow passages 742, 744 with respect to the drain passages 746, 747.

Description

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

  2. Description of the Related Art Conventionally, a valve timing adjusting device including a housing rotor that rotates in conjunction with a crankshaft and a vane rotor that rotates in conjunction with a camshaft is known. For example, in Patent Document 1, for a vane rotor that divides a plurality of working chambers in a housing rotor, the desired valve timing is realized by adjusting the rotational phase with respect to the housing rotor by entering and exiting the working fluid into each working chamber. Have been disclosed. The disclosed device of Patent Document 1 includes a control system that controls the entry and exit of the working fluid into and from each working chamber in accordance with the moving position of the spool within the sleeve.

  Specifically, in the disclosed device of Patent Document 1, an advance position for changing the rotation phase to advance and a retard position for changing the rotation phase to retard are set as the moving position of the spool. In each of the advance angle position and the retard angle position, the control system switches between an introduction chamber as a working chamber for introducing the working fluid and a discharge chamber as a working chamber for discharging the working fluid. As a result, it is possible to control the operation fluid to enter and exit each working chamber.

  Here, in particular, in the device disclosed in Patent Document 1, two types of movement positions are set as advance positions. In one advance position, when the rotational speed of the internal combustion engine is low, the return of the hydraulic fluid from the discharge chamber side to the introduction chamber side is allowed through the return passage that is cut off from the drain passage. In this case, since the alternating cycle of the cam torque transmitted from the camshaft to the vane rotor becomes longer, the followability of the reflux with respect to the cycle becomes sharp, so that the introduction pressure to the introduction chamber follows the rotational speed of the internal combustion engine, for example. Even when the value is low, the response of the valve timing adjustment can be improved. Further, at the other advance angle position, when the rotational speed of the internal combustion engine is high, the return passage communicates with the drain passage, whereby the hydraulic fluid in the discharge chamber is drained to the outside. In this case, the valve timing is not obtained by using the recirculation that slows down the followability with respect to the alternating cycle of the short cam torque, but using the introduction pressure into the introduction chamber that is increased by following the rotational speed of the internal combustion engine, for example. Adjustment responsiveness can be improved.

  In the device disclosed in Patent Document 1, two types of movement positions are set for the retard angle position, and the advance angle responsiveness can be improved as in the case of the two types of advance angle positions.

JP 2012-122453 A

  However, in the disclosed apparatus of Patent Document 1, two types of a return use position and a non-use position are set as each of the advance position and the retard position. Therefore, under a situation where the amount of spool movement is limited by a small mounting space in the internal combustion engine, a range that can be set as each advance angle position and each retard angle position becomes narrow. Therefore, the robustness tends to be deteriorated with respect to the hydraulic fluid entry / exit control in accordance with the moving position of the spool, and hence the valve timing adjustment.

  The present invention has been made in view of the above-described problems, and an object thereof is to improve both the responsiveness and robustness of valve timing adjustment.

  The invention disclosed in order to solve the above-described problem is that a housing rotor (12) rotating in conjunction with a crankshaft of an internal combustion engine and a camshaft (2) of the internal combustion engine rotate in conjunction with each other, and a plurality of operations are performed in the housing rotor. The chambers (22, 24) are partitioned in the rotational direction, and the movement of the spool (74) in the sleeve (73), and the vane rotor (14) in which the rotational phase with respect to the housing rotor is adjusted by the entry and exit of hydraulic fluid into and from the respective working chambers And a control system (50) for controlling the flow of hydraulic fluid into and out of each working chamber in accordance with the position, and a valve timing adjusting device for adjusting the valve timing of the valve that opens and closes the camshaft by torque transmission from the crankshaft The moving position that changes the rotational phase is defined as the advanced position (Pa), while the moving position that changes the rotational phase is retarded. When the position (Pr) is defined, an advance chamber is defined as an introduction chamber serving as a working chamber into which the working fluid is introduced by pressure following the rotational speed (S) of the internal combustion engine, and a discharge chamber serving as a working chamber from which the working fluid is discharged. The control system for switching and selecting each of the position and the retard angle position is a recirculation passage (742, 744) that recirculates the working fluid from the discharge chamber side to the introduction chamber side at a specific position that is at least one of the advance angle position and the retard angle position. , 737) and the recirculation passage, the drain passage (746, 747, 66) for draining the working fluid discharged from the discharge chamber to the recirculation passage side and the sleeve rotating integrally with the vane rotor The control valve body (780, 790) reciprocally moves in the radial direction, and the return passage is connected to the drain passage from the blocking region (Aai, Ari) that cuts off the return passage from the drain passage. It is thereby communicating area (Aac, Arc) to, and a control valve body which moves in response to an increase of the centrifugal force (F), characterized by having.

  According to the present invention, at the specific position of the spool, while the rotational speed of the internal combustion engine is low and the centrifugal force is small, the return passage is blocked from the drain passage by the control valve body in the cutoff region. The working fluid is allowed to recirculate from the inlet toward the introduction chamber. At this time, since the alternating cycle of the cam torque transmitted from the cam shaft to the vane rotor becomes longer, the followability of the return to the alternating cycle becomes sharp, so the pressure introduced into the introduction chamber following the rotational speed of the internal combustion engine is increased. Even if it is low, the responsiveness of valve timing adjustment can be improved. Further, at a specific position of the spool, when the rotational speed increases and the centrifugal force increases, the control valve element moved to the communication region causes the return passage to be in communication with the drain passage, and therefore is discharged from the discharge chamber to the return passage side. The hydraulic fluid is drained to the outside without being refluxed to the introduction chamber side. At this time, responsiveness of valve timing adjustment is not used by using the introduction pressure into the introduction chamber that has become high pressure following the rotation speed, without using the reflux that slows down the followability with respect to the alternating cycle of the short cam torque. Can increase.

  According to such an invention, at least one of the advance angle position and the retard angle position, which are specific positions, even if the amount of movement of the spool is limited, the return use position and the non-use position are made common. Therefore, the range that can be set as the at least one position can be expanded. Therefore, the robustness can be enhanced at the same time as the above responsiveness with respect to the hydraulic fluid entry / exit control according to the spool movement position, and thus the valve timing adjustment.

  According to another disclosed invention, the center of gravity (Ca, Cr) of the control valve body is set closer to the communication region than the rotation center (O) of the sleeve in the blocking region.

  As in the present invention, the control valve body whose center of gravity is set closer to the communication region than the rotation center of the sleeve in the blocking region can surely move to the communication region as the centrifugal force increases. Therefore, the reliability of the effect of improving the responsiveness of the valve timing adjustment can be improved.

It is sectional drawing which shows the valve timing adjustment apparatus by one Embodiment. It is a schematic diagram explaining the whole structure of the valve timing adjustment apparatus of FIG. It is a characteristic view explaining the cam torque transmitted to the vane rotor of FIG. It is a cross-sectional schematic diagram which shows the structure of the control system of FIG. It is a cross-sectional schematic diagram which shows the operation state different from FIG. It is a cross-sectional schematic diagram which shows the operation state different from FIG. It is a cross-sectional schematic diagram which shows the operation state different from FIGS. It is a cross-sectional schematic diagram which shows the operation state different from FIGS. It is a cross-sectional schematic diagram which shows the operation state different from FIGS. It is a cross-sectional schematic diagram which shows the operation state different from FIGS. It is a cross-sectional schematic diagram which shows the operation state different from FIGS. It is a cross-sectional schematic diagram which shows the operation state different from FIGS. It is a cross-sectional schematic diagram which shows the advance angle drain control valve and retard angle drain control valve of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG. It is a cross-sectional schematic diagram which shows the modification of FIG.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

  As shown in FIG. 1, a valve timing adjusting apparatus 1 according to an embodiment of the present invention is mounted on an internal combustion engine of a vehicle. The device 1 adjusts the valve timing of the internal combustion engine by using the pressure of the hydraulic fluid that is the hydraulic fluid. The apparatus 1 adjusts the valve timing of the intake valve as the valve timing of the “valve” that opens and closes the camshaft 2 by transmission of crank torque from a crankshaft (not shown) in the internal combustion engine. The apparatus 1 includes a rotation mechanism system 10 and a control system 50.

(Basic structure of rotating mechanism system)
First, the basic configuration of the rotation mechanism system 10 will be described. The rotation mechanism system 10 is installed in a transmission path that transmits crank torque from the crankshaft to the camshaft 2. The rotation mechanism system 10 includes a housing rotor 12 and a vane rotor 14.

  The housing rotor 12 has a plurality of shoes 120 and a sprocket (not shown). Each shoe 120 protrudes inward in the radial direction from a place spaced apart from each other in the rotational direction. A storage chamber 20 is formed between the shoes 120 adjacent to each other in the rotation direction. The sprocket is connected to the crankshaft via a timing chain (not shown). With this connection, while the internal combustion engine is rotating, crank torque is transmitted from the crankshaft to the sprocket, so that the housing rotor 12 rotates in a certain direction (counterclockwise in FIG. 1) in conjunction with the crankshaft.

  The vane rotor 14 is coaxially disposed in the housing rotor 12. The vane rotor 14 has a rotating shaft 140 and a plurality of vanes 142. The cylindrical rotating shaft 140 is fixed coaxially with the cam shaft 2. With this fixing, the vane rotor 14 can rotate relative to the housing rotor 12 while rotating in a certain direction (counterclockwise in FIG. 1) in conjunction with the camshaft 2.

  Each vane 142 protrudes radially outward from the rotating shaft 140 at a predetermined interval in the rotational direction, and is accommodated in the corresponding accommodating chamber 20. Each vane 142 divides the corresponding accommodating chamber 20 in the rotation direction, thereby partitioning the advance working chamber 22 and the retard working chamber 24 in the housing rotor 12. A plurality of the advance working chambers 22 and the retard working chambers 24 are formed, and are alternately arranged in the rotation direction.

  With such a configuration, in the rotation mechanism system 10, the rotation phase is adjusted by entering and exiting the hydraulic oil to and from each advance working chamber 22 and each retard working chamber 24, thereby realizing valve timing corresponding to the rotation phase. The Specifically, the volume of each advance working chamber 22 is expanded by introducing hydraulic oil, and the volume of each retarded working chamber 24 is reduced by discharging hydraulic oil, whereby the rotational phase changes in the advance direction. Accordingly, the valve timing is advanced. On the other hand, the volume of each retarded working chamber 24 is increased by introducing hydraulic oil, and the volume of each advanced working chamber 22 is reduced by discharging hydraulic oil, so that the rotational phase changes in the retarded direction, and accordingly. The valve timing is retarded. Further, the hydraulic oil is confined in either of the working chambers 22 and 26 due to the restriction of the hydraulic oil entering and exiting from each of the advance working chambers 22 and each retarded working chamber 24, so that the rotational phase changes depending on the working oil. Without, the valve timing is substantially maintained.

(Basic configuration of control system)
Next, the basic configuration of the control system 50 will be described. The control system 50 controls the entry and exit of the hydraulic oil in order to drive the rotation mechanism system 10. As shown in FIG. 2, the control system 50 includes passages 62, 64, 66 and 68, a control valve unit 70 and a control circuit 90.

  The advance angle entrance / exit passage 62 communicates with each advance angle working chamber 22. The retard angle entry / exit passage 64 communicates with each retard angle working chamber 24. The drain recovery passage 66 can be drained to the drain pan 3 side by being released to the atmosphere together with the drain pan 3 which is an external drain recovery section. The supply passage 68 communicates with the pump 4 as a supply source. Here, the pump 4 provided in the internal combustion engine is a mechanical pump that is driven by receiving crank torque during rotation of the internal combustion engine, and discharges hydraulic oil sucked from the drain pan 3 to the supply passage 68. As a result, at the time of steady operation in which the supply of hydraulic oil from the pump 4 is continued in the internal combustion engine, the supply pressure of hydraulic oil from the pump 4 also increases and decreases following the increase and decrease of the rotational speed of the internal combustion engine.

  The control valve unit 70 is an electromagnetically driven spool valve that uses a driving force generated by energizing the solenoid 71 and a restoring force generated by the return spring 72. The control valve unit 70 has an advance / inlet port 82, a retard / inject port 84, an advance drain port 86, a retard drain port 87, and a supply port 88. The advance angle input / output port 82 communicates with each advance angle working chamber 22 via an advance angle input / output passage 62. The retard angle entry / exit port 84 communicates with each retard angle working chamber 24 via the retard angle entry / exit passage 64. The advanced drain port 86 and the retarded drain port 87 communicate with the drain recovery passage 66. The supply port 88 is in communication with the supply passage 68. The control valve unit 70 performs switching control of hydraulic oil input / output through the ports 82, 84, 86, 87, 88 in accordance with energization to the solenoid 71.

  The control circuit 90 is an electronic circuit mainly composed of, for example, a microcomputer, and is electrically connected to the solenoid 71 and various electrical components (not shown) of the internal combustion engine. The control circuit 90 controls the operation of the internal combustion engine including energization to the solenoid 71 in accordance with a computer program stored in the internal memory.

(Cam torque)
Next, cam torque transmitted from the cam shaft 2 to the vane rotor 14 will be described. During rotation of the internal combustion engine, cam torque generated due to a spring reaction force or the like from an intake valve driven to open and close by the cam shaft 2 is transmitted to the shaft 2 and acts on the vane rotor 14. Here, as shown in FIG. 3, the fluctuating torque alternates between a negative torque acting in the advance direction with respect to the housing rotor 12 and a positive torque acting in the retard direction with respect to the housing rotor 12. The cam torque may be such that, for example, the peak torque T + of the positive torque is larger than the peak torque T− of the negative torque, so that the average torque is biased toward the positive torque side. Alternatively, the cam torque may be such that the average torque becomes substantially zero when the peak torque T + of the positive torque becomes substantially equal to the peak torque T− of the negative torque.

(Detailed configuration of control system)
Next, a detailed configuration of the control system 50 will be described. As shown in FIG. 1, the control valve unit 70 constituting the control system 50 linearly reciprocates the spool 74 within the sleeve 73.

  Specifically, the sleeve 73 is formed in a cylindrical shape from metal. The sleeve 73 is coaxially built over the vane rotor 14 and the camshaft 2. With this built-in, the sleeve 73 rotates integrally with the vane rotor 14 and the cam shaft 2. As shown in FIG. 4, the sleeve 73 accommodates a return spring 72 made of a metal coil spring coaxially. The sleeve 73 forms an advance drain port 86, a retard input / output port 84, a supply port 88, an advance input / output port 82, and a retard drain port 87 in this order from one end side to the other end side in the axial direction. ing.

  As shown in FIG. 1, the spool 74 is formed of a metal in a cylindrical rod shape. The spool 74 is accommodated coaxially in the sleeve 73 and is slidably supported by the inner peripheral surface of the accommodation destination. With such sliding support, the spool 74 also rotates integrally with the vane rotor 14 and the cam shaft 2. As shown in FIG. 4, a drive shaft 71 a of a solenoid 71 is connected to one axial end of the spool 74. A return spring 72 is connected to the other axial end of the spool 74. The solenoid 71 urges the spool 74 toward the return spring 72 by generating a driving force on the drive shaft 71a in accordance with energization from the control circuit 90 (see FIG. 2). At the same time, the return spring 72 urges the spool 74 toward the solenoid 71 by generating a restoring force by compressive deformation between the spool 74 and the sleeve 73. Under such an urging state, the moving position of the spool 74 (hereinafter simply referred to as “spool moving position”) is determined in accordance with the balance between the driving force of the driving shaft 71 a and the restoring force of the return spring 72.

  As shown in FIG. 2, the control valve unit 70 has an advance recirculation passage 742, a retard recirculation passage 744, an advance drain passage 746, and a retard drain passage 747. As shown in FIG. 4, the advance angle return passage 742 and the retard angle return passage 744 are each formed in a through-hole shape by the spool 74. The advance angle return passage 742 and the retard angle return passage 744 extend from the opening ends 742a and 744a formed by joining each other to the opening ends 742b and 744b that are separated from each other in the axial direction. The advance drain passage 746 is formed in a through hole shape by the spool 74. The advance drain passage 746 is provided so as to be able to communicate with the open end 742 b of the advance return passage 742, and extends to the axial end of the spool 74 on the advance drain port 86 side. The retarded drain passage 747 is formed in a through hole shape by the spool 74. The retard drain passage 747 is provided so as to be able to communicate with the opening end 744 b of the retard return passage 744 and extends to the axial end of the spool 74 on the retard drain port 87 side.

  With this configuration, at the advance angle position Pa shown in FIGS. 4 to 7 as the spool movement position, the open end 742a of the advance return flow path 742 communicates with the advance angle input / output port 82 and the supply port 88, and the open end of the same path 742 742 b communicates with the retarded entry / exit port 84. At the same time, at the advance position Pa, the open end 744 a of the retard return path 744 communicates with the advance / inlet port 82 and the supply port 88, and the open end 744 b of the path 744 is closed by the sleeve 73.

  8-11, the open end 744a of the retard return passage 744 communicates with the retard inlet / outlet port 84 and the supply port 88, and the open end 744b of the passage 744 is at the retard position Pr shown in FIGS. The lead angle communication port 82 communicates. At the same time, at the retard position Pr, the open end 742 a of the advance recirculation passage 742 communicates with the retard input / output port 84 and the supply port 88, and the open end 742 b of the passage 742 is closed by the sleeve 73.

  Further, in the holding position Ph shown in FIG. 12 as the spool movement position, the open ends 742a and 744a of the respective return passages 742 and 744 communicate with the supply port 88, but the open ends 742b and 744b of the return passages 742 and 744 are connected to the sleeve. It is blocked by 73. At the same time, at the holding position Ph, both the advance / inlet port 82 and the retard-in / out port 84 are closed by the spool 74.

  As shown in FIG. 2, the control valve unit 70 further includes an advance return check valve 76 and a retard return check valve 77. The advance angle return check valve 76 and the retard angle return check valve 77 are provided in the advance angle return path 742 and the retard angle return path 744, respectively. As shown in FIG. 4, the reflux check valves 76 and 77 are formed by combining individual valve seats 762 and 772, valve members 760 and 770, and a common elastic member 767.

  The advance valve seat 762 is formed by a conical surface whose diameter decreases toward the opening end 742b side of the inner surface of the advance return passage 742. The advance valve member 760 is formed in a spherical shape with metal. The advance valve member 760 is accommodated in the advance recirculation passage 742 closer to the opening end 742a than the advance valve seat 762, and can be attached to and detached from the valve seat 762 in the axial direction. The retard valve seat 772 is formed by a conical surface whose diameter decreases toward the opening end 744 b side in the inner surface of the retard return passage 744. The retard valve member 770 is formed in a spherical shape with metal. The retard valve member 770 is accommodated in the retard recirculation passage 744 closer to the opening end 744 a than the retard valve seat 772, and can be attached to and detached from the valve seat 772 in the axial direction. The elastic member 767 made of a metal coil spring is accommodated across the advance and return passages 742 and 744, and is coaxially interposed between the advance and return valve members 760 and 770. Has been. The elastic member 767 generates a restoring force by compressive deformation between the advance valve member 760 and the retard valve member 770, thereby causing the advance valve member 760 and the retard valve member 770 to move toward the advance valve seat 762 side. Further, the urging is performed toward the retarded valve seat 772 side.

  With such a configuration, the opening angle 742b side is higher than the opening end 742a side in the advance angle recirculation passage 742, so that when the advance valve member 760 is separated from the advance valve seat 762 as shown in FIG. The reflux check valve 76 is opened. Thus, particularly in the advance angle return passage 742 at the advance position Pa, the return of the hydraulic oil from the retard angle input / output port 84 side to the advance angle input / output port 82 side is allowed as indicated by the broken line arrow in FIG. On the other hand, when the advanced valve member 760 is seated on the advanced valve seat 762 as shown in FIGS. 5 to 11 because the advanced end reflux passage 742 has a higher pressure on the open end 742a side than the open end 742b side, the advanced angle recirculation is performed. The check valve 76 is closed. Thereby, particularly in the advance recirculation passage 742 at the advance position Pa, the backflow of the hydraulic oil from the advance / inlet port 82 side to the retard input / output port 84 side is restricted as indicated by broken line arrows in FIGS.

  Further, when the retarded valve member 770 is separated from the retarded valve seat 772 as shown in FIG. The stop valve 77 is opened. Thereby, in particular, in the retarded angle return passage 744 at the retarded angle position Pr, the return of the hydraulic oil from the advanced angle input / output port 82 side to the retarded angle input / output port 84 side is permitted as indicated by the broken line arrow in FIG. On the other hand, when the retarded valve member 770 is seated on the retarded valve seat 772 as shown in FIGS. 4 to 7 and 9 to 11, the retarded return passage 744 has a higher pressure on the opened end 744 a side than on the opened end 744 b side. Then, the retarded return check valve 77 is closed. As a result, particularly in the retarded angle return passage 744 at the retarded angle position Pr, the backflow of hydraulic oil from the retarded angle inlet / outlet port 84 side to the advanced angle inlet / outlet port 82 side is restricted as shown by broken line arrows in FIGS.

  As shown in FIG. 2, the control valve unit 70 further includes an advance drain control valve 78 and a retard drain control valve 79. The advance drain control valve 78 and the retard drain control valve 79 are provided in the advance drain passage 746 and the retard drain passage 747, respectively. As shown in FIGS. 4 and 13, the drain control valves 78 and 79 are configured by combining individual control valve bodies 780 and 790 and individual urging members 782 and 792, respectively.

  The advance control valve body 780 is formed in a rectangular parallelepiped shape or a cylindrical shape from metal. The advance angle control valve body 780 is accommodated in the advance angle drain passage 746 and can reciprocate in the radial direction of the spool 74 in the sleeve 73. In the advance angle control valve body 780, two types of areas Aai and Aac are set as moving areas. Specifically, in the advance blocking area Aai shown in FIGS. 4, 5, 8 and 9, the advance control valve body 780 closes the advance drain passage 746 in the middle, so that the advance return passage 742 advances. The square drain passage 746 is blocked. On the other hand, in the advance communication area Aac shown in FIGS. 6, 7, and 10 to 12, the advance control valve body 780 opens the advance drain passage 746 in the middle, so that the advance return passage 742 becomes the advance drain. It communicates with the passage 746.

  Here, as shown in FIG. 13, the center of gravity Ca of the advance angle control valve body 780 is radially outside the rotation center O common to the sleeve 73 and the spool 74 in the advance angle blocking area Aai, that is, on the advance angle communication area Aac side. Is set to be located. The advance angle control valve body 780 having such a setting is subjected to the action of the centrifugal force F in the sleeve 73 that rotates integrally with the vane rotor 14 during the rotation of the internal combustion engine, so that the advance angle blocking area Aai is changed to the advance angle communication area Aac. Is moved according to the increase of the force F. In the present embodiment, the center of gravity Ca of the advance angle control valve body 780 formed from one homogeneous material substantially coincides with the center of the dimension of the valve body 780 in the three-dimensional direction.

  As shown in FIGS. 4 and 13, the advance biasing member 782 made of a metal coil spring is housed inside the spool 74 on the radially outer side of the advance control valve body 780. The advance angle biasing member 782 is interposed between the advance angle control valve body 780 and the spool 74. The advance urging member 782 generates a restoring force by compressive deformation between the advance control valve body 780 and the spool 74, thereby moving the valve body 780 from the advance communication area Aac side to the advance angle cutoff area Aai side. Energize in the radial direction. Under such an urging state, as shown in FIGS. 4, 5, 8, and 9, as shown in FIGS. . On the other hand, as shown in FIGS. 6, 7, 10 to 12, when the rotational speed S of the internal combustion engine becomes equal to or higher than the set speed Sth, the advance control valve body 780 moves within the advance communication area Aac. The set speed Sth is set to, for example, about 3500 rpm as the crankshaft rotational speed S that is a double value of the camshaft 2 rotational speed.

  As shown in FIGS. 4 and 13, the retard control valve element 790 is formed in a rectangular parallelepiped shape or a cylindrical shape from metal. The retard control valve element 790 is accommodated in the retard drain passage 747 and can reciprocate in the radial direction of the spool 74 in the sleeve 73. Two types of areas Ari and Arc are also set in the retard control valve element 790 as moving areas. Specifically, in the retarded angle blocking region Ari shown in FIGS. 4, 5, 8, and 9, the retarded control valve body 790 blocks the retarded drain passage 747 in the middle so that the retarded return passage 744 is retarded. The square drain passage 747 is blocked. On the other hand, in the retard communication area Arc shown in FIGS. 6, 7, 10 to 12, the retard control valve body 790 opens the retard drain passage 747 in the middle, so that the retard return passage 744 is retarded. It communicates with the passage 747.

  Here, as shown in FIG. 13, the center of gravity Cr of the retard control valve element 790 is radially outward from the rotation center O common to the sleeve 73 and the spool 74 in the retard blocking area Ari, that is, the retard communication area Arc side. Is set to be located. The retard angle control valve body 790 having such a setting is subjected to the action of the centrifugal force F in the sleeve 73 that rotates integrally with the vane rotor 14 during the rotation of the internal combustion engine, so that the retard angle blocking region Ari is changed to the retard angle communication region Arc. Is moved according to the increase of the force F. In the present embodiment, the center of gravity Cr of the retard control valve body 790 formed from one homogeneous material also substantially coincides with the dimensional center of the valve body 790 in the three-dimensional direction.

  As shown in FIGS. 4 and 13, the retard urging member 792 made of a metal coil spring is housed inside the spool 74 on the radially outer side of the retard control valve body 790. The retard urging member 792 is interposed between the retard control valve element 790 and the spool 74. The retard urging member 792 generates a restoring force by compressive deformation between the retard control valve body 790 and the spool 74, thereby moving the valve body 790 from the retard communication area Arc to the retard blocking area Ari. Energize in the radial direction. Under such an urging state, as shown in FIGS. 4, 5, 8, and 9, while the rotational speed S of the internal combustion engine is less than the set speed Sth, the retard control valve body 790 moves within the retard cut-off area Ari. . On the other hand, as shown in FIGS. 6, 7, 10 to 12, when the rotational speed S of the internal combustion engine becomes equal to or higher than the set speed Sth, the retard control valve body 790 moves within the retard communication area Arc. The set speed Sth is set to substantially the same value as that of the advance angle control valve body 780.

  In addition to the above, the control system 50 includes a reed supply check valve (that is, a reed valve) 69 in the supply passage 68 as shown in FIGS. The supply check valve 69 is opened when the supply passage 68 has a higher pressure on the pump 4 side than on the supply port 88 side. As a result, in the supply passage 68, hydraulic oil supply from the pump 4 side toward the supply port 88 side is permitted as indicated by the broken line arrows in FIGS. On the other hand, the supply check valve 69 is closed when the supply port 88 side has a higher pressure than the pump 4 side. As a result, in the supply passage 68, the backflow of hydraulic oil from the supply port 88 side toward the pump 4 side is restricted as indicated by broken line arrows in FIGS. 4, 5, 7 to 9, 11.

(Valve timing adjustment operation)
During steady operation of the internal combustion engine, the control circuit 90 controls energization to the solenoid 71 so as to realize valve timing suitable for the operation state. As a result, the spool 74 moves to any one of the advance angle position Pa, the retard angle position Pr, and the holding position Ph, so that the hydraulic oil enters and exits the advance angle working chambers 22 and the retard angle working chambers 24. Is done. At this time, in particular, at the advance angle position Pa and the retard angle position Pr, the “introduction chamber” for introducing the hydraulic oil and the “discharge chamber” for discharging the hydraulic oil are switched between the plurality of operation chambers 22, 24. Selected. Hereinafter, each of the operations at the advance position Pa and the retard position Pr and the operation at the holding position Ph will be described in detail as the valve timing adjustment operations of the apparatus 1.

(A1) Advance angle operation at the advance angle position Pa during low speed rotation In advance angle operation in which the rotation phase is advanced at the advance angle position Pa in FIG. 2, the rotational speed S of the internal combustion engine is as shown in FIGS. While the speed is lower than the set speed Sth, the control valve bodies 780 and 790 move to the respective shut-off areas Aai and Ari. As a result, the reflux passages 742 and 744 are blocked from the drain passages 746 and 747, respectively.

  Under such a shut-off state, when each retarded working chamber 24 as a “discharge chamber” is compressed by transmitting negative torque of the cam torque, each retarded working chamber is placed in the advanced return passage 742 as indicated by the broken line arrow in FIG. The hydraulic oil is discharged from 24 through the retarded angle inlet / outlet passage 64 and the retarded angle inlet / outlet port 84. At this time, each advance working chamber 22 as an “introducing chamber” expanded by negative torque transmission communicates with the advance return passage 742 through the advance / inlet passage 62 and the advance / inlet port 82. Therefore, the recirculation through the advance recirculation passage 742 that is cut off from the advance drain passage 746 from each retard operation chamber 24 side to each advance operation chamber 22 side is caused by the advance recirculation check valve 76. Allowed by valve opening. At this time, in the retarded reflux passage 744 that directly communicates with the advanced reflux passage 742, the retarded reflux check valve 77 is closed and the supply passage 68 communicated with the advanced reflux passage 742 via the supply port 88. Then, the supply check valve 69 is closed. For these reasons, the hydraulic oil discharged from each retarded working chamber 24 to the advanced return passage 742 is returned to each advanced working chamber 22, so that the valve timing is changed by changing the rotational phase advance. The advance angle is adjusted.

  On the other hand, when the respective advance working chambers 22 are compressed by the positive torque transmission as the cam torque whose direction is reversed, the working oil is discharged from each advance working chamber 22 into the advance return passage 742 as indicated by the broken line arrow in FIG. Try to be. At this time, however, the backflow from the advance working chamber 22 side to the retard working chamber 24 side through the advance return passage 742 is restricted by closing the advance return check valve 76. Also at this time, the retarded recirculation check valve 77 is closed in the retarded recirculation passage 744 and the supply check valve 69 is closed in the supply passage 68. For these reasons, the rotational phase that has changed in the advance direction before reversing the direction of the cam torque is less likely to return to the retard direction, so the valve timing can be easily advanced.

(A2) Advance angle operation at the advance angle position Pa during high speed rotation In advance angle operation in which the rotation phase is advanced at the advance angle position Pa in FIG. 2, the rotational speed S of the internal combustion engine is as shown in FIGS. When the set speed Sth or higher is reached, the control valve bodies 780 and 790 move to the respective communication areas Aac and Arc. As a result, the reflux passages 742 and 744 are communicated with the drain passages 746 and 747, respectively.

  Under such a communication state, when each retarded working chamber 24 as a “discharge chamber” is compressed by negative torque transmission of the cam torque, the advanced drain passage 746 communicating with the advanced return passage 742 has a broken line in FIG. As indicated by the arrow, the hydraulic oil in each retarded working chamber 24 is discharged. At this time, in the supply passage 68 communicating with the advance recirculation passage 742, the supply of the hydraulic oil to the supply port 88 side is permitted by opening the supply check valve 69. As a result, in each of the advance angle return passages 742, even if each advance angle working chamber 22 as an “introduction chamber” is expanded by negative torque transmission, the return toward each advance angle working chamber 22 side from each retard angle working chamber 24 side. Is regulated by the closing of the advance / return check valve 76. At this time, the retarded-return check valve 77 is closed in the retarded-return passage 744. For these reasons, the hydraulic oil discharged from each retarded working chamber 24 to the advanced return flow path 742 side is not returned to each advanced advance working chamber 22 and from the return passage 742 to the advanced drain path 746. It is drained to the external drain pan 3 through. At the same time, hydraulic oil supplied at a high pressure following the rotational speed S equal to or higher than the set speed Sth is introduced into each advance angle working chamber 22. Therefore, the valve timing is advanced by changing the advance angle of the rotation phase.

  On the other hand, when the advance working chambers 22 are compressed by the positive torque transmission as the direction reversed cam torque, the backflow from the advance working chamber 22 side to the retard working chamber 24 side as shown by the broken line arrow in FIG. The advance angle recirculation check valve 76 is closed by the advance angle recirculation passage 742. At this time, the retarded recirculation check valve 77 is closed in the retarded recirculation passage 744 and the supply check valve 69 is closed in the supply passage 68. For these reasons, the rotational phase that has changed in the advance direction before reversing the direction of the cam torque is less likely to return to the retard direction, so the valve timing can be easily advanced.

(R1) Delay angle operation at the retard angle position Pr during low speed rotation Even in the retard angle operation in which the rotation phase is retarded at the retard angle position Pr in FIG. 2, the rotational speed S of the internal combustion engine is as shown in FIGS. While the speed is lower than the set speed Sth, the control valve bodies 780 and 790 move to the respective shut-off areas Aai and Ari. As a result, the reflux passages 742 and 744 are blocked from the drain passages 746 and 747, respectively.

  Under such a shut-off state, when each advance working chamber 22 serving as a “discharge chamber” is compressed by transmitting positive torque of the cam torque, each advanced working chamber is provided in the retarded return passage 744 as indicated by the broken line arrow in FIG. The hydraulic oil is discharged from the valve 22 through the advance / inlet passage 62 and the advance / inlet port 82. At this time, each retarded working chamber 24 as an “introducing chamber” expanded by positive torque transmission communicates with the retarded return passage 744 via the retarded inlet / outlet passage 64 and the retarded inlet / outlet port 84. Therefore, from each advance working chamber 22 side to each retard working chamber 24 side, the recirculation through the retarded return passage 744 that is in a state of being blocked with respect to the retarded drain passage 747 is caused by the retarded return check valve 77. Allowed by valve opening. At this time, in the advance reflux path 742 that communicates directly with the retard return path 744, the advance return check valve 76 closes and the supply path 68 communicates with the retard return path 744 via the supply port 88. Then, the supply check valve 69 is closed. From these facts, the hydraulic oil discharged from each advance working chamber 22 to the retard return passage 744 is returned to each retard working chamber 24, so that the valve timing is changed by changing the rotational phase retarded. Delay angle is adjusted.

  On the other hand, when each retarded working chamber 24 is compressed by the negative torque transmission as the direction-reversed cam torque, the hydraulic oil is discharged from each retarded working chamber 24 into the retarded return passage 744 as shown by the broken arrow in FIG. Try to be. However, at this time, the backward flow from the retarding working chamber 24 side to the advanced working chamber 22 side through the retarding return passage 744 is restricted by closing the retarding return check valve 77. Also at this time, the advance return check valve 76 is closed in the advance return path 742 and the supply check valve 69 is closed in the supply path 68. For these reasons, the rotational phase changed in the retarded direction before the cam torque direction reversal becomes difficult to return to the advanced angle direction, so that the valve timing can be easily retarded.

(R2) Delay angle operation at the retard angle position Pr during high speed rotation Even in the retard angle operation in which the rotation phase is retarded at the retard angle position Pr in FIG. 2, the rotational speed S of the internal combustion engine is as shown in FIGS. When the set speed Sth or higher is reached, the control valve bodies 780 and 790 move to the respective communication areas Aac and Arc. As a result, the reflux passages 742 and 744 are communicated with the drain passages 746 and 747, respectively.

  Under such a communication state, when each advance working chamber 22 as the “discharge chamber” is compressed by positive torque transmission among the cam torque, the retard drain passage 747 communicating with the retard return passage 744 has a broken line in FIG. As indicated by the arrow, the hydraulic oil in each advance angle working chamber 22 is discharged. At this time, in the supply passage 68 that communicates with the retarded recirculation passage 744, the supply of the hydraulic oil to the supply port 88 side is permitted by opening the supply check valve 69. As a result, in each of the retarded angle return passages 744, even if each retarded working chamber 24 serving as an “introducing chamber” is expanded by negative torque transmission, the return toward each retarded working chamber 24 side from each advanced angle working chamber 22 side. Is controlled by closing the retarded reflux check valve 77. At this time, the advance return check valve 76 is closed in the advance return passage 742. For these reasons, the hydraulic oil discharged from each advance working chamber 22 to the retarded return passage 744 side is not returned to each retarded working chamber 24, but from the return passage 744 to the retarded drain passage 747. It is drained to the external drain pan 3 through. At the same time, each retarded working chamber 24 is introduced with hydraulic oil supplied at a high pressure following the rotational speed S equal to or higher than the set speed Sth. Therefore, the valve timing is retarded by changing the rotational phase retarded.

  On the other hand, when each retarded working chamber 24 is compressed by the negative torque transmission as the direction-reversed cam torque, the reverse flow from each retarded working chamber 24 side to each advanced working chamber 22 side as shown by the broken line arrow in FIG. The retarded-circulation check valve 77 is regulated by the retarded-reflux passage 744 by closing. At this time, the advance recirculation check valve 76 is closed in the advance recirculation passage 742, and the supply check valve 69 is closed in the supply passage 68. For these reasons, the rotational phase changed in the retarded direction before the cam torque direction reversal becomes difficult to return to the advanced angle direction, so that the valve timing can be easily retarded.

(H) Holding operation at the holding position Ph In the holding operation in which the rotation phase is not changed by the hydraulic oil at the holding position Ph, regardless of the rotational speed S of the internal combustion engine, that is, regardless of the state of the control valve bodies 780, 790. The working chambers 22 and 24 are blocked from the reflux passages 742 and 744 and the supply passage 68 as shown in FIG. As a result, since the hydraulic oil is confined in each of the working chambers 22 and 24, the valve timing is held and adjusted within the range of the rotational phase change due to the influence of the cam torque. At this time, in the supply passage 68 that is in communication with the reflux passages 742 and 744, the supply of the hydraulic oil to the supply port 88 side is permitted as shown by the broken line arrow in FIG. Thus, the return check valves 76 and 77 are closed in the return passages 742 and 744.

(Function and effect)
The effects of the apparatus 1 described above will be described below.

  According to the device 1, at the advance position Pa and the retard position Pr of the spool 74, while the rotational speed S of the internal combustion engine is low and the centrifugal force F is small, the control valve bodies 780 and 790 in the shut-off areas Aai and Ari are used. The reflux passages 742 and 744 are blocked from the drain passages 746 and 747. As a result, in the case of the advance position Pa, the return of hydraulic oil from each retarded working chamber 24 functioning as a “discharge chamber” toward each advanced working chamber 22 functioning as an “introducing chamber”. Is acceptable. In the case of the retard position Pr, the return of the working oil from the respective advance working chambers 22 functioning as “discharge chambers” toward the respective retard working chambers 24 functioning as “introduction chambers”. Is acceptable. In any case, when the centrifugal force F is small, the alternating cycle of the cam torque transmitted from the camshaft 2 to the vane rotor 14 becomes long, and the follow-up performance of the reflux with respect to the alternating cycle becomes sharp. Therefore, even if the introduction pressure into the “introduction chamber” following the rotational speed S of the internal combustion engine is low, the response of the valve timing adjustment can be improved.

  Further, when the rotational speed S increases and the centrifugal force F increases at the advance position Pa and the retard position Pr of the spool 74, the return passages 742 and 744 are caused by the control valve bodies 780 and 790 moved to the communication areas Aac and Arc. Will be in communication with the drain passages 746 and 747. As a result, in the case of the advance position Pa, the hydraulic oil discharged from each retarded working chamber 24 functioning as a “discharge chamber” to the advanced return passage 742 side is advanced by each advance operation functioning as an “introducing chamber”. It is drained to the outside without being refluxed to the chamber 22 side. In the case of the retard position Pr, the hydraulic oil discharged from each advance working chamber 22 functioning as the “discharge chamber” to the retard return path 744 side is used for each retard operation acting as the “introducing chamber”. It is drained to the outside without being refluxed to the chamber 24 side. In either case, when the centrifugal force F increases, the reflux that slows down the follow-up performance with respect to the alternating cycle of the short cam torque is not used, and the “introduction chamber” where the high pressure follows the rotational speed S is used. By utilizing the introduction pressure, the responsiveness of the valve timing adjustment can be improved.

  According to such an apparatus 1, even in a situation where both the advance position Pa and the retard position Pr, which are “specific positions”, and the amount of movement of the spool 74 is limited, the return use position and the non-use position Are made common, so that the range that can be set as the positions Pa and Pr can be expanded. Therefore, the robustness can be enhanced at the same time as the above responsiveness with respect to the hydraulic oil entry / exit control according to the spool movement position, and thus the valve timing adjustment.

  Here, the control valve bodies 780 and 790 whose center of gravity is set closer to the communication areas Aac and Arc than the rotation center O of the sleeve 73 in the shut-off areas Aai and Ari are surely connected to the communication areas Aac and Ari, as the centrifugal force F increases. Can move to Arc. Therefore, the reliability of the effect of improving the responsiveness of the valve timing adjustment can be improved.

  Further, the control valve bodies 780 and 790 that are urged in the radial direction from the communication areas Aac and Arc to the blocking areas Aai and Ari by the urging members 782 and 792 in the sleeve 73 reduce the centrifugal force F. Accordingly, it is possible to reliably return to the blocking areas Aai and Ari. Therefore, this can also improve the reliability of the effect of improving the responsiveness of the valve timing adjustment.

  Furthermore, when the centrifugal force F is small, the recirculation from the “discharge chamber” side compressed by the transmission of the cam torque toward the “introduction chamber” side is performed by the recirculation check valves 76 and 77 and the control valves of the shut-off areas Aai and Ari. Allowed by bodies 780, 790. At the same time, when the centrifugal force F is small, the backflow of the working oil through the reflux passages 742 and 744 tends to occur from the “introducing chamber” side compressed by the transmission of the cam torque reversed in the direction toward the “exhaust chamber” side. Then, the backflow is regulated by the reflux check valves 76 and 77. According to these, when the followability of recirculation and reverse flow becomes sensitive to an alternating cycle with a long cam torque, the introduction time of hydraulic oil to the “introduction chamber” is shortened by allowing recirculation and restricting the reverse flow. The response of the valve timing adjustment can be improved.

  When the centrifugal force F increases, the hydraulic oil in the “discharge chamber” compressed by the transmission of the cam torque is returned to the “introduction chamber” side by the control valve bodies 780 and 790 moved to the communication areas Aac and Arc. Instead, it is drained to the outside. At the same time, when the centrifugal force F increases, the reverse flow of the hydraulic oil from the “introducing chamber” side to the “exhaust chamber” side compressed by the transmission of the cam torque reversed in direction is restricted by the reflux check valves 76 and 77. Is done. According to these, when the follow-up performance of the check valve and the follow-up performance of the recirculation and the reverse flow slow down with respect to the alternating cycle of the short cam torque, the hydraulic oil for the “introduction chamber” is controlled by the high introduction pressure and the restriction of the back-flow. This can shorten the introduction time of the valve and improve the responsiveness of the valve timing adjustment.

(Other embodiments)
Although one embodiment of the present invention has been described above, the present invention is not construed as being limited to the embodiment, and can be applied to various embodiments without departing from the gist of the present invention. it can.

  Specifically, as shown in FIG. 14, in the first modification, the drain passage 737 provided with the advance drain control valve 78 or the retard drain control valve 79 is connected to the advance drain in the sleeve 73 outside the spool 74. You may form so that communication with the channel | path 746 or the retarded angle drain channel | path 747 is possible. In this case, the advance recirculation passage 742 or the retard recirculation passage 744 is connected to the drain passage through the advance drain passage 746 or the retard drain passage 747 in which the advance drain control valve 78 or the retard drain control valve 79 is not provided. 737 is communicated or blocked. FIG. 14 shows Modification 1 in the case where the retard drain control valve 79 is provided in the retard drain passage 737.

  As shown in FIGS. 15 to 18, in Modification 2, by not providing one of the advance drain control valve 78 and the retard drain control valve 79, only one of the advance position Pa and the retard position Pr is set to the “specific position”. It is good also as.

  15 and 16, the retard drain control valve 79 including the retard control valve body 790 and the retard return passage 744 and the retard return check valve 77 are not provided, and the advance reflux is not provided. An elastic member 767 unique to the check valve 76 is interposed between the advance valve member 760 and the spool 74. In this case, the operation at the low speed rotation (a1) as shown by the broken line arrow in FIG. 15 and the operation at the high speed rotation (a2) (not shown) are common advance angle positions as “specific positions”. It can be realized in the same manner as the above embodiment at Pa. Therefore, responsiveness and robustness can be improved at the same time by adjusting the advance angle of the valve timing. In this case, at the retarded angle position Pr at the time of low speed rotation, as shown by the broken line arrow in FIG. 16, the operation according to the high speed rotation (r2) is realized.

  On the other hand, in the modified example 2 of FIGS. 17 and 18, the advance drain control valve 78 including the advance control valve body 780 is not provided, and the advance return passage 742 and the advance return check valve 76 are not provided. An elastic member 767 unique to the stop valve 77 is interposed between the retard valve member 770 and the spool 74. In this case, the operation at the low speed rotation (r1) as shown by the broken line arrow in FIG. 17 and the operation at the time of high speed rotation (r2) (not shown) are common advance angle positions as “specific positions”. It can be realized in the same manner as the above embodiment at Pa. Therefore, responsiveness and robustness can be improved at the same time by adjusting the retardation of the valve timing. In this case, at the advance angle position Pa at the time of low speed rotation, an operation according to the high speed rotation (a2) is realized as shown by a broken line arrow in FIG.

  As shown in FIG. 19, in the third modification, the center of gravity Ca, Cr may be shifted from the center of the dimension by forming the control valve bodies 780, 790 from a plurality of materials having different specific gravities. However, even in this case, it is preferable to set the center of gravity on the side of the communication areas Aac, Arc rather than the rotation center O in the blocking areas Aai, Ari.

  In the fourth modification, for example, another urging member is added so as to urge the control valve bodies 780 and 790 in the direction opposite to the urging members 782 and 792, so that the center of rotation O in the blocking regions Aai and Ari. The center of gravity may be set on the opposite side of the communication areas Aac and Arc across the radial direction. In the fifth modification, at least one of the check valves 69, 76, and 77 may not be provided.

  As shown in FIGS. 20 and 21, in the sixth modification, the retarded working chambers 24 as the “discharge chambers” or the respective advancement positions are provided outside the control valve bodies 780 and 790 that are not provided with the biasing members 782 and 792 in the radial direction. A part of the hydraulic oil may be discharged from the corner working chamber 22. In this case, the control valve bodies 780 and 790 can be returned to the shut-off areas Aai and Ari by the pressure of the hydraulic oil discharged to the outside in the radial direction of the control valve bodies 780 and 790.

  In the modified example 7, the present invention may be applied to a device that adjusts the valve timing of the exhaust valve as the “valve”, and a device that adjusts the valve timing of both the intake valve and the exhaust valve as the “valve”. .

1 Valve timing adjusting device, 2 cam shaft, 3 drain pan, 4 pump, 10 rotation mechanism system, 12 housing rotor, 14 vane rotor, 22 advance working chamber, 24 retard working chamber, 50 control system, 66 drain collecting passage, 70 Control valve unit, 73 sleeve, 74 spool, 76 advance return check valve, 77 retard return check valve, 78 advance drain control valve, 79 retard drain control valve, 742 advance return passage, 744 retard return Passage, 746 advance angle drain passage, 747, 737 retard angle drain passage, 780 advance angle control valve body, 782 advance angle biasing member, 790 delay angle control valve body, 792 retard angle biasing member, Aac advance angle communication region, Aai advance angle blocking area, Arc retard angle communication area, Ari retard angle blocking area, Ca, Cr center of gravity, F centrifugal force, O rotation center, Pa advance angle position, P Retard position, S rotation speed, Sth set speed

Claims (4)

A housing rotor (12) rotating in conjunction with a crankshaft of the internal combustion engine;
It rotates in conjunction with the camshaft (2) of the internal combustion engine, divides a plurality of working chambers (22, 24) in the rotation direction in the housing rotor, and rotates with respect to the housing rotor by entering and exiting the working fluid into each working chamber. A vane rotor (14) whose phase is adjusted;
A control system (50) for controlling entry / exit of the hydraulic fluid into / from each of the working chambers according to a moving position of the spool (74) in the sleeve (73),
A valve timing adjusting device for adjusting a valve timing of a valve that opens and closes the camshaft by torque transmission from the crankshaft;
When the moving position for changing the rotational phase by advance is defined as an advanced position (Pa), the moving position for changing the rotational phase by delay is defined as a retard position (Pr).
An introduction chamber as the working chamber for introducing the hydraulic fluid with a pressure following the rotational speed (S) of the internal combustion engine, and a discharge chamber as the working chamber for discharging the hydraulic fluid, the advance position and The control system for switching and selecting at each of the retard angle positions,
A reflux passage (742, 744, 737) for refluxing the working fluid from the discharge chamber side to the introduction chamber side at a specific position that is at least one of the advance position and the retard position;
Drain passages (746, 747, 66) for draining the hydraulic fluid discharged from the discharge chamber to the reflux passage side under communication with the reflux passage;
A control valve body (780, 790) that reciprocates in the radial direction within the sleeve that rotates integrally with the vane rotor, from a blocking region (Aai, Ari) that blocks the reflux path from the drain path. And a control valve body that moves in response to an increase in centrifugal force (F) to a communication region (Aac, Arc) that communicates the reflux passage with the drain passage. .   2. The valve timing adjusting device according to claim 1, wherein a center of gravity (Ca, Cr) of the control valve body is set closer to the communication region than a rotation center (O) of the sleeve in the blocking region. . The control system is
The biasing member (782, 792) for biasing the control valve body in a radial direction from the communication region side to the blocking region side in the sleeve is provided. Valve timing adjustment device. The control system is
While the working fluid allows the working fluid to reflux from the discharge chamber side to the introduction chamber side through the reflux passage, the working fluid regulates the reverse flow from the introduction chamber side to the discharge chamber side through the reflux passage. The valve timing adjusting device according to any one of claims 1 to 3, further comprising a stop valve (76, 77).

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