JP6497430B2 - Valve timing control device - Google Patents

Description

  The present invention relates to a valve opening / closing timing control device, and more specifically, a drive-side rotator that rotates in synchronization with a crankshaft of an internal combustion engine, a driven-side rotator that is fixed to a camshaft by a connecting bolt that is coaxial with a camshaft, The present invention relates to an improvement in a valve opening / closing timing control device having a fluid control spool housed in a connecting bolt.

  In Patent Literature 1, as a valve opening / closing timing control device configured as described above, a driving side rotating body (a rotation transmitting member in the literature) and a driven side rotating body (a rotating member in the literature) are arranged on a coaxial core, A configuration is shown in which a spool valve is movably supported in the axial direction inside a connecting bolt (a mounting bolt in the literature) that connects the rotor to the camshaft.

  In Patent Document 1, an electromagnetic drive mechanism for moving the spool valve is provided outside the driven-side rotating body, and fluid controlled by the operation of the spool valve is allowed to flow from the outer peripheral surface of the mounting bolt to the advance chamber and the retard chamber. The relative rotation phase of the valve opening / closing timing control device is set and the valve opening / closing timing is set.

  Patent Document 2 shows a solenoid valve having a spool and a sleeve that movably accommodates the spool, which is provided outside the valve opening / closing timing control device. In this solenoid valve, a first port through which fluid is supplied to the sleeve, and a second port and a third port communicating with the valve opening / closing timing control device are formed. In addition, the outer peripheral surface of the sleeve is shaped so that the cross-sectional shape is substantially D-shaped, and a communication path that connects the first port, the second port, and the third port is formed.

  In Patent Document 2, a holding operation for holding the valve opening / closing timing control device at an intermediate phase is ensured by supplying fluid from the first port to the second port and the third port.

Japanese Patent No. 4013364 Japanese Patent No. 4032284

  In the configuration in which the spool is housed inside as described in Patent Document 1, it is possible to control the fluid supply / discharge to the advance chamber and the retard chamber from the inside of the valve opening / closing timing control device, and the components of the fluid control system The number of points is reduced and the valve timing control device is downsized.

  The valve opening / closing timing control device sets a relative rotation phase by selectively supplying fluid to an advance chamber and a retard chamber by a control valve. However, in the valve timing control device, for example, the fluid slightly leaks from the advance chamber and the retard chamber during phase control. Therefore, even when the situation where the spool is in the neutral position continues, the valve opening / closing timing control device rotates, so that the fluid in the advance chamber and the retard chamber leaks due to the action of centrifugal force, etc. The relative rotational phase may fluctuate greatly (so-called fluttering) due to cam fluctuation torque acting from the camshaft.

  On the other hand, if the advance chamber and retard chamber are filled with fluid, the relative rotation phase of the valve opening / closing timing control device can be easily maintained even when cam fluctuation torque is applied, and the valve opening / closing timing varies greatly. Never do.

  As engine oil is used as the hydraulic oil for the valve timing control device, especially when the engine temperature rises and the viscosity of the hydraulic oil decreases, the amount of hydraulic oil leaks from the advance chamber and retard chamber Increases and the phase holding becomes unstable.

  With respect to such a problem, in the configuration of Patent Document 2, it is possible to supply fluid (hydraulic oil) to the advance chamber and the retard chamber regardless of the set position of the spool, and to suppress the occurrence of fluttering or the like. Is possible.

  However, in the case where the communication path is formed on the outer periphery of the sleeve as described in Patent Document 2, not only the fluid viscosity decreases and the fluid flow rate increases as the fluid temperature rises, but also the spool, As a result of the expansion of the member that accommodates the spool, the cross-sectional area of the communication passage is increased, and the flow rate of the fluid is further increased.

  An object of the present invention is to rationally configure a valve opening / closing timing control device capable of suppressing fluctuations in the relative rotational phase even when the amount of fluid leakage increases from the advance chamber and the retard chamber as the temperature rises. is there.

A characteristic configuration of the valve timing control apparatus according to the present invention includes a driving side rotating body that rotates synchronously with a crankshaft of an internal combustion engine,
A driven-side rotating body fixed to the camshaft so as to rotate integrally with the camshaft for opening and closing the valve;
An advance chamber and a retard chamber formed by the drive side rotor and the driven side rotor,
An attachment member comprising a cylindrical wall portion, coaxial with the camshaft, and attached to the driven-side rotating body;
A spool that is reciprocally housed along the axis of the mounting member in a space defined by the cylindrical wall portion of the mounting member, and that is supplied with fluid discharged from an external pump;
A first port for allowing fluid to selectively flow into or out of the advance chamber and the retard chamber according to the movement of the spool; A second port is formed in the cylindrical wall of the mounting member;
A first flow path that communicates the first port with the advance chamber and a second flow path that communicates the second port with the retard chamber are formed in the driven-side rotor.
The thermal expansion coefficient of the material forming the driven-side rotating body is larger than the thermal expansion coefficient of the material forming the mounting member, and the outer peripheral surface of the mounting member and the inner peripheral surface of the driven-side rotating body are in contact with each other. When attached, the first flow path communicates with the first port, the second flow path communicates with the second port,
A supply port through which fluid from the pump is supplied to the spool is formed in the cylindrical wall portion of the attachment member, and a supply flow path that communicates with the supply port is formed in the driven-side rotator.
By a gap communicating passage created between the outer peripheral surface of the mounting member and the inner peripheral surface of the driven side rotational member, between said first passage and said feed passage, and the supply flow path and the second flow path and in that the communicating can be supplied to Oite fluid between.

According to this characteristic configuration, when the outer peripheral surface of the attachment member and the inner peripheral surface of the driven-side rotating body are attached in contact with each other, the first flow path communicates with the first port, and the second flow path becomes the second port. The supply flow path of the driven side rotating body communicates with the supply port formed in the cylindrical wall portion of the attachment member. Then, by a gap communicating passage created between the inner and outer circumferential surfaces of the mounting member of the driven side rotation body, between the supply flow path and the first flow path, and the supply passage and the second flow path Oite between, communicating can be supplied fluid.
In other words, when the fluid viscosity decreases with increasing temperature and the amount of fluid leakage from the advance chamber and retard chamber increases, the amount of fluid supplied to at least one of the advance chamber and the retard chamber Can be increased. This makes it possible to maintain the relative rotational phase against the action of the cam fluctuation torque.
Therefore, even when the amount of fluid leakage increases from the advance chamber and the retard chamber as the temperature rises, the valve opening and closing timing at which the fluid can be supplied to the advance chamber and the retard chamber to suppress fluctuations in the relative rotational phase. A control unit was configured.

A characteristic configuration of the valve timing control apparatus according to the present invention includes a driving side rotating body that rotates synchronously with a crankshaft of an internal combustion engine,
A driven-side rotating body fixed to the camshaft so as to rotate integrally with the camshaft for opening and closing the valve;
An advance chamber and a retard chamber formed by the drive side rotor and the driven side rotor,
An attachment member comprising a cylindrical wall portion, coaxial with the camshaft, and attached to the driven-side rotating body;
A spool that is reciprocally housed along the axis of the mounting member in a space defined by the cylindrical wall portion of the mounting member, and that is supplied with fluid discharged from an external pump;
A first port for allowing fluid to selectively flow into or out of the advance chamber and the retard chamber according to the movement of the spool; A second port is formed in the cylindrical wall of the mounting member;
A first flow path that communicates the first port with the advance chamber and a second flow path that communicates the second port with the retard chamber are formed in the driven-side rotor.
A partition member provided between the driven-side rotating body and the mounting member and formed of a material having a thermal expansion coefficient larger than a thermal expansion coefficient of a material forming the mounting member; and the mounting member is the driven When attached to the side rotor, the first flow path communicates with the first port, the second flow path communicates with the second port,
The gap communication path created between the inner peripheral surface of the partition member and the outer peripheral surface of the mounting member is provided between the supply flow path to which the fluid from the pump is supplied and the first flow path, and the supply certain Oite fluid in that communicating can be supplied between the flow path and the second flow path.

According to this characteristic configuration, when the outer peripheral surface of the attachment member and the inner peripheral surface of the partition member are attached in contact with each other, the first flow path communicates with the first port, and the second flow path communicates with the second port. . Then, by a gap communicating passage created between the mounting member and the partition member, between the supply passage and the first passage, and Oite between the supply passage and the second flow path, the fluid can be supplied Communicate with.
In other words, when the fluid viscosity decreases with increasing temperature and the amount of fluid leakage from the advance chamber and retard chamber increases, the amount of fluid supplied to at least one of the advance chamber and the retard chamber Can be increased. This makes it possible to maintain the relative rotational phase against the action of the cam fluctuation torque.
Therefore, even when the amount of fluid leakage increases from the advance chamber and the retard chamber as the temperature rises, the valve opening and closing timing at which the fluid can be supplied to the advance chamber and the retard chamber to suppress fluctuations in the relative rotational phase. A control unit was configured.

  As another configuration, the gap communication path is created between the first communication path created between the supply flow path and the first flow path, and between the supply flow path and the second flow path. There may be two communication passages, and the passage resistance of the first communication passage may be different from the passage resistance of the second communication passage.

  According to this, for example, the passage resistance between the first flow path and the second flow path is such that more fluid can be supplied to one of the advance chamber and the retard chamber that resists the cam fluctuation torque. By setting this, it is also possible to obtain a force that resists cam fluctuation torque.

It is sectional drawing of a valve opening / closing timing control apparatus. It is the II-II sectional view taken on the line of FIG. It is the III-III sectional view taken on the line of FIG. It is the IV-IV sectional view taken on the line of FIG. It is a perspective view of a connecting bolt, an internal rotor, and an adapter. It is sectional drawing which shows an outer peripheral side communicating path. It is the VII-VII sectional view taken on the line of FIG. It is sectional drawing which shows embodiment from which an outer peripheral side communicating path differs. It is sectional drawing which shows embodiment from which an outer peripheral side communicating path differs. It is sectional drawing which shows an inner peripheral side communicating path. It is the XI-XI sectional view taken on the line of FIG. It is sectional drawing which shows different embodiment of an inner peripheral side communicating path. It is sectional drawing which shows different embodiment of an inner peripheral side communicating path. It is sectional drawing which shows a clearance communicating path. It is sectional drawing which shows the modification of a clearance communicating path. It is the XVI-XVI sectional view taken on the line of FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[Basic configuration]
As shown in FIGS. 1 and 2, an external rotor 20 (an example of a drive side rotating body) that rotates synchronously with a crankshaft 1 of an engine E as an internal combustion engine, and an intake camshaft 5 coaxial with a combustion chamber of the engine E The valve opening / closing timing control device A is configured to include an internal rotor 30 (an example of a driven-side rotating body) that rotates integrally with the intake camshaft 5 so as to be relatively rotatable about the rotation axis X of the intake camshaft 5.

  This valve opening / closing timing control device A includes an internal rotor 30 with respect to the external rotor 20, and the internal rotor 30 is connected to the intake camshaft 5 by a connection bolt 38 (an example of an attachment member) penetrating the center position. doing. Inside the space of the connecting bolt 38, a bolt shaft core (coincident with the rotation shaft core X) and a coaxial core are accommodated, and a spool 41 is accommodated so as to be reciprocally movable (reciprocally movable) along the bolt shaft core. A spool spring 42 for energizing the spool 41 is accommodated. An electromagnetic solenoid 44 for operating the spool 41 is supported by the engine E, and the spool 41, the spool spring 42, and the electromagnetic solenoid 44 constitute an electromagnetic control valve 40.

  The valve opening / closing timing control device A changes the relative rotational phase between the external rotor 20 and the internal rotor 30 by controlling the hydraulic oil (an example of fluid) by the electromagnetic control valve 40, thereby controlling the opening / closing timing of the intake valve 5V. Configured to do. In this configuration, the spool 41 and the spool spring 42 rotate integrally with the internal rotor 30.

  An engine E (an example of an internal combustion engine) in FIG. 1 is provided in a vehicle such as a passenger car. The engine E is configured as a four-cycle type in which a piston 3 is accommodated in a cylinder bore of a cylinder block 2 at an upper position of the crankshaft 1 and the piston 3 and the crankshaft 1 are connected by a connecting rod 4.

  An upper portion of the engine E is provided with an intake camshaft 5 and an exhaust camshaft for opening and closing the intake valve 5V. The engine E includes a hydraulic pump P (an example of a fluid pressure pump) that is driven by the crankshaft 1. The hydraulic pump P supplies the lubricating oil stored in the oil pan of the engine E to the electromagnetic control valve 40 through the supply passage 8 as hydraulic oil (an example of fluid).

  The timing chain 7 is wound around the output sprocket 6 formed on the crankshaft 1 of the engine E and the timing sprocket 23S of the external rotor 20. As a result, the external rotor 20 rotates in synchronization with the crankshaft 1. Although not shown in the drawings, a sprocket is also provided at the front end of the camshaft on the exhaust side, and a timing chain 7 is wound around the sprocket.

  As shown in FIG. 2, in the valve opening / closing timing control device A, the external rotor 20 rotates in the driving rotation direction S by the driving force from the crankshaft 1. The direction in which the inner rotor 30 rotates relative to the outer rotor 20 in the same direction as the driving rotation direction S is referred to as an advance angle direction Sa, and the opposite direction is referred to as a retard angle direction Sb. In this valve opening / closing timing control device A, when the relative rotational phase is displaced in the advance direction Sa, the intake compression ratio is increased as the displacement amount is increased, and when the relative rotational phase is displaced in the retard direction Sb, the displacement amount is increased. The relationship between the crankshaft 1 and the intake camshaft 5 is set so as to reduce the intake compression ratio as it increases.

  In this embodiment, the intake camshaft 5 is provided with the valve opening / closing timing control device A. However, the valve opening / closing timing control device A is provided on the exhaust camshaft, and both the intake camshaft 5 and the exhaust camshaft are provided. You may be prepared for.

[Valve opening / closing timing control device]
As shown in FIGS. 1 to 5, the valve opening / closing timing control device A includes an external rotor 20 and an internal rotor 30, and also includes a bush-shaped adapter 37 that is sandwiched between the internal rotor 30 and the intake camshaft 5. Configured.

  The external rotor 20 includes an external rotor main body 21, a front plate 22, and a rear plate 23, which are integrated by fastening a plurality of fastening bolts 24. A timing sprocket 23 </ b> S is formed on the outer periphery of the rear plate 23.

  The outer rotor body 21 is integrally formed with a plurality of protrusions 21T that protrude inward in the radial direction with respect to the rotation axis X. The inner rotor 30 protrudes on the outer periphery of the inner rotor body 31 so as to come into contact with the inner peripheral surface of the outer rotor body 21 and the cylindrical inner rotor body 31 that is in close contact with the protruding end of the protruding portion 21T of the outer rotor body 21. And a plurality of (four) vane portions 32 provided.

  Thus, a plurality of fluid pressure chambers C are formed on the outer peripheral side of the inner rotor body 31 at an intermediate position between the protrusions 21T adjacent in the rotational direction by including the inner rotor 30 with respect to the outer rotor 20. These fluid pressure chambers C are partitioned by the vane portion 32, so that the advance chamber Ca and the retard chamber Cb are partitioned.

  In this valve opening / closing timing control device A, the outer rotor main body 21 and the inner rotor main body 31 are made of an aluminum alloy, and the connecting bolt 38 and the adapter 37 are made of a steel material containing iron. By setting this material, the thermal expansion coefficient of the inner rotor body 31 is set to be larger than the thermal expansion coefficient of the connecting bolt 38 and the adapter 37.

  In this valve opening / closing timing control device A, a lock member 25 is provided in a guide hole 26 formed in a posture along the rotation axis X with respect to one of the plurality of vane portions 32 so as to be slidable. A lock spring for projecting and urging 25 is provided. Further, the rear plate 23 is formed with a lock recess that allows the lock member 25 to be engaged and disengaged. A lock mechanism L is constituted by the lock member 25, the lock spring, and the lock recess.

  In this lock mechanism L, the lock member 25 is engaged with the lock recess by the urging force of the lock spring, and the relative rotation phase is held at the most retarded phase.

  As shown in FIG. 1, the relative rotational phase (hereinafter referred to as the relative rotational phase) between the outer rotor 20 and the inner rotor 30 across the adapter 37 and the front plate 22 is changed from the most retarded phase to the intermediate phase, which will be described later. A torsion spring 28 for applying an urging force is provided.

  The connecting bolt 38 has a bolt head portion 38H and a male screw portion 38S. The male screw portion 38S is screwed into the female screw portion of the intake camshaft 5, so that the internal rotor 30 is sucked through the adapter 37. The camshafts 5 are connected to each other and rotate together.

  A cylindrical wall portion 38C centering on the rotation axis X is formed on the side of the connecting bolt 38 that is close to the bolt head portion 38H, and the spool 41 is accommodated inside the cylindrical wall portion 38C. Further, an intermediate recess 38 </ b> A for sending hydraulic oil is formed on the outer periphery of the connecting bolt 38.

  The adapter 37 includes an inner peripheral surface 37A having an inner diameter that contacts the outer peripheral surface of the intermediate portion of the connecting bolt 38, an outer peripheral surface 37B that contacts the inner periphery of the rear plate 23, and a first side wall 37S1 that contacts the inner rotor body 31. The second side wall 37S2 that contacts the intake camshaft 5 is formed in a cylindrical shape.

  As shown in FIG. 5, a restriction pin 39 that is parallel to the rotational axis X is provided at a position that penetrates the contact surface between the inner rotor 30 and the adapter 37 and the contact surface between the adapter 37 and the intake camshaft 5. It is fitted. Thereby, the internal rotor 30, the adapter 37, and the intake camshaft 5 rotate integrally.

  In this adapter 37, a plurality of (four) outlet channels 37D are formed in a penetrating state by drilling so that hydraulic oil supplied from the intermediate recess 38A of the connecting bolt 38 to the inner peripheral surface 37A is sent to the outer peripheral surface 37B. Has been. Furthermore, a plurality of (four) branch channels 37E that are parallel to the rotation axis X are formed so that the hydraulic oil from each of the outlet channels 37D is sent out in the direction of the first side wall 37S1.

  These branch flow paths 37E communicate with a pump flow path 35 (an example of a first flow path) formed in the inner rotor body 31. The first side wall 37S1 has a plurality of groove portions 37G formed radially in a region extending from the annular recess 37C to the outer peripheral surface 37B. The groove portion 37G constitutes a part of the retarded channel 34.

[Valve opening / closing timing control device: oil passage configuration]
The space in which the relative rotational phase is displaced in the advance direction Sa by the supply of hydraulic oil is the advance chamber Ca. Conversely, the space in which the relative rotational phase is displaced in the retard direction Sb by the supply of hydraulic oil is delayed. This is the corner chamber Cb. The relative rotational phase in a state in which the vane portion 32 has reached the operating end in the advance angle direction Sa (including the phase near the operation end of the vane portion 32 in the advance angle direction Sa) is referred to as the most advanced angle phase. The relative rotational phase in a state in which reaches the operating end in the retarding direction Sb (including the phase near the operating end of the vane portion 32 in the retarding direction Sb) is referred to as the most retarded phase.

  The internal rotor body 31 communicates with a pump passage 35 (an example of a supply passage) that is parallel to the rotation axis X so as to supply hydraulic oil from the hydraulic pump P to the spool 41 and an advance chamber Ca. The advance channel 33 (an example of the first channel) and the retard channel 34 (an example of the second channel) communicating with the retard chamber Cb are formed.

  In addition, an advance channel 33 communicates with the lock recess. Accordingly, when the hydraulic oil is supplied to the advance chamber 33 to the advance chamber Ca, the lock member 25 is detached from the lock recess against the urging force of the lock spring, and the lock state can be released.

  The spool spring 42 applies an urging force in a direction in which the spool 41 is separated from the intake camshaft 5, and the connecting bolt 38 is provided with a stopper 43 that determines an operating end on the outer end side of the spool 41. .

  The electromagnetic solenoid 44 includes a plunger 44a that protrudes by an amount proportional to the electric power supplied to the internal solenoid, and operates the spool 41 by the pressing force of the plunger 44a.

  In the spool 41, land portions 41A are formed on the inner end side (the intake camshaft 5 side) and the outer end side, and an annular groove portion 41B is formed on the entire circumference of the intermediate position of these land portions 41A. . The inside of the spool 41 is formed hollow, and a drain hole 41 </ b> D is formed at the protruding end of the spool 41.

  A pump port 38 </ b> Cp (an example of a supply port) to which hydraulic oil is supplied from the pump flow path 35 is formed in the cylindrical wall portion 38 </ b> C of the connection bolt 38. The cylindrical wall portion 38C has an advance port 38Ca (an example of a first port) for supplying and discharging hydraulic oil to and from the advance chamber Ca by the operation of the spool 41, and supply and discharge of hydraulic oil to and from the retard chamber Cb. And a retarding port 38Cb (an example of a second port). Incidentally, the advance port 38Ca and the retard port 38Cb are arranged at positions sandwiching the pump port 38Cp in the direction along the rotation axis X.

  A pump-side annular groove 35P communicating with the pump port 38Cp is formed on the inner periphery of the inner rotor body 31, and a plurality (four) of pump flow paths 35 are communicated with this. Further, an advance side annular groove 33A that communicates with the advance port 38Ca is formed on the inner periphery of the inner rotor body 31, and a plurality (four) of the advance passages 33 communicate with this. Further, a retard side annular groove 34A that communicates with the retard port 38Cb is formed on the inner periphery of the adapter 37, and a plurality (four) of the retard channels 34 communicate with this.

  Particularly, as shown in FIGS. 1, 3, and 4, the retarding flow path 34 includes a retarding-side annular groove 34 </ b> A formed on the inner periphery of the adapter 37 and a groove formed on the first side wall 37 </ b> S <b> 1 of the adapter 37. 37G and a hole-like portion formed in the inner rotor main body 31.

  The electromagnetic solenoid 44 is held at the non-pressing position shown in FIG. 1 in the non-energized state, and when it is in the non-pressing position, the spool 41 is held at the advance position shown in FIG. Further, when a predetermined power is supplied to the electromagnetic solenoid 44, the plunger 44a reaches the inner end side pressing position, and the spool 41 is held in the retard position. Further, by applying a lower power to the electromagnetic solenoid 44, the protruding amount of the plunger 44a is limited, and the electromagnetic solenoid 44 is held at a neutral position (position shown in FIG. 6) which is intermediate between the retard position and the advance position.

  A supply flow path 8 for supplying hydraulic oil from the hydraulic pump P is formed in the engine constituent member 10 that rotatably supports the intake camshaft 5.

  A supply space 11 to which hydraulic oil from the supply flow path 8 is supplied is formed inside the connecting bolt 38, and a check valve 45 made of a spring and a ball is provided inside. On the outer periphery of the connecting bolt 38, an intermediate recess 38A to which hydraulic oil that has passed through the check valve 45 is supplied is formed in an annular shape over the entire periphery.

  As a result, the hydraulic oil from the hydraulic pump P is supplied from the supply flow path 8 to the supply space 11, and is further supplied from the check valve 45 to the intermediate recess 38 </ b> A. The hydraulic oil supplied to the intermediate recess 38A is sent from the inner peripheral surface 37A of the adapter 37 to the plurality of outlet channels 37D, and sequentially passes through the branch channel 37E, the pump channel 35, and the pump port 38Cp communicating with this. Is supplied to the groove portion 41B of the spool 41.

  When the spool 41 is set to the advance position (position shown in FIG. 1) in the situation where the hydraulic oil is supplied, the hydraulic oil from the pump port 38Cp is sent to the advance port 38Ca and from the retard port 38Cb. Hydraulic oil is discharged. On the contrary, when the spool 41 is set to the retard position, the hydraulic oil from the pump port 38Cp is sent to the retard port 38Cb, and the hydraulic oil from the advance port 38Ca is discharged. Further, when the spool 41 is set to the neutral position, the supply and discharge of hydraulic oil to and from the advance port 38Ca and the retard port 38Cb are blocked.

  As a result, when the spool 41 is set to the advance position, the retard position, or the neutral position, the relative rotation phase is displaced in the advance direction Sa, and the relative rotation phase is maintained in the retard direction Sb. The

[Communication path: Outer side communication path]
In the valve timing control apparatus A of the present invention, since the hydraulic oil leaks from the advance chamber Ca and the retard chamber Cb even when the spool 41 is in the neutral position, as shown in FIGS. 6 and 7. In addition, a plurality (four) of outer peripheral side communication passages 51 are formed on the outer periphery of the connecting bolt 38 in order to make up the leaked hydraulic oil in the advance chamber Ca and the retard chamber Cb. The outer peripheral side communication passage 51 is also configured to increase the amount of supplied oil by using a decrease in the viscosity of the hydraulic oil when the oil temperature rises.

  The outer peripheral side communication path 51 includes an outer peripheral side advance communication path 51F (an example of a first communication path) obtained by cutting the outer periphery of the connecting bolt 38 into a groove shape, and an outer peripheral side retarded communication path 51R (second communication path). Example). The outer peripheral side advance communication passage 51F connects the pump passage 35 (strictly, the pump side annular groove 35P) and the advance passage 33 (strictly, the advance side annular groove 33A) to the advance chamber Ca. It is formed at a position for supplying hydraulic oil. Further, the outer peripheral side retarded communication passage 51R communicates the pump flow path 35 (strictly, the pump-side annular groove 35P) and the retard angle flow path 34 (strictly, the retarded-side annular groove 34A), thereby retarding the retardation chamber. It is formed at a position for supplying hydraulic oil to Cb.

  The outer peripheral side communication passage 51 of the present invention is formed in a groove shape on the outer periphery of the connecting bolt 38, but instead, it is formed by cutting the entire outer surface of the connecting bolt 38 as shown in FIG. You may do it. Moreover, as shown in FIG. 9, you may form by cutting a part of outer periphery of the connecting bolt 38 in D cut shape.

  Further, the outer peripheral side communication passage 51 may be formed by a space in which fluid can be circulated by forming a rough surface on the outer surface of the connecting bolt 38.

  In particular, the advance side communication distance La through which hydraulic oil flows in the outer peripheral side advance communication path 51F and the retard side communication distance Lb in which hydraulic oil flows through the outer peripheral side retard communication path 51R are set to different values. Specifically, by making the advance side communication distance La shorter than the retard side communication distance Lb (La <Lb), the passage resistance when hydraulic oil flows through the outer side advance communication path 51F is reduced. It is lower than the passage resistance when hydraulic oil flows through the corner communication passage 51R. As a result, the amount of hydraulic oil flowing in the advance passage 33 is made larger than the amount of oil flowing in the retard passage 34 to obtain a force against the cam fluctuation torque.

  Further, the groove depths of the outer peripheral side advance communication passage 51F and the outer peripheral retard communication passage 51R formed on the outer surface of the connecting bolt 38 may be different. Also by this, the passage resistance of the outer peripheral side advance communication passage 51F is made lower than the passage resistance of the outer periphery side retard communication passage 51R, and the amount of hydraulic oil supplied to the advance passage 33 is reduced. 34 is larger than the amount of hydraulic oil supplied to 34.

  In this outer peripheral side communication path 51, when the outer peripheral side advance communication path 51F and the outer peripheral side retard communication path 51R are formed in a groove shape or a D-cut shape, these are the same straight line parallel to the rotation axis X. It is not necessary to arrange them above, and they may be arranged on different straight lines. Further, only one of the outer peripheral side advance communication path 51F and the outer peripheral side retard communication path 51R may be formed.

[Communication path: Inner peripheral side communication path]
In the present invention, as shown in FIGS. 10 and 11, a plurality (four) of inner peripheral sides of the inner rotor body 31 are provided on the inner periphery of the inner rotor body 31 in order to compensate for the leaked hydraulic oil in the advance chamber Ca and the retard chamber Cb. A communication path 52 is formed. The inner peripheral side communication passage 52 is also configured to increase the amount of supplied oil by utilizing a decrease in the viscosity of the hydraulic oil when the oil temperature rises.

  The inner peripheral communication path 52 includes an inner peripheral advance communication path 52F (an example of a first communication path) formed by cutting the inner surface of the inner rotor body 31 into a groove shape, and an inner peripheral retard angle. The communication path 52R (an example of a second communication path) is configured. The inner peripheral side advance communication passage 52F is formed at a position where the pump passage 35 and the advance passage 33 are communicated with each other and hydraulic oil is supplied to the advance chamber Ca. Further, the inner peripheral retarding communication path 52R is formed at a position where the pump flow path 35 and the retarding flow path 34 communicate with each other and hydraulic oil is supplied to the retarding chamber Cb.

  The inner peripheral side communication passage 52 of the present invention is formed in a groove shape on the inner periphery of the inner rotor body 31, but instead of this, as shown in FIG. It may be formed by cutting. Further, as shown in FIG. 13, the inner rotor body 31 may be formed by a hole formed in a direction along the rotation axis X. When the inner peripheral side communication passage 52 is formed by a hole, the hole position is set so as to communicate with the advance side annular groove 33A, the pump flow path 35, and the retard angle side annular groove 34A. Is done.

  In addition, the inner peripheral side communication passage 52 may be formed by a space that allows fluid to flow by forming a rough surface on the inner periphery of the inner rotor body 31.

  In particular, the advance side communication distance La through which hydraulic oil flows through the inner circumferential side advance communication path 52F and the retard side communication distance Lb through which hydraulic oil flows through the inner circumferential side retard communication path 52R are set to different values. Yes. Specifically, by making the advance side communication distance La shorter than the retard side communication distance Lb (La <Lb), the passage resistance when hydraulic oil flows through the inner circumference advance communication path 52F is reduced to the inner circumference. It is lower than the passage resistance when hydraulic oil flows through the side retard communication passage 52R.

  Further, by cutting the inner periphery of the inner rotor body 31, the groove depths of the inner peripheral side advance communication passage 52F and the inner peripheral side retard communication passage 52R may be made different. This also reduces the amount of hydraulic fluid supplied to the advance flow path 33 by making the inner circumferential side advance communication path 51F2 path resistance lower than the path resistance of the inner circumference retard communication path 52R. The amount of hydraulic oil supplied to the passage 34 is larger.

  In this inner peripheral side communication path 52, when the inner peripheral side advance communication path 52F and the inner peripheral side retard communication path 52R are formed in a groove shape, these are on the same straight line parallel to the rotation axis X. However, these may be arranged on different straight lines. Only one of the inner peripheral side advance communication passage 52F and the inner peripheral retard communication passage 52R may be formed.

  In addition, since the internal rotor main body 31 is formed by an extrusion process, you may form a groove part by the setting of the shape of the die | dye used for this extrusion process.

[Communication path: Gap communication path]
In the present invention, as shown in FIG. 14, the gap communication passage 53 is formed by a gap created between the internal rotor main body 31 and the connecting bolt 38 when the temperature rises by utilizing the difference in thermal expansion coefficient. Is formed. The gap communication path 53 also functions to increase the amount of supplied oil by utilizing the decrease in the viscosity of the hydraulic oil when the oil temperature rises.

  The gap communication path 53 includes a gap advance communication path 53F (an example of a first communication path) and a gap retard angle communication path 53R (an example of a second communication path). The gap advance communication passage 53F is formed at a position where the pump passage 35 and the advance passage 33 are communicated to each other and hydraulic oil is supplied to the advance chamber Ca. The gap retardation communication path 53R is formed at a position where the pump passage 35 and the retardation passage 34 are communicated with each other and hydraulic oil is supplied to the retardation chamber Cb.

  In particular, the advance side communication distance La through which hydraulic oil flows through the gap advance communication path 53F and the retard side communication distance Lb through which hydraulic oil flows through the gap retard communication path 53R are set to different values. Specifically, the passage resistance when the hydraulic oil flows through the gap advance communication path 53F is set lower than the passage resistance when the hydraulic oil flows through the gap retard communication path 53R. As a result, the amount of hydraulic oil flowing through the advance passage 33 is made larger than the amount of oil flowing through the retard passage 34.

[Communication passage: Modification of gap communication passage]
As shown in FIGS. 15 and 16, the gap communication passage 53 of this modification includes an advance-side bush 55 (partition member) between the pump passage 35 and the advance passage 33 on the inner periphery of the inner rotor body 31. 1), and a retard angle side bush 56 (an example of a partition member) is provided between the pump channel 35 and the retard channel 34.

  The advance-side bush 55 and the retard-side bush 56 are made of a material having a thermal expansion coefficient larger than that of the connecting bolt 38, and are fitted and fixed to the inner periphery of the inner rotor body 31 without a gap. When the oil temperature of the hydraulic oil is lower than the set value, the inner circumference contacts the outer circumference of the connecting bolt 38.

  Further, when the temperature of the hydraulic oil rises, a gap advance communication path 53F appears due to a difference in thermal expansion coefficient between the advance side bush 55 and the connection bolt 38, and between the retard angle side bush 56 and the connection bolt 38. A gap retardation communication path 53R appears. A gap communication path 53 is formed by the gap advance communication path 53F and the gap retard communication path 53R.

  Accordingly, when the oil temperature is low, the gap advance communication path 53F and the gap retard communication path 53R are not created, and hydraulic oil is not supplied to the advance chamber Ca and the retard chamber Cb. On the other hand, when the temperature of the hydraulic oil rises, the gap advance communication path 53F and the gap retard communication path 53R are created, and the advance chamber Ca and the retard angle are generated even when the spool 41 is in the neutral position. Hydraulic fluid is supplied to the chamber Cb.

  Particularly, in the modified example of the gap communication passage 53, an advance side communication distance La through which hydraulic oil flows through the gap advance communication path 53F and a retard side communication distance Lb through which hydraulic oil flows through the gap retard communication passage 53R are set. It is set to a different value. That is, the advance side communication distance La is the thickness in the direction along the rotational axis X of the advance side bush 55, and the retard side communication distance Lb is in the direction along the rotational axis X of the retard side bush 56. It is thickness.

  Also in this modification, by making the advance side communication distance La shorter than the retard side communication distance Lb (La <Lb), the passage resistance when hydraulic oil flows through the gap advance communication path 53F is reduced to the gap retard angle. It is lower than the passage resistance when hydraulic oil flows through the communication passage 53R.

  In this modification, only one of the advance side bush 55 and the retard side bush 56 may be provided on the inner periphery of the inner rotor body 31. In this case, the inner peripheral surface of the portion of the inner rotor body 31 that does not include the bush is brought into contact with the outer peripheral surface of the connecting bolt 38.

[Communication passage: Modification of gap communication passage]
In this modification, a groove-like flow path is formed by processing the inner circumference of one of the advance-side bush 55 and the retard-side bush 56 described above.

  In this way, by forming a groove-like flow path on the inner periphery of one of the advance side bush 55 and the retard side bush 56, even when the temperature of the hydraulic oil is low, the advance chamber Ca and the retarded side bush 56 are delayed. It is possible to supply hydraulic oil to at least one of the corner chamber Cb and to increase the amount of supplied oil by using a decrease in the viscosity of the hydraulic oil when the oil temperature rises.

[Other Embodiments of Communication Path]
In the embodiment, the communication path is formed either on the outer side of the connection bolt 38 or on the inner side of the internal rotor body 31. However, a communication path such as a groove is formed on the outer periphery of the connection bolt 38, and the internal rotor body. A communication path may be configured by combining two types of communication paths by forming a groove-like communication on the inner periphery of 31.

  Further, when the passage resistance is set to the communication passage that supplies the hydraulic oil from the pump flow path 35 to the advance flow path 33 and the communication path that supplies the hydraulic oil from the pump flow path 35 to the retard flow path 34. For example, the groove formed on the outer periphery of the connecting bolt 38 or the inner periphery of the inner rotor body 31 is formed deeper toward the side closer to the advance passage 33, or the groove width toward the side closer to the advance passage 33. The channel resistance may be set by widening.

[Operation / Effect of Embodiment]
The valve opening / closing timing control device A has a configuration in which hydraulic oil leaks from the advance chamber Ca and the retardation chamber Cb, and the leakage is also promoted by the centrifugal force accompanying the rotation of the valve opening / closing timing control device A. . The amount of leakage of the hydraulic oil is small when the hydraulic oil temperature is low and the viscosity of the hydraulic oil is high, and increases as the viscosity decreases as the temperature rises. Accordingly, when the spool 41 is in the neutral position in a state where the oil temperature has risen, the amount of hydraulic oil leaked from the advance chamber Ca and the retard chamber Cb increases, and the cam fluctuation acting from the intake camshaft 5 increases. The relative rotation phase fluctuates due to the torque, causing fluttering.

  On the other hand, in the present invention, a communication path for flowing the hydraulic oil from the pump port 38Cp to the advance channel 33 or the retard channel 34 is formed at the boundary portion between the inner rotor body 31 and the connecting bolt 38. As a result, the amount of hydraulic oil leaking from the advance chamber Ca and the retard chamber Cb is compensated, and at least one of the advance chamber Ca and the retard chamber Cb is filled with the hydraulic oil to change the cam. The fluctuation of the relative rotational phase is suppressed by the torque.

  In particular, even when the operating oil is in a situation where the viscosity decreases and the amount of leak increases as the oil temperature rises, the advance angle is increased via the communication path due to the difference in thermal expansion coefficient between the internal rotor body 31 and the connecting bolt 38. The amount of hydraulic oil supplied to the chamber Ca or the retard chamber Cb is increased, and hydraulic oil that only compensates for the leak amount is supplied to the advance chamber Ca and the retard chamber Cb to suppress fluctuations in the relative rotational phase. ing.

  Further, in the case where the valve opening / closing timing control device A is provided in the intake camshaft 5, the cam fluctuation torque acts in the retarding direction Sb. For this reason, even when the spool 41 is in the neutral position, the relative rotational phase is displaced in the retarding direction Sb due to leakage of hydraulic oil from the advance chamber Ca and the retard chamber Cb.

  In order to cope with such a problem, the advance side communication distance La is made shorter than the retard side communication distance Lb, and the passage resistance of the first communication passage is made smaller than the passage resistance of the second communication passage. Accordingly, more hydraulic oil is supplied to the advance chamber Ca than the retard chamber Cb, the displacement of the relative rotation phase in the retard direction is suppressed, and the fluctuation of the relative rotation phase due to the cam fluctuation torque is suppressed.

  The present invention can be used in a configuration that includes a drive-side rotator and a driven-side rotator, and has a spool inside a connecting bolt that connects the driven-side rotator to the camshaft.

1 Crankshaft 5 Camshaft (Intake camshaft)
20 Drive-side rotating body (external rotor)
30 driven-side rotator 33 first flow path (advanced flow path)
34 Second channel (retarded channel)
35 Supply channel (pump channel)
38 Mounting member (connection bolt)
38C Cylindrical wall 38Cp Supply port (pump port)
38Ca 1st port (advance port)
38Cb second port (retarding port)
41 Spool 51F 1st communication path (outer peripheral side advance communication path)
51R 2nd communication path (outer peripheral retarded communication path)
52F 1st communication path (inner circumference advance communication path)
52R 2nd communicating path (inner peripheral side retarded communicating path)
53F 1st communication path (gap advance communication path)
53R Second communication path (gap-side retarded communication path)
55 Partition member (advanced side bush)
56 Partition member (retard angle side bush)
Ca Lead angle chamber Cb Delay angle chamber E Internal combustion engine
P pump (hydraulic pump)

Claims (3)

A drive-side rotating body that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating body fixed to the camshaft so as to rotate integrally with the camshaft for opening and closing the valve;
An advance chamber and a retard chamber formed by the drive side rotor and the driven side rotor,
An attachment member comprising a cylindrical wall portion, coaxial with the camshaft, and attached to the driven-side rotating body;
A spool that is reciprocally housed along the axis of the mounting member in a space defined by the cylindrical wall portion of the mounting member, and that is supplied with fluid discharged from an external pump;
A first port for allowing fluid to selectively flow into or out of the advance chamber and the retard chamber according to the movement of the spool; A second port is formed in the cylindrical wall of the mounting member;
A first flow path that communicates the first port with the advance chamber and a second flow path that communicates the second port with the retard chamber are formed in the driven-side rotor.
The thermal expansion coefficient of the material forming the driven-side rotating body is larger than the thermal expansion coefficient of the material forming the mounting member, and the outer peripheral surface of the mounting member and the inner peripheral surface of the driven-side rotating body are in contact with each other. When attached, the first flow path communicates with the first port, the second flow path communicates with the second port,
A supply port through which fluid from the pump is supplied to the spool is formed in the cylindrical wall portion of the attachment member, and a supply flow path that communicates with the supply port is formed in the driven-side rotator.
By a gap communicating passage created between the outer peripheral surface of the mounting member and the inner peripheral surface of the driven side rotational member, between said first passage and said feed passage, and the supply flow path and the second valve timing control apparatus for communicating can be supplied to Oite fluid between the flow path. A drive-side rotating body that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating body fixed to the camshaft so as to rotate integrally with the camshaft for opening and closing the valve;
An advance chamber and a retard chamber formed by the drive side rotor and the driven side rotor,
An attachment member comprising a cylindrical wall portion, coaxial with the camshaft, and attached to the driven-side rotating body;
A spool that is reciprocally housed along the axis of the mounting member in a space defined by the cylindrical wall portion of the mounting member, and that is supplied with fluid discharged from an external pump;
A first port for allowing fluid to selectively flow into or out of the advance chamber and the retard chamber according to the movement of the spool; A second port is formed in the cylindrical wall of the mounting member;
A first flow path that communicates the first port with the advance chamber and a second flow path that communicates the second port with the retard chamber are formed in the driven-side rotor.
A partition member provided between the driven-side rotating body and the mounting member and formed of a material having a thermal expansion coefficient larger than a thermal expansion coefficient of a material forming the mounting member; and the mounting member is the driven When attached to the side rotor, the first flow path communicates with the first port, the second flow path communicates with the second port,
The gap communication path created between the inner peripheral surface of the partition member and the outer peripheral surface of the mounting member is provided between the supply flow path to which the fluid from the pump is supplied and the first flow path, and the supply flow path and a valve timing control apparatus for communicating can be supplied to Oite fluid between the second flow path.   The gap communication path has a first communication path created between the supply flow path and the first flow path, and a second communication path created between the supply flow path and the second flow path. The valve opening / closing timing control device according to claim 1, wherein a passage resistance of the first communication passage is different from a passage resistance of the second communication passage.

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