JP2009185762A - Valve timing adjuster - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing adjuster with improved reliability, by reducing falling-off etc. of a member. <P>SOLUTION: This valve timing adjuster 10 has a housing 11, a vane rotor 16, a spring 26 and a bushing 22. The spring 26 is locked at one end on the vane rotor 16, and is locked at the other end on the housing 11, and energizes the vane rotor 16 in the ignition timing advance direction to the housing 11. An anti-camshaft side end surface of the vane rotor 16 has a recessed part 165 recessed to the camshaft side. An inner wall of the vane rotor 16 in the recessed part 165 has a projection part 168 projecting in the radial inner direction. The bushing 22 is inserted in a camshaft side end part into the recessed part 165, and stores the spring 26 inside. The bushing 22 has a locking groove 222 in the camshaft side end part, and the projection part 168 of the vane rotor 16 is locked in the locking groove 222. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a valve timing adjusting device for changing the opening / closing timing of at least one of an intake valve and an exhaust valve of an internal combustion engine (hereinafter referred to as an “internal combustion engine”) according to operating conditions.

Conventionally, a vane-type valve that drives a driven shaft through a housing that rotates synchronously with the drive shaft of an engine and opens and closes at least one of an intake valve and an exhaust valve by a phase difference due to relative rotation between the housing and the driven shaft Timing adjustment devices are known.
In the valve timing adjusting device disclosed in Patent Document 1, a cylindrical housing member is press-fitted on the opposite cam shaft side of the vane rotor, and an urging member is housed inside the housing member. The biasing member has one end locked to the vane rotor and the other end locked to the housing, and biases the vane rotor in the advance direction with respect to the housing.

By the way, in recent years, the friction of the valve operating system has been reduced due to the high output and low fuel consumption of the engine, and the fluctuation torque range of the engine has been increased. For this reason, when the vane rotor of the valve timing adjusting device is phase-maintained at a low pressure, the phase fluctuation width of the vane rotor becomes large, and the vane rotor may strike the advance stopper surface of the housing. When the vane rotor hits the advance stopper surface, the accommodation member press-fitted into the vane rotor is subject to an inertial force in the advance direction, and the accommodation member may rotate relative to the vane rotor. When the housing member rotates relative to the vane rotor, the notch portion formed in the housing member and the urging member may interfere with each other, and the original rotation operation range of the vane rotor may not be secured. Further, if the vane rotor continues to strike the advance stopper surface, the housing member loses the coaxiality, and as a result, the vane rotor may fall off the vane rotor.
JP 2005-155346 A

  Therefore, an object of the present invention is to provide a valve timing adjusting device that reduces the dropout of members and the like and improves reliability.

  The invention described in claim 1 includes a housing, a vane rotor, a biasing member, and a housing member. The housing rotates together with one of the drive shaft and the driven shaft of the engine, and a storage chamber is formed inside. The vane rotor divides the housing chamber into a retard chamber and an advance chamber, rotates with the other of the engine drive shaft and the driven shaft, and acts on the housing by the pressure of the working fluid supplied to the retard chamber and the advance chamber. Relative rotation. The biasing member has one end locked to the vane rotor and the other end locked to the housing, and biases the vane rotor in the advance angle direction or the retard angle direction with respect to the housing. The accommodating member is provided on the counter driven shaft side of the vane rotor, is formed in a cylindrical shape, and accommodates the urging member inside.

  The end surface on the counter driven shaft side of the vane rotor has a recess that is recessed toward the driven shaft. A protrusion that protrudes in the radially inward direction is formed on the inner wall of the vane rotor in the recess. The receiving member has a driven shaft side end inserted into the recess of the vane rotor. The housing member has a locking groove at the end of the driven shaft, and the protruding portion of the vane rotor is locked in the locking groove. Thereby, relative rotation of the housing member relative to the vane rotor and axial movement of the housing member relative to the vane rotor can be suppressed. Therefore, even if the vane rotor hits the stopper surface of the housing during the operation of the valve timing adjustment device and the inertia force in the direction in which the biasing member biases the vane rotor acts on the storage member, the rotation of the storage member due to the inertial force is suppressed. Thus, the interference of the housing member with the biasing member can be reduced. Moreover, even if an axial force, that is, a force in a direction in which the housing member is detached from the vane rotor, acts on the housing member, it is possible to reduce the dropout of the housing member from the vane rotor.

  According to the second aspect of the present invention, the locking groove includes a first groove extending in the axial direction from the driven shaft side end of the housing member, and a direction in which the biasing member biases the vane rotor continuously from the first groove. Consists of a second groove extending in the opposite direction. Therefore, since the protrusion of the vane rotor is locked to the second groove of the locking groove formed in the L shape in the housing member, the vane rotor hits the stopper surface of the housing during the operation of the valve timing adjusting device and biases it. Even if the inertial force in the direction in which the member biases the vane rotor acts on the housing member, the circumferential inner wall surface of the second groove of the housing member is locked to the protruding portion of the vane rotor. As a result, rotation of the housing member due to inertial force is suppressed, and interference of the housing member with the biasing member can be reduced.

  Further, with the above-described configuration, even if an axial force on the housing member, that is, a force in a direction in which the housing member separates from the vane rotor, is applied, the axial inner wall surface in the second groove of the housing member is projected from the vane rotor. It is locked to the part. Thereby, the dropout of the housing member from the vane rotor can be reduced.

  In the invention according to claim 3, the inner wall of the second groove of the housing member forms a tapered surface whose width decreases as it goes in the direction opposite to the direction in which the biasing member biases the vane rotor. And the protrusion part which protrudes from a vane rotor is fitted by the accommodating member in the taper surface. Further, the second groove of the locking groove extends from the first groove in a direction opposite to the direction in which the biasing member biases the vane rotor. Therefore, even if the inertia force in the direction in which the vane rotor hits the stopper surface of the housing and the urging member urges the vane rotor during the operation of the valve timing adjusting device acts on the accommodating member, the circumferential direction in the second groove of the accommodating member The inner wall surface is pressed against the protruding portion, and the coupling force due to the fitting between the tapered surface of the containing member and the protruding portion is not weakened. Therefore, the relative position of the housing member with respect to the vane rotor can be further stabilized.

  In the valve timing adjusting device of the present invention, the biasing member biases the vane rotor and the housing. Therefore, a reaction force is generated between the urging member and the vane rotor and the housing in a direction opposite to the resultant force of the force acting on the vane rotor and the housing from the urging member. This reaction force acts on the inner peripheral wall of the housing member from the biasing member. Thereby, the accommodating member is pressed against the inner peripheral wall of the recess of the vane rotor. As a result, a gap may be generated between the housing member and the inner peripheral wall of the vane rotor in a direction opposite to the direction in which the housing member is pressed by the urging member.

  Therefore, in the invention according to claim 4, the housing member has a locking groove at the driven shaft side end portion, and the position acts on the vane rotor and the housing from the biasing member in the circumferential direction of the housing member. It is set within a range of ± 90 ° of the reaction direction of the resultant force. That is, the housing member has a locking groove on the side where the housing member is pressed rather than the shaft center. Therefore, in the vicinity of the locking groove, there is no gap between the outer peripheral wall of the housing member and the inner peripheral wall of the vane rotor, or very little, if any. As a result, even if a force such as an inertial force is applied to the housing member during the operation of the valve timing adjusting device, the housing member may excessively rotate over the protruding portion in the locking groove, or may fall off the vane rotor. Can be reduced.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(One embodiment)
A valve timing adjusting device according to an embodiment of the present invention is shown in FIGS. The valve timing adjusting device 10 of this embodiment is a hydraulic control type and controls the valve timing of the exhaust valve.

  As shown in FIG. 1, the housing 11 is configured by fixing chain sprockets 12, shoe housings 13, and a front plate 14, which are separate members, coaxially with bolts 20, so that the vane rotor 16 can be relatively rotated. Contained. The chain sprocket 12, the shoe housing 13, and the front plate 14 are formed by sintering or forging with iron, for example. The chain sprocket 12 receives a driving force from a crankshaft as a drive shaft of an engine (not shown) by a chain (not shown), and rotates in synchronization with the crankshaft.

  The vane rotor 16 is integrally fixed by a camshaft (not shown) and a bolt (not shown), and rotates together with the camshaft. The camshaft drives an exhaust valve (not shown) to open and close. The housing 11, the vane rotor 16 and the camshaft rotate in the clockwise direction when viewed from the arrow X direction shown in FIG. Hereinafter, this rotational direction is referred to as an advance direction. The vane rotor 16 has a concave portion 165 that is recessed in a substantially annular shape toward the camshaft side on the end surface on the side opposite to the camshaft. The bush 22 serving as a housing member is inserted into the recess 165 at the camshaft side end, and lightly press-fitted into the recess 165 substantially coaxially with the vane rotor 16. The bush 22 will be described in detail later.

The vane rotor 16 has a convex portion 166 that protrudes in a substantially annular shape toward the opposite camshaft side on the radially inner side of the concave portion 165, that is, the inner side of the bush 22. Grooves 167 extending in the radially inward direction from the outer peripheral edge are formed in the convex portion 166.
The chain sprocket 12 constitutes one side wall of the housing 11, and the front plate 14 constitutes the other side wall of the housing 11. As shown in FIG. 2, the shoe housing 13 is formed in an annular shape, and has four shoes 131, 132, 133, and 134 that protrude to the inner peripheral side at substantially equal intervals in the circumferential direction. A fan-shaped storage chamber 50 is formed in the gap between the shoes adjacent in the rotation direction.

  The vane rotor 16 is formed by sintering or forging with iron, for example. The vane rotor 16 includes a boss portion 160 that abuts between the camshaft and the end surfaces in the rotation axis direction, and four vanes 161, 162, and 163 that are installed at substantially equal intervals in the circumferential direction and project radially outward from the boss portion 160. 164. Positioning of the vane rotor 16 and the cam shaft in the rotational direction is performed by fitting a positioning pin (not shown) into the pin hole 18 provided in the boss portion 160 and the pin hole provided in the cam shaft.

  Each vane is accommodated in each accommodating chamber 50 so as to be relatively rotatable, and each accommodating chamber 50 is divided into a retarded hydraulic chamber as a retarded chamber and an advanced hydraulic chamber as an advanced chamber. The arrows representing the retard direction and the advance direction shown in FIG. 2 represent the retard direction and the advance direction of the vane rotor 16 with respect to the housing 11. As shown in FIGS. 1 and 2, the camshaft and vane rotor 16 are rotatable relative to the housing 11 coaxially.

  As shown in FIG. 2, a retarded hydraulic chamber 51 is formed between the shoe 131 and the vane 161, and a retarded hydraulic chamber 52 is formed between the shoe 132 and the vane 162, and the shoe 133 and the vane 163 A retard hydraulic chamber 53 is formed between them, and a retard hydraulic chamber 54 is formed between the shoe 134 and the vane 164. An advance hydraulic chamber 55 is formed between the shoe 134 and the vane 161, an advance hydraulic chamber 56 is formed between the shoe 131 and the vane 162, and an advance hydraulic chamber is formed between the shoe 132 and the vane 163. 57 is formed, and an advance hydraulic chamber 58 is formed between the shoe 133 and the vane 164.

Hydraulic oil is supplied to each retarded hydraulic chamber from a retarded oil passage 100 (see FIG. 2) formed in the vane rotor 16, and each advanced hydraulic chamber has an end face side that contacts the vane rotor 16 of the chain sprocket 12. Hydraulic oil is supplied from the advance oil passage 110 formed in the above.
By switching the supply of hydraulic oil to both the oil passages 100 and 110 and the discharge of the hydraulic oil from both the oil passages 100 and 110, the vane rotor 16 is rotated relative to the housing 11, and the camshaft is moved relative to the crankshaft. Adjust the phase difference.

  The spring pin 24 shown in FIG. 1 is press-fitted and fixed in a press-fitting hole 25 (see FIG. 2) formed in the shoe 133 of the shoe housing 13 through the front plate 14. The spring 26 as an urging member is accommodated inside the bush 22, one end is locked to a groove 167 formed in the convex portion 166 of the vane rotor 16, and the other end is locked to the spring pin 24. The urging force of the spring 26 acts as a torque for rotating the vane rotor 16 in the advance direction with respect to the housing 11.

  Here, the fluctuation torque received from the exhaust valve when the camshaft drives the exhaust valve varies positively and negatively. The positive direction of the variable torque represents the retard direction of the vane rotor 16 with respect to the housing 11, and the negative direction of the variable torque represents the advance direction of the vane rotor 16 with respect to the housing 11. The average of the fluctuation torque works in the positive direction, that is, in the retard direction. The torque in the advance direction applied by the spring 26 to the vane rotor 16 is approximately the same as the average of the fluctuation torque received by the camshaft.

  The seal member 28 is made of, for example, resin, and is fitted to the inner peripheral wall of each shoe and the outer peripheral wall of each vane as shown in FIG. A minute clearance is provided between the outer peripheral wall of each shoe and the boss portion 160 and between the outer peripheral wall of each vane and the inner peripheral wall of the shoe housing 13, and hydraulic oil leaks between the hydraulic chambers through this clearance. Is prevented by the seal member 28. Each of the sealing members 28 is pressed toward the outer peripheral wall of the boss portion 160 and the inner peripheral wall of the shoe housing 13 by the urging force of the leaf spring.

  As shown in FIG. 1, the stopper piston 30 formed in a bottomed cylindrical shape is accommodated in a through hole 17 formed through the vane 161 in the rotation axis direction so as to be reciprocally movable in the rotation axis direction. The stopper piston 30 has an accommodation hole 31 for accommodating the spring 34 therein. One end of the spring 34 is locked to the front plate 14, and the other end is locked to the bottom of the accommodation hole 31 of the stopper piston 30. The spring 34 biases the stopper piston 30 toward the fitting ring 36. The fitting ring 36 is press-fitted and held in a press-fitting hole 121 provided in the chain sprocket 12. The fitting ring 36 is formed with a fitting hole 37 into which the bottom side of the stopper piston 30 is fitted.

  In the state where the stopper piston 30 shown in FIG. 1 is fitted to the fitting ring 36, the relative rotation of the vane rotor 16 with respect to the housing 11 is restricted. The predetermined angular position at which the stopper piston 30 is fitted to the fitting ring 36 is the optimum starting phase when the camshaft phase with respect to the crankshaft starts the engine, and the valve timing adjusting device for the exhaust valve of the present embodiment 10 is the most advanced position. A back pressure chamber 38 provided on the side opposite to the fitting ring 36 of the through hole 17 with respect to the stopper piston 30 communicates with the communication hole 15 formed in the front plate 14 at the most advanced angle position and is opened to the atmosphere. Therefore, the reciprocating movement of the stopper piston 30 at the most advanced angle position is not hindered.

  The first pressure chamber 40 formed on the fitting ring 36 side communicates with the retard hydraulic chamber 51, and the second pressure chamber 42 formed around the stopper piston 30 communicates with the advance hydraulic chamber 55. The hydraulic pressures in the first pressure chamber 40 and the second pressure chamber 42 act in the direction in which the stopper piston 30 comes out from the fitting ring 36.

Next, the bush 22 will be described in detail.
As shown in FIGS. 3A and 3B, the bush 22 is formed in a substantially cylindrical shape by, for example, metal. The bush 22 has a notch 221 at the end on the camshaft side opposite to the axial direction. The bush 22 has a locking groove 222 at the axial camshaft side end. The locking groove 222 is continuous with the first groove 223 extending in the axial direction from the camshaft side end of the bush 22, and is cut in a direction opposite to the direction in which the spring 26 biases the vane rotor 16. It consists of a second groove 224 that extends, and is substantially L-shaped. That is, the second groove 224 is formed to extend in the retard direction from the end of the first groove 223 on the side opposite to the camshaft.

  As shown in FIG. 3B, the bush 22 forms tapered surfaces 225 and 226 that face each other in the axial direction in the second groove 224. The second groove 224 has a taper surface 225 and a taper surface 226 that have a smaller width in the axial direction toward the retarding direction. In addition, the bush 22 forms a wall surface 227 between the tapered surface 225 and the tapered surface 226 on the side opposite to the first groove 223 of the second groove 224.

  As described above, the vane rotor 16 has the recess 165 that is recessed in a substantially annular shape toward the camshaft side on the end surface on the side opposite to the camshaft. The outer diameter of the recess 165, that is, the inner diameter of the recess 165 of the vane rotor 16 is set to be substantially the same as or slightly larger than the outer diameter of the bush 22. As shown in FIG. 1, the bush 22 is lightly press-fitted into the recess 165 substantially coaxially with the vane rotor 16. As shown in FIGS. 1 and 4, the inner wall of the recess 165 of the vane rotor 16 has a protruding portion 168 that protrudes in the radially inward direction. The height of the protrusion 168, that is, the amount of protrusion from the inner wall of the vane rotor 16 is set slightly smaller than the thickness of the bush 22 in the radial direction.

  As shown in FIG. 4, the width in the bush 22 axial direction in the vicinity of the wall surface 227 of the second groove 224, that is, the distance between the tapered surface 225 and the tapered surface 226 is larger than the width of the protrusion 168 in the bush 22 axial direction. Slightly small. When the bush 22 is attached to the vane rotor 16, first, the bush 22 is lightly press-fitted into the recess 165 of the vane rotor 16 by aligning the positions of the first groove 223 and the protrusion 168. Next, the bush 22 is rotated in the advance direction. Accordingly, the protruding portion 168 is located in the second groove 224 and is fitted between the tapered surface 225 and the tapered surface 226 and the bush 22. As a result, a coupling force is generated between the vane rotor 16 and the bush 22 at the fitting portion between the protrusion 168 and the second groove 224.

  The spring 26 shown in FIGS. 1 and 5 is a so-called torsion spring and is accommodated inside the bush 22. The spring 26 is attached by engaging one end with a groove 167 formed in the convex portion 166 of the vane rotor 16 and then twisting the other end in an advance direction to engage with a spring pin 24 provided in the housing 11. It is done. Therefore, the spring 26 urges the vane rotor 16 and the housing 11 at the groove 167 and the spring pin 24. Thereby, the urging force of the spring 26 acts as a torque for rotating the vane rotor 16 relative to the housing 11 in the advance direction. At this time, the other end of the spring 26 is located inside the notch 221 of the bush 22 and does not interfere with the bush 22.

As shown in FIG. 5, a force F ₁ as an urging force from the spring 26 acts on the groove 167 of the vane rotor 16. Further, a force F ₂ as an urging force from the spring 26 acts on the spring pin 24. Therefore, a reaction force F ₃ is generated in the spring 26 in the direction opposite to the resultant force of the force F ₁ and the force F ₂ . The reaction force F ₃ acts on the inner peripheral wall of the bush 22 from the spring 26. As a result, the bush 22 is pressed against the inner peripheral wall of the recess 165 of the vane rotor 16.

In the present embodiment, the locking groove 222 of the bush 22 has a force F ₁ acting on the vane rotor 16 from the spring 26 and a force F ₂ acting on the housing 11 from the spring 26 in the circumferential direction of the bush 22. Is formed in a range of ± 90 ° in the direction in which the reaction force F ₃ of the resultant force acts. That is, the bush 22 has a locking groove 222 on the side where the bush 22 is pressed with respect to the shaft center O. Therefore, in the vicinity of the locking groove 222, no gap is formed between the outer peripheral wall of the bush 22 and the inner peripheral wall of the vane rotor 16, or even a slight amount is generated.

Next, the operation of the valve timing adjusting device 10 will be described with reference to FIGS. 1 and 2. 1 and 2 show a state of the valve timing adjusting device 10 before the engine is started, that is, when the engine is stopped.
<When the engine is stopped>
When the engine is stopped, the stopper piston 30 is fitted in the fitting ring 36. In the state immediately after starting the engine, the retarded hydraulic chambers 51, 52, 53, 54, the advanced hydraulic chambers 55, 56, 57, 58, the first pressure chamber 40, and the second pressure chamber 42 are sufficiently supplied from the hydraulic pump. Since the hydraulic oil is not supplied, the stopper piston 30 is maintained in a state of being fitted to the fitting ring 36, and the camshaft is held at the most advanced position with respect to the crankshaft. Thus, the housing 11 and the vane rotor 16 are prevented from swinging and colliding with each other due to torque fluctuations received by the camshaft until hydraulic fluid is supplied to the hydraulic chambers, thereby preventing hitting sound.

<After starting the engine>
When the hydraulic oil is sufficiently supplied from the hydraulic pump after the engine is started, the stopper piston 30 comes out of the fitting ring 36 due to the hydraulic pressure supplied to the first pressure chamber 40 and the second pressure chamber 42. The vane rotor 16 is relatively rotatable. The camshaft phase difference with respect to the crankshaft is adjusted by controlling the hydraulic pressure applied to each retarded hydraulic chamber and each advanced hydraulic chamber.

<At retarded angle operation>
When the valve timing adjusting device 10 is retarded, an electronic control unit (ECU) (not shown) controls the drive current supplied to the switching valve. A switching valve (not shown) connects the hydraulic pump and the retarded oil passage 100 and connects the advanced oil passage 110 and the oil pan. The hydraulic oil discharged from the hydraulic pump is supplied to the retarded hydraulic chambers 51, 52, 53 and 54 via the retarded oil passage 100. The hydraulic pressure in the retarded hydraulic chambers 51, 52, 53, and 54 acts on the vanes 161, 162, 163, and 164, and generates torque that biases the vane rotor 16 in the retarded direction. At this time, the hydraulic oil in the advance chambers 55, 56, 57 and 58 is discharged to the oil pan via the advance oil passage 110. The torque generated by the hydraulic pressure in the retarded hydraulic chambers 51, 52, 53, 54 resists the torque in the advance direction generated by the spring 26, and the vane rotor 16 rotates in the retard direction with respect to the housing 11.

<Advance angle operation>
When the valve timing adjusting device 10 is advanced, the ECU controls the drive current supplied to the switching valve. The switching valve connects the hydraulic pump and the advance oil passage 110 and connects the retard oil passage 100 and the oil pan. The hydraulic oil discharged from the hydraulic pump is supplied to the advance hydraulic chambers 55, 56, 57 and 58 via the advance oil passage 110. The hydraulic pressure in the advance hydraulic chambers 55, 56, 57, 58 acts on the vanes 161, 162, 163, 164, and generates torque that urges the vane rotor 16 in the advance direction. At this time, the hydraulic oil in the retarded hydraulic chambers 51, 52, 53, 54 is discharged to the oil pan via the retarded oil passage 100. The vane rotor 16 advances relative to the housing 11 by the resultant force of the torque generated by the hydraulic pressure in the advance hydraulic chambers 55, 56, 57, and 58 and the torque that causes the restoring force of the spring 26 to rotate the vane rotor 16 in the advance direction. Rotate angularly.

<Intermediate holding operation>
When the vane rotor 16 reaches the target phase, the ECU controls the duty ratio of the drive current supplied to the switching valve. Thereby, the switching valve cuts off the connection between the hydraulic pump and the retard oil passage 100 and the advance oil passage 110, and retard oil chambers 51, 52, 53, 54 and advance oil chambers 55, 56, 57. , 58 to restrict the hydraulic oil from being discharged to the oil pan. For this reason, the vane rotor 16 is held at the target phase.

  During the above-described intermediate holding operation, when the pressure in each retarded hydraulic chamber and each advanced hydraulic chamber is low, that is, when the vane rotor 16 is held in phase at a low pressure, the vane 163 of the vane rotor 16 is formed on the housing shoe 133. The advance stopper surface 135 may be hit. When the vane rotor 16 hits the advance stopper surface 135, an inertia force in the advance direction acts on the bush 22 lightly press-fitted into the vane rotor 16, and the bush 22 may rotate relative to the vane rotor 16.

  In the case of the embodiment of the present invention, the locking groove 222 of the bush 22 is continuous with the first groove 223 extending in the axial direction from the camshaft side end of the bush 22 and the first groove 223 in the retarding direction. It consists of a second groove 224 that extends through a notch, and is substantially L-shaped. The protruding portion 168 of the vane rotor 16 is locked to the second groove 224 of the locking groove 222. Therefore, even if the vane rotor 16 strikes the advance stopper surface 135 of the housing 11 during the operation of the valve timing adjusting device 10 and the inertial force in the advance direction acts on the bush 22, the wall surface 227 in the second groove 224 of the bush 22. Is locked to the protrusion 168 of the vane rotor 16. As a result, rotation of the bush 22 due to inertial force is suppressed, and interference of the bush 22 with the spring 26 can be reduced. Further, even if an axial force is applied to the bush 22, that is, a force in a direction in which the bush 22 is detached from the vane rotor 16, the tapered surface 226 in the second groove 224 of the bush 22 is engaged with the protruding portion 168 of the vane rotor 16. Stopped. Thereby, dropping of the bush 22 from the vane rotor 16 can be reduced. Therefore, the reliability of the valve timing adjusting device 10 can be improved.

  In the case of one embodiment of the present invention, the bush 22 forms tapered surfaces 225 and 226 whose width decreases in the second groove 224 toward the retard direction. The protruding portion 168 protruding from the vane rotor 16 is fitted to the tapered surfaces 225 and 226 of the bush 22. Further, the second groove 224 of the locking groove 222 is formed by cutting out from the first groove 223 in the retarding direction. Therefore, even if the vane rotor 16 strikes the advance stopper surface 135 of the housing 11 during the operation of the valve timing adjusting device 10 and the inertial force in the advance direction acts on the bush 22, the wall surface 227 in the second groove 224 of the bush 22. Is pressed against the protruding portion 168, and the coupling force between the tapered surfaces 225, 226 of the bush 22 and the protruding portion 168 is not weakened. Therefore, the relative position of the bush 22 with respect to the vane rotor 16 can be further stabilized.

  Furthermore, in the case of one embodiment of the present invention, the bush 22 has a locking groove 222 at the camshaft side end, and the position thereof is a spring 26 with respect to the vane rotor 16 and the housing 11 in the circumferential direction of the bush 22. Is set in a range of ± 90 ° of the reaction direction of the resultant force of the force acting from the side. That is, the bush 22 has a locking groove 222 on the side where the bush 22 is pressed with respect to the shaft center O. Therefore, in the vicinity of the locking groove 222, no gap is formed between the outer peripheral wall of the bush 22 and the inner peripheral wall of the vane rotor 16, or even a slight amount is generated. Accordingly, even when a force such as an inertial force is applied to the bush 22 during the operation of the valve timing adjusting device 10, the bush 22 gets over the protruding portion 168 in the locking groove 222 and rotates excessively or from the vane rotor 16. Dropping off can be reduced. Therefore, the reliability of the valve timing adjusting device 10 can be further improved.

(Other embodiments)
In another embodiment of the present invention, the bush may not be press-fitted into the recess of the vane rotor. In the present invention, the bush has a locking groove, and the locking groove is locked to the protruding portion of the vane rotor. Therefore, even if the bush is not press-fitted into the vane rotor, the bushing is rotated by inertial force or from the vane rotor. This can reduce the falling off of the bush.

  In the above-described embodiment, an example in which the valve timing adjusting device is applied to an engine exhaust valve has been described. However, in another embodiment of the present invention, the valve timing adjusting device may be applied to an intake valve. In the above-described embodiment, an example in which the vane rotor is urged in the advance direction with respect to the housing by the spring has been described. However, in another embodiment of the present invention, the vane rotor may be biased with respect to the housing in a retarded direction by a spring. In this case, if the second groove of the bush is formed so as to extend in the advance direction from the first groove, the same effect as the above-described embodiment can be obtained.

The present invention can also be applied to a valve timing adjusting device that does not include a stopper piston.
Thus, the present invention is not limited to the above-described embodiment, and can be applied to other various embodiments without departing from the gist thereof.

1 is a cross-sectional view showing a valve timing adjusting device according to an embodiment of the present invention. II-II sectional view taken on the line of FIG. It is a figure which shows the accommodating member of the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: (A) is a top view, (B) is the BB sectional drawing of FIG. 3 (A). The fragmentary sectional view which shows the latching groove vicinity of the valve timing adjustment apparatus by one Embodiment of this invention. The top view which shows the valve timing adjustment apparatus by one Embodiment of this invention.

Explanation of symbols

  10: Valve timing adjusting device, 11: Housing, 12: Chain sprocket (housing), 13: Shoe housing (housing), 14: Front plate (housing), 16: Vane rotor, 22: Bush (housing member), 26: Spring (Biasing member), 50: storage chamber, 51, 52, 53, 54: retarded hydraulic chamber (retarded chamber), 55, 56, 57, 58: advanced hydraulic chamber (advanced chamber), 165: recessed portion 168: protrusion, 222: locking groove

Claims (4)

Provided in a driving force transmission system for transmitting a driving force from a drive shaft of an internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve, and opens and closes at least one of the intake valve and the exhaust valve In the valve timing adjusting device for adjusting the timing,
A housing having a storage chamber that rotates together with one of the drive shaft and the driven shaft and is formed in a predetermined angle range in the rotation direction;
It rotates with the other of the drive shaft and the driven shaft, partitions the storage chamber into a retard chamber and an advance chamber, and retards or advances by the pressure of the working fluid supplied to the retard chamber and the advance chamber. A vane rotor driven to rotate relative to the housing on the corner side;
One end is locked to the vane rotor, the other end is locked to the housing, and a biasing member that biases the vane rotor in an advance direction or a retard direction with respect to the housing;
Provided coaxially with the vane rotor on the counter-driven shaft side of the vane rotor, formed in a cylindrical shape, and an accommodating member that accommodates the urging member inside,
The end surface on the side of the driven shaft of the vane rotor has a recess recessed toward the driven shaft.
The inner wall of the recess of the vane rotor has a protruding portion that protrudes in a radially inward direction,
The accommodating member has a locking groove at a driven shaft side end portion, the driven shaft side end portion is inserted into the recessed portion, and the protruding portion is locked in the locking groove. Timing adjustment device. The locking groove includes a first groove extending in the axial direction from the driven shaft side end of the housing member, and a direction opposite to the direction in which the biasing member biases the vane rotor. Formed in an L-shape consisting of a second groove extending into the notch,
The valve timing adjusting device according to claim 1, wherein the protruding portion is engaged with the second groove. The inner wall of the housing member in the second groove forms a tapered surface with a width that decreases in the direction opposite to the direction in which the biasing member biases the vane rotor;
3. The valve timing adjusting device according to claim 1, wherein the protruding portion is fitted to the housing member on the tapered surface.   The housing member has the locking groove at the driven shaft side end, and the position thereof is a resultant force of the force acting from the biasing member on the housing and the vane rotor in the circumferential direction of the housing member. The valve timing adjusting device according to any one of claims 1 to 3, wherein the valve timing adjusting device is in a range of ± 90 ° of a reaction direction.

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