JP2011094533A - Valve timing variable device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing variable device with a restriction pin for restricting a valve timing changeable range projected in an early stage. <P>SOLUTION: This valve timing variable device is so configured that when the restriction pin is projected from a storage hole, the cross-sectional area of an oil passage for discharging hydraulic fluid pressing the restriction pin to the storage hole is increased. By such a structure, time required for setting pressing force by the hydraulic fluid weaker than urging force for urging the restriction pin in a projecting direction is shortened. Therefore, the restriction pin is projected in an early stage. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a variable valve timing device.

  As is well known, as a device applied to an internal combustion engine such as a vehicle, a variable valve timing device that changes the valve timing of an engine valve such as an intake valve or an exhaust valve by changing the rotational phase of a camshaft with respect to a crankshaft. Has been put to practical use. The variable valve timing device includes a variable valve timing mechanism having a first rotating body that is drivingly connected to the crankshaft and a second rotating body that is drivingly connected to the camshaft. The relative rotation phase of the camshaft with respect to the crankshaft is changed by relatively rotating the first rotating body and the second rotating body using hydraulic pressure or the like, whereby the valve timing is changed. .

  Further, a variable valve timing device having a limiting mechanism for limiting the changeable range of the valve timing according to the operating state has been studied. As such a limiting mechanism, the limiting pin protrudes from one rotating body to the other rotating body among the first rotating body drivingly connected to the crankshaft and the second rotating body drivingly connected to the camshaft. It is conceivable that the limiting pin protrudes to a restricting portion provided on the other rotating body so that the relative rotation of both rotating bodies is limited.

  More specifically, the limiting mechanism is controlled as follows. That is, the limiting pin is urged by the urging means so as to protrude from the accommodating portion to the restricting portion, and is pressed by hydraulic pressure so as to be accommodated in the accommodating portion against this urging force. The pressing force at this time is generated by supplying hydraulic pressure to a pin hydraulic chamber formed in the variable valve timing device. That is, when the urging force by the urging means is larger than the pressing force by the hydraulic pressure, the limit pin protrudes to the restricting portion. Thereby, the relative rotation between the first rotating body and the second rotating body is limited, and the changeable range of the valve timing is limited.

Japanese Patent Laid-Open No. 2001-41012

  In the limiting mechanism as described above, although there is a request for protrusion of the limiting pin, it takes time to protrude the limiting pin if the pressing force is large. For this reason, there is a possibility that the execution of the valve timing may be delayed even though there is a request to limit the changeable range of the valve timing.

  The present application has been made in view of such circumstances, and an object thereof is to provide a variable valve timing device that can quickly limit the changeable range of the valve timing.

  In the following, means for achieving the above object and its effects are described.

According to the first aspect of the present invention, the relative rotation phase between the first rotating body that is drivingly connected to the crankshaft of the internal combustion engine and the second rotating body that is drivingly connected to the camshaft that opens and closes the engine valve is hydraulically controlled. A variable valve timing mechanism for changing the valve timing of the engine valve by changing the first and second rotating bodies, and a movable body housed in a housing portion formed on one of the first rotating body and the second rotating body. The relative rotation between the first rotating body and the second rotating body is set between the relative rotatable range by projecting to the restricting portion formed on the other of the rotating body and the second rotating body. A variable valve timing device including a rotation limiting mechanism for limiting to a rotation limiting phase, wherein the rotation limiting mechanism moves the moving body from the one rotating body provided with the housing portion to the other rotation. An urging unit that urges the body toward the body; and a deregulation hydraulic chamber that presses the moving body in a direction against the urging unit when hydraulic oil is supplied. When the movable body protrudes from the housing portion, the movable body is housed in the housing portion when a cross-sectional area of the oil passage communicating with the hydraulic chamber and discharging hydraulic oil in the deregulated hydraulic chamber is discharged. The valve timing variable device is configured to increase as compared with the time when the valve timing is increased.
Further, the invention according to claim 2 is the valve timing variable device according to claim 1, wherein the valve timing variable mechanism has at least one concave portion therein, and the first rotating body and the second rotating body. And the other of the first rotating body and the second rotating body, the vane partitioning the recess into a first hydraulic chamber and a second hydraulic chamber, and the restriction release hydraulic chamber and the first A cross-sectional area of an oil passage that communicates at least one of the hydraulic chamber, the second hydraulic chamber, and the restricting portion and discharges the hydraulic oil in the restriction-released hydraulic chamber is such that the movable body protrudes from the accommodating portion. The gist of the invention is that the moving body is configured to increase when the mobile body is housed in the housing portion.

  According to the above configuration, when the relative rotation between the first rotating body and the second rotating body is limited, that is, when the limiting pin is projected, compared to when the limiting pin is stored in the storage portion, The cross-sectional area of the oil passage through which the hydraulic oil in the regulation release hydraulic chamber is discharged is increased. Therefore, when the limit pin is protruded, the hydraulic oil in the restriction release hydraulic chamber is easily removed. As a result, the pressing force applied to the limit pin in the direction of the accommodating portion is quickly reduced, the limit pin is projected to the engagement portion at an early stage, and the changeable range of the valve timing is limited at an early stage.

Sectional drawing which shows the structure of an internal combustion engine provided with the apparatus about embodiment which actualized the control apparatus of the valve timing variable apparatus of this invention. (A) is a top view which shows the structure, (b) is sectional drawing which follows the DA-DA line, (c) is sectional drawing which follows the DB-DB line about the valve timing variable apparatus of the embodiment. The schematic diagram which shows the hydraulic pressure supply path | route of the embodiment. About the valve timing variable apparatus of the embodiment, (a) is a cross-sectional view when the relative rotational phase of the vane rotor is in a phase retarded from the restricting portion, and (b) is a state in which the limit pin is fitted in the ratchet groove. Sectional drawing at the time, (c) is a sectional view when the limiting pin is fixed to the locking hole.

  DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, an embodiment embodying a valve timing variable device according to the present invention will be described with reference to FIGS.

  As shown in FIG. 1, the internal combustion engine 1 includes an engine body 10 that rotates a crankshaft 16 through combustion of a mixture of intake air and fuel, a hydraulic mechanism 60 that supplies hydraulic oil to the engine body 10, and There is provided a control device 100 that comprehensively controls various devices including the device.

  A combustion chamber 14 for burning the air-fuel mixture is formed in the cylinder block 11 of the engine body 10. The linear motion of the piston 15 accompanying the combustion of the air-fuel mixture is converted into the rotational motion of the crankshaft 16. A cylinder head 13 on which valve-operated parts are arranged is attached to the upper part of the cylinder block 11.

  The cylinder head 13 includes an intake valve 21 that opens and closes the combustion chamber 14 with respect to the intake passage, an intake camshaft 22 that drives the valve in the valve opening direction, an exhaust valve 23 that opens and closes the combustion chamber 14 with respect to the exhaust passage, and An exhaust camshaft 24 that drives the valve in the valve opening direction is provided. Further, a variable valve timing device 3 that includes a variable valve timing mechanism 30 and a hydraulic mechanism 60 and changes the valve timing of the intake valve 21 is also provided.

  An oil pan 12 that stores hydraulic oil supplied to each part of the internal combustion engine 1 is attached to the lower part of the cylinder block 11. The hydraulic oil stored in the oil pan 12 is supplied to each supply part including the variable valve timing mechanism 30 via the hydraulic mechanism 60. The hydraulic oil discharged from the variable mechanism 30 is returned to the oil pan 12 again via the hydraulic mechanism 60.

  The control device 100 includes various sensors that monitor engine operating conditions, that is, various sensors including a crank position sensor 102 and a cam position sensor 103, and an electronic control device that controls the operation of each device based on outputs from these sensors. 101 is provided. The crank position sensor 102 is provided in the vicinity of the crankshaft 16 and outputs a signal corresponding to the engine rotational speed NE. The cam position sensor 103 is provided in the vicinity of the intake camshaft 22 and outputs a signal corresponding to the rotation angle of the shaft 22.

  The electronic control device 101 performs various controls such as valve timing control for adjusting the valve timing. In the valve timing control, a target value for valve timing is set based on the engine operating state (engine load and engine speed NE). Then, the valve timing variable mechanism 30 is controlled via the hydraulic mechanism 60 so that the valve timing calculated based on the outputs of the crank position sensor 102 and the cam position sensor 103 matches the target value.

  The configuration of the variable valve timing mechanism 30 will be described with reference to FIG. 2A shows a planar structure of the variable mechanism 30 with the cover 34 shown in FIGS. 2B and 2C removed from the housing body 32. FIG. In FIG. 2A, an arrow RA indicates the rotation direction of the intake camshaft 22 and the sprocket 33 (hereinafter referred to as “rotation direction RA”).

  As shown in FIG. 2A, the variable valve timing mechanism 30 is synchronized with the housing rotor 31 that rotates in synchronization with the crankshaft 16 and the end of the intake camshaft 22 to be synchronized with the shaft 16. And the rotating vane rotor 35. The housing rotor 31 constitutes the first rotating body, and the vane rotor 35 constitutes the second rotating body.

  The housing rotor 31 is connected to the crankshaft 16 through a timing chain (not shown), and rotates in synchronization with the shaft 16. The housing rotor 31 is assembled inside the sprocket 33 to be integrated therewith. The housing body 32 is rotated in a manner, and the cover 34 is attached to the body 32.

  The vane rotor 35 is disposed in a space within the housing main body 32 and is accommodated in a space formed by the main body 32 and the cover 34.

  The housing main body 32 is provided with three partition walls 31A that protrude toward the vane rotor 35 in the radial direction. The vane rotor 35 is provided with three vanes 36 that project toward the housing body 32 and divide the three vane storage chambers 37 between the partition walls 31A into an advance chamber 38 and a retard chamber 39, respectively.

  The advance chamber 38 is located behind the vane 36 in the rotation direction RA of the intake camshaft 22 in one vane storage chamber 37, and is used for the hydraulic timing of the valve timing variable mechanism 30 by the hydraulic mechanism 60. The volume changes according to the supply / discharge state. The retarding chamber 39 is positioned in front of the vane 36 in the rotational direction RA of the intake camshaft 22 in one vane accommodating chamber 37, and the valve timing variable mechanism by the hydraulic mechanism 60 is the same as the advance chamber 38. The volume changes according to the hydraulic oil supply / discharge state of 30.

  The variable valve timing mechanism 30 changes the valve timing by changing the relative rotational phase of the vane rotor 35 with respect to the housing rotor 31 based on the above configuration. Specifically, the change of the valve timing by the variable mechanism 30 is performed as follows.

  By supplying the hydraulic oil to the advance chamber 38 through the advance oil passage 74 and discharging the hydraulic oil from the retard chamber 39 through the retard oil passage 75, the vane rotor 35 is advanced from the housing rotor 31. When the intake camshaft 22 rotates in the rotation direction RA, the valve timing changes to the advance side. When the vane rotor 35 rotates to the advance side with respect to the housing rotor 31, that is, when the rotation phase of the vane rotor 35 is at the most advanced phase, the valve timing is set to the most advanced timing.

  By discharging hydraulic oil from the advance chamber 38 through the advance oil passage 74 and supplying hydraulic oil to the retard chamber 39 through the retard oil passage 75, the vane rotor 35 is retarded from the housing rotor 31. When the intake camshaft 22 rotates rearward in the rotational direction RA, the valve timing changes to the retard side. When the vane rotor 35 rotates to the retard side to the limit with respect to the housing rotor 31, that is, when the rotational phase of the vane rotor 35 is at the most retarded phase, the valve timing is set to the most retarded timing.

  The flow of hydraulic oil between each of the advance chamber 38 and the retard chamber 39 and the hydraulic mechanism 60 is blocked, that is, the hydraulic oil is held in each of the advance chamber 38 and the retard chamber 39. Thus, when the relative rotation between the housing rotor 31 and the vane rotor 35 is disabled, the valve timing is maintained at that timing.

  With reference to FIG. 3, the distribution structure of the hydraulic fluid between the variable valve timing mechanism 30 and the hydraulic mechanism 60 will be described. FIG. 3 schematically shows the configuration of the oil passage between these devices.

  The hydraulic oil stored in the oil pan 12 is pumped up to the oil pump 61 via the suction oil passage 71. The hydraulic oil discharged from the oil pump 61 is supplied to each part including the variable valve timing mechanism 30.

  The oil pan 12 and the oil pump 61 are connected by the suction oil passage 71, and the oil pump 61 and the oil control valve 63 are connected by a first supply oil passage 72. The oil control valve 63 and the oil pan 12 are connected by a first discharge oil passage 73, and the oil control valve 63 and the advance chamber 38 are connected by an advance oil passage 74. The oil control valve 63 and the retard chamber 39 are connected by a retard oil passage 75, and the oil control valve 63 and a pin hydraulic chamber 45 to be described later are connected by a limiting oil passage 76.

  The oil control valve 63 switches the connection between the first supply oil passage 72 and the first discharge oil passage 73, the advance oil passage 74, the retard oil passage 75, and the restriction oil passage 76, thereby moving the advance chamber 38 and The supply / discharge state of the hydraulic oil to the retard chamber 39 and the pin hydraulic 45 is changed.

  The variable valve timing device 3 is provided with a rotation limiting mechanism 40 that limits the relative rotation range of the vane rotor 35.

  The rotation restricting mechanism 40 operates based on the supply of hydraulic oil from the hydraulic mechanism 60, and restricts the relative rotation between the housing rotor 31 and the vane rotor 35 to restrict the valve timing to the rotation restricting range.

Specifically, as shown in FIG. 2B, a limit pin 42 (which constitutes the moving body) provided on the vane 36 and moving with respect to the vane 36, and also provided on the vane 36. A housing hole 44 (which constitutes the housing portion) through which hydraulic oil is supplied and discharged by the hydraulic mechanism 60, and a biasing spring which is also provided in the vane 36 and biases in a direction in which the limiting pin 42 protrudes from the housing hole 44. 43 (which constitutes the biasing means) and a restricting portion 55 provided on the housing rotor 31. The limit pin 42 is biased so as to protrude to the restricting portion 55 by providing one end of the bias spring 43 so as to come into contact with the upper end portion 46 of the limit pin 42 in a compressed state. Further, as shown in FIG. 2C, the restriction portion 55 is provided so as to follow the locking hole 41 and the circumferential locus of the limiting pin 42 from the locking hole 41 to a predetermined position on the retard side. The ratchet groove 50 is shallower than the locking hole 41 formed. When the limit pin 42 is fitted in the locking hole 41, the relative rotation between the housing rotor 31 and the vane rotor 35 is locked, that is, the valve timing is fixed. The relative rotational phase of the variable valve timing mechanism 30 at this time is referred to as an intermediate lock phase.
Therefore, when the limit pin 42 is inserted into the restricting portion 55, the changeable range of the valve timing is between the intermediate lock phase and the phase where the ratchet groove 50 on the retard side from the intermediate lock phase is provided. Restricted to the corresponding valve timing range.

  The limit pin 42 is a vane based on the relationship between the pressing force by the hydraulic oil supplied to the pin hydraulic chamber 45 (which constitutes the restriction release hydraulic chamber) through the limit oil passage 76 and the biasing force of the biasing spring 43. It operates between a direction protruding from 36 and a direction retracting into vane 36. Specifically, the pressing force by the hydraulic pressure of the pin hydraulic chamber 45 acts on the limit pin 42 in the accommodation direction Z1. Further, the biasing force of the biasing spring 43 acts on the limit pin 42 in the protruding direction Z2. The pin hydraulic chamber 45 refers to a space in the accommodation hole 44 where the restriction oil passage 76 is located among the spaces partitioned by the restriction pin 42.

  Next, the operation of the rotation limiting mechanism 40 will be described. When hydraulic oil is discharged from the pin hydraulic chamber 45 by the hydraulic mechanism 60 and the pin hydraulic chamber 45 is not filled with hydraulic oil, the urging force in the protruding direction by the urging spring 43 is pushed in the housing direction by the hydraulic oil in the pin hydraulic chamber 45. It will exceed the pressure. As a result, the limit pin 42 can be protruded from the accommodation hole 44. Conversely, when hydraulic oil is supplied to the pin hydraulic chamber 45 by the hydraulic mechanism 60 and the pin hydraulic chamber 45 is filled with hydraulic oil, the pressing force in the accommodation direction by the hydraulic oil in the pin hydraulic chamber 45 is biased by the urging spring 43. It exceeds the biasing force in the protruding direction by. As a result, the limit pin 42 is accommodated in the accommodation hole 44.

Here, in the present embodiment, when the limit pin 42 is projected, the cross-sectional area of the oil passage through which the hydraulic oil in the pin hydraulic chamber 45 is discharged is larger than when the limit pin 42 is accommodated in the accommodation hole 44. It is configured to increase. This will be specifically described below.
When the relative rotational phase of the vane rotor 35 is at a retarded angle phase with respect to the restricting portion 55 (see FIG. 4A), hydraulic oil is supplied to the advance chamber 38 by the hydraulic mechanism 60, while the pin hydraulic pressure The hydraulic oil is discharged from the chamber 45 and the retarded angle chamber 39. At this time, for example, when the viscosity of the hydraulic oil in the pin hydraulic chamber 45 is high, it takes time to discharge the hydraulic oil through the pin oil passage 76. As a result, it takes time for the urging force in the protruding direction applied to the limiting pin 42 by the urging spring 43 to exceed the pressing force in the accommodating direction applied to the limiting pin 42 by the hydraulic oil in the pin hydraulic chamber 45. It takes time to protrude. For this reason, there is a possibility that the restriction on the relative rotation of the variable valve timing mechanism 30 is not immediately executed.
Here, in the present embodiment, the shape of the limiting pin 42 is formed as follows. That is, when the limiting pin 42 is accommodated in the accommodation hole 44, the lower end portion 47 formed in the protruding direction of the pin 42 and the opening portion of the accommodation hole 44 have substantially the same plane while leaving a slight clearance. It is fitted to make up. Thereby, the limiting pin 42 can slide in the protruding direction from the accommodation hole 44, and the hydraulic oil in the pin hydraulic chamber 45 is suppressed from leaking to the outside of the hydraulic chamber 45. The upper portion of the lower end portion 47 of the limiting pin 42 is formed to be narrower than the lower end portion 47. Therefore, as shown in FIG. 4B, when the lower end portion 47 of the limiting pin 42 protrudes from the receiving hole 44, a gap is generated between the opening of the receiving hole 44 and the limiting pin 42. From this gap, The hydraulic oil in the hydraulic chamber 45 is discharged to the restricting portion 55. That is, the cross-sectional area of the oil passage from which the hydraulic oil is discharged increases by adding the clearance to the cross-sectional area of the restriction oil passage 76.
As shown in the figure, when the limit pin 42 protrudes into the ratchet groove 50, the restricting portion 55 communicates with the retard chamber 39, and the hydraulic oil discharged from the pin hydraulic chamber 45 is retarded. It flows into the chamber 39.
As a result, the operating hydraulic pressure in the pin hydraulic chamber 45 is discharged early, and the limiting pin 42 protrudes to the restricting portion 55, so that the relative rotation of the variable valve timing mechanism 30 is limited early. Even when the cross-sectional area of the oil passage from which the hydraulic oil in the pin hydraulic chamber 45 is discharged is the largest, the restriction pin 42 is accommodated by the hydraulic oil supplied from the restriction oil passage 76 and other oil passages. The cross-sectional area and the like of each oil passage are adjusted so as to move in the direction of the hole 44.
In FIG. 4B, the limit pin 42 protrudes from the accommodation hole 44 and fits into the ratchet groove 50, whereby the vane rotor 35 is in a state where relative rotation to the retard side is limited. Thereafter, when the vane rotor 35 further rotates relative to the advance side, the limit pin 42 protrudes, whereby the limit pin 42 and the locking hole 41 are engaged with each other as shown in FIG. 31 and the vane rotor 35 are fixed to each other. That is, the relative rotational phase of the vane rotor 35 with respect to the housing rotor 31 is held (fixed) at the intermediate lock phase.
Even when the hydraulic control of the variable valve timing mechanism 30 and the intermediate lock mechanism 40 is impossible, the limit pin 42 projects into the restricting portion 55 as follows when the engine is started.

First, when the engine is started and cranking is started, the housing rotor 31 to which the sprocket 33 is fixed is rotated in the direction of arrow A shown in FIG. At this time, since the hydraulic pressure in the retard chamber 39 and the advance chamber 38 is reduced, the vane rotor 35 is rotated relative to the housing rotor 31 to the position of the most retarded phase. When the vane rotor 35 relatively rotates to the most retarded angle phase in this way, the rotation of the housing rotor 31 is also transmitted to the vane rotor 35 and the rotation of the intake camshaft 22 is started.
When the rotation of the intake camshaft 22 is started, alternating torque on the advance side and the retard side is generated on the intake camshaft 22 by the reaction force from the valve spring that urges the intake valve 21. By this alternating torque, the vane rotor 35 is swung to the advance side and the retard side with respect to the housing rotor 31. When the vane rotor 35 is swung to the advance side, the limit pin 42 fits into the ratchet groove 50.
When the alternating torque is applied again to the intake camshaft 22 in this state, the vane rotor 35 is restricted from rotating in the retarded direction by the engagement of the ratchet groove 50 and the limit pin 42. Therefore, it is further rotated only to the advance side, and finally the limit pin 42 is fitted into the restricting portion.
In this way, in the variable valve timing device 3, even when the valve timing cannot be fixed to the intermediate lock phase by hydraulic control, the relative rotation of the vane rotor 35 using the alternating torque of the intake camshaft 22 during cranking is achieved. Thus, the valve timing is fixed to the intermediate lock phase when the engine is started. Also at this time, the restriction pin 42 protrudes from the accommodation hole 44, thereby generating a gap between the opening of the accommodation hole 44 and the restriction pin 42, from which the hydraulic oil in the pin hydraulic chamber 45 is It is discharged to the regulation part 55. That is, the cross-sectional area of the oil passage from which the hydraulic oil can be discharged is increased by adding the gap in addition to the cross-sectional area of the restriction oil passage 76. In addition, the fluttering of the vane rotor 35 is suppressed by starting with the valve timing fixed to the intermediate lock phase in this way.

According to the control device for a variable valve timing device according to the present embodiment described above, the following effects can be obtained.
(1) When the limiting pin 42 protrudes from the accommodation hole 44, the cross-sectional area of the oil passage through which the hydraulic oil in the pin hydraulic chamber 45 is discharged is increased compared to when the limiting pin 42 does not protrude. Thereby, when there is a request for protrusion of the limit pin 42, the limit pin 42 can be protruded early, and the changeable range of the valve timing can be limited early. Further, with the above configuration, when a start request is made in a state where the limit pin is not in the intermediate lock phase, the limit pin 42 is inserted into the locking hole 41 early and reliably during cranking. Thereby, the engine is started while the flutter of the vane rotor 35 is suppressed.
(2) By making the upper portion of the lower end portion 47 of the limiting pin 42 thinner than the lower end portion 47, when the pin 42 protrudes from the accommodation hole 44, the hydraulic oil flows from the pin hydraulic chamber 45 to the restriction portion 55. It is trying to be discharged. With this configuration, for example, a complicated configuration such as providing a valve that adjusts the opening degree of the restriction oil passage 76 in accordance with the protruding state of the restriction pin 42 is provided. The discharge of hydraulic oil can be promoted.

  In addition, this embodiment can also be changed and implemented as follows.

  The side surface of the lower end portion 47 of the limiting pin 42 and the opening of the accommodation hole 44 may be tapered. By making these tapered, when the restriction pin 42 is returned to the accommodation hole 44, there is a possibility that the lower end portion 47 and the opening of the accommodation hole 44 are caught and the restriction pin 42 cannot be accommodated in the accommodation hole 44. It is suppressed.

  In this embodiment, the hydraulic oil in the pin hydraulic chamber 45 is discharged from the gap between the lower end portion 47 of the control pin 42 and the opening of the accommodation hole 44. However, the hydraulic oil is sufficiently discharged only from the gap. There are cases where it cannot be discharged. Therefore, for example, an opening / closing valve that opens in conjunction with the protrusion of the control pin is provided on the side surface of the accommodation hole 44 so that the hydraulic oil is discharged from the opening / closing valve to the advance chamber 38 or the retard chamber 39. It may be.

  In the present embodiment, the hydraulic oil in the pin hydraulic chamber 45 is discharged from the gap between the lower end portion 47 of the control pin 42 and the opening of the accommodation hole 44. There may be a case where it is not preferable to flow into the corner chamber 39 and the restriction portion 55. Therefore, a throttle valve may be provided in the restriction oil passage 76 and the opening degree of the throttle valve may be increased when the control pin 42 is protruded, that is, when the hydraulic oil is discharged. By controlling the throttle valve as described above, the amount of hydraulic oil removed from the restricted oil passage 76 is increased, so that the effect (1) can be obtained.

  In the present embodiment, the limit pin 42 is projected from the accommodation hole 44 using the biasing force of the biasing spring 43. In addition, the biasing spring 43 may be omitted, and the limiting pin 42 may be protruded from the accommodation hole 44 by supplying hydraulic pressure.

  The second rotor that is drivingly connected to the intake camshaft 22 may be the housing rotor 31, and the first rotor that is drivingly connected to the crankshaft 16 may be the vane rotor 35.

  In the present embodiment, the limiting pin 42 protrudes from the vane rotor 35 in the central axis direction of the vane rotor 35, but may be protruded in a direction perpendicular to the central axis of the vane rotor 35. Further, the limit pin 42 may protrude from the housing rotor 31 to the vane rotor 35.

  The present invention can be similarly applied even when the variable valve timing device 50 is provided on the exhaust camshaft 24.

  DESCRIPTION OF SYMBOLS 1 ... Internal combustion engine, 3 ... Valve timing variable apparatus, 10 ... Engine main body, 11 ... Cylinder block, 12 ... Oil pan, 13 ... Cylinder head, 14 ... Combustion chamber, 15 ... Piston, 16 ... Crankshaft, 21 ... Intake valve , 22 ... intake camshaft, 23 ... exhaust valve, 24 ... exhaust camshaft, 30 ... variable valve timing mechanism, 31 ... housing rotor, 31A ... partition wall, 32 ... housing body, 33 ... sprocket, 34 ... cover, 35 ... Vane rotor, 36 ... Vane, 37 ... Vane housing chamber, 38 ... Advancing chamber, 39 ... Delay chamber, 40 ... Rotation limiting mechanism, 41 ... Locking hole, 42 ... Limiting pin, 43 ... Biasing spring, 44 ... Housing Hole, 45 ... Pin hydraulic chamber, 46 ... Upper end, 47 ... Lower end, 50 ... Ratchet groove, 55 ... Regulator, 60 ... Hydraulic mechanism, 61 ... Oil pump 63 ... Oil control valve, 70 ... Oil passage, 71 ... Suction oil passage, 72 ... First supply oil passage, 73 ... First discharge oil passage, 74 ... Advance oil passage, 75 ... Delay oil passage, 76 ... Restriction Oil passage.

Claims (2)

By changing the relative rotational phase of the first rotating body drivingly connected to the crankshaft of the internal combustion engine and the second rotating body drivingly connected to the camshaft for opening and closing the engine valve by hydraulic control, the engine valve A variable valve timing mechanism that makes the valve timing variable, and a moving body that is accommodated in an accommodating portion that is formed on one of the first rotating body and the second rotating body are the first rotating body and the second rotating body. A rotation limiting mechanism that limits the relative rotation between the first rotating body and the second rotating body to a rotation limiting phase set between the relative rotatable ranges by projecting to a restricting portion formed on the other side. A variable valve timing device comprising:
The rotation limiting mechanism includes an urging unit that urges the moving body from the one rotating body provided with the housing portion toward the other rotating body, and hydraulic fluid supplied to the moving body. A deregulation hydraulic chamber that is pressed in a direction against the biasing means,
When the movable body protrudes from the housing portion, the movable body communicates with the housing portion, and the cross-sectional area of the oil passage that communicates with the unregulated hydraulic chamber and discharges the hydraulic oil in the unrestricted hydraulic chamber is A valve timing variable device configured to increase as compared with when it is accommodated. The variable valve timing mechanism has at least one recess inside, and has one of the first rotating body and the second rotating body, and a vane that divides the recess into a first hydraulic chamber and a second hydraulic chamber. , Comprising the other of the first rotating body and the second rotating body,
A cross-sectional area of an oil passage that communicates at least one of the restriction release hydraulic chamber, the first hydraulic chamber, the second hydraulic chamber, and the restriction portion and that discharges hydraulic oil in the restriction release hydraulic chamber is the movement. 2. The valve timing according to claim 1, wherein when the body protrudes from the housing portion, the valve timing is configured to increase compared to when the moving body is housed in the housing portion. Variable device.

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