JP2009180148A - Valve timing adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing adjusting device capable of reducing its dimension without increasing the number of manufacturing processes of a bushing. <P>SOLUTION: A housing 3 has a storage chamber. A vane rotor 5 is driven to be relatively rotated to a delay side or an advance side with respect to the housing 3 by hydraulic pressure. The bushing 10 is formed into a bottomed cylindrical shape. A locking pin 9 regulates the relative rotation of the vane rotor 5 and the bushing 10. An assist spring 8 is stored in the bushing 10 and presses the vane rotor 5 to the advance side or the delay side with respect to the housing 3. The bottom 12 of the bushing 10 has a first recessed groove 14 locking the locking pin 9 and a second recessed groove 17 locking the assist spring 8. The first recessed groove 14 and second recessed groove 17 communicate with a direction parallel to the axis of the bushing 10. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a valve timing adjusting device that adjusts the opening / closing timing (hereinafter, “opening / closing timing”) of at least one of an intake valve and an exhaust valve of an internal combustion engine.

  Conventionally, a housing that receives the driving force of the crankshaft of the internal combustion engine and a vane rotor that transmits the driving force of the crankshaft to the camshaft are provided to the housing by the pressure of the hydraulic oil in the retard chamber and the advance chamber in the housing. On the other hand, there is known a valve timing adjusting device that adjusts the phase of the camshaft with respect to the crankshaft, that is, the valve timing, by driving the vane rotor to rotate relative to the retard side and the advance side.

  Generally, in a valve timing adjusting device that controls the phase of a camshaft on the exhaust valve side of an internal combustion engine, the phase is controlled to the advance side when the internal combustion engine is started, and the internal combustion engine is started. For this reason, when the internal combustion engine is stopped, the phase of the valve timing adjusting device is controlled to the advance side. However, when the internal combustion engine stops while the phase is controlled to the retarded side, such as during a failure, the phase is moved to the advanced side against the torque of the camshaft only with the low hydraulic pressure at the start. It becomes difficult. For this reason, there is known a valve timing adjusting device that is equipped with an assist spring that biases the vane rotor toward the advance side with respect to the housing and moves the phase toward the advance side.

As described in Patent Document 1, one end of the assist spring is locked to the front plate of the housing, and the other end is locked to a support member provided on the front plate side of the vane rotor. The vane rotor and the support member are positioned by inserting a non-rotating pin into a hole provided in each surface where the vane rotor and the support member are joined, and relative rotation is restricted.
However, if the support member is downsized with the miniaturization of the valve timing adjusting device, it is difficult to form the hole of the support member with a sintering mold. For this reason, if the hole of a supporting member is formed by cutting, the process of manufacturing a supporting member will increase and manufacturing cost will become high.

JP 2004-84645 A

  The objective of this invention is providing the valve timing adjustment apparatus which can make a physique small, without increasing the manufacturing process of a supporting member.

  According to the first aspect of the present invention, the valve timing adjusting device includes a housing having a storage chamber and a vane rotor that is driven to rotate relative to the housing toward the retard side or the advance side by the pressure of the working fluid. A cylindrical portion formed in a cylindrical shape and a bottom portion that closes one end of the cylindrical portion, the bottom portion abutting on the counter-driven shaft side of the vane rotor, and a support member provided coaxially with the rotation shaft of the vane rotor, Locked to the vane rotor, the other end is locked to the bottom of the support member, and the regulating member for positioning the vane rotor and the support member in the relative rotation direction is housed inside the cylindrical portion of the support member, and one end is held in the housing And an urging means for urging the vane rotor toward the advance side or the retard side with respect to the housing. The support member has a first concave groove portion that locks the other end of the regulating member on the vane rotor side of the bottom portion, and a second concave groove portion that locks the other end of the urging means on the side opposite to the vane rotor on the bottom portion. The first groove portion and the second groove portion communicate with each other in a direction parallel to the axis of the support member.

  Thereby, the 1st ditch | groove part and 2nd ditch | groove part of a support member can be formed in one process. For this reason, a supporting member can be reduced in size without increasing the manufacturing process of a supporting member. As a result, the physique of the valve timing adjusting device can be reduced without increasing the manufacturing cost.

  According to the second aspect of the present invention, the support member has a bolt hole in the bottom portion into which a bolt for coupling the vane rotor and the driven shaft is inserted. The second concave groove portion of the support member communicates with the bolt hole in the radial direction. Thereby, the 1st ditch | groove part and 2nd ditch | groove part of a support member can be easily manufactured with a type | mold of sintering. For this reason, a supporting member can be reduced in size without increasing the manufacturing process of a supporting member. As a result, the physique of the valve timing adjusting device can be reduced without increasing the manufacturing cost.

  According to invention of Claim 3, a supporting member is formed from iron sintering. Thereby, when forming a supporting member with a metal mold | die, a 1st ditch | groove part and a 2nd ditch | groove part can be easily manufactured with a sintering metal mold | die. For this reason, a supporting member can be reduced in size without increasing the manufacturing process of a supporting member. As a result, the physique of the valve timing adjusting device can be reduced without increasing the manufacturing cost.

  According to the fourth aspect of the present invention, the support member has a protrusion that protrudes from the bottom toward the opening. The second groove portion opens to the anti-driven shaft side of the protruding portion. The surface of the protruding portion on the side of the driven shaft that is in contact with the head seating surface of the bolt that joins the vane rotor and the driven shaft is subjected to surface pressure and needs to be increased. Since the first concave groove portion and the second concave groove portion communicate with each other in a direction parallel to the axis of the support member, the second concave groove portion does not open to the anti-driven shaft side of the protruding portion, and the anti-driven shaft of the protruding portion A large side surface can be secured. For this reason, a supporting member can be reduced in size, without increasing the process of reinforcing a protrusion part with respect to the surface pressure of an axial bolt. As a result, the physique of the valve timing adjusting device can be reduced without increasing the manufacturing cost.

  According to the fifth aspect of the present invention, the cylindrical portion of the support member has a cutout portion through which one end of the urging means is inserted, and the second concave groove portion of the support member is provided on the opposite side of the cutout portion in the radial direction. It is done. Thereby, since the attitude | position of an urging | biasing means can be maintained, it can prevent that the cylinder part and urging | biasing means of a supporting member rub against each other. For this reason, the thickness of the cylinder part of a support member can be made thin and the support member can be reduced in size, without increasing the process of reinforcing the surrounding wall of a holding member. As a result, the physique of the valve timing adjusting device can be reduced without increasing the manufacturing cost.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
1 to 5 show a valve timing adjusting device according to a first embodiment of the present invention. The valve timing adjusting device 1 of the present embodiment is a hydraulic control type that uses hydraulic oil as a working fluid, and adjusts the valve timing for controlling the phase at the start of the exhaust valve of the internal combustion engine to the advance side.
First, the mechanical configuration of the valve timing adjusting device 1 will be described. The valve timing adjusting device 1 according to the present embodiment includes a housing 3, a vane rotor 5, a bushing 10 as a support member, an assist spring 8 as a biasing means, a non-rotating pin 9 as a regulating means, and the like. .

As shown in FIGS. 1 to 3, the housing 3, which is a drive-side rotator, includes a chain sprocket 32 and a shoe housing 33. The chain sprocket 32 is coupled to a crankshaft as a drive shaft of an internal combustion engine (not shown) by a chain, and rotates in synchronization with the crankshaft. The driving force of the crankshaft is transmitted to the camshaft 2 via the valve timing device 1 and drives the exhaust valve to open and close.
The camshaft 2 as a driven shaft is inserted into the chain sprocket 32 so as to be rotatable relative to the chain sprocket 32, and rotates with a predetermined phase difference with respect to the chain sprocket 32. The chain sprocket 32 and the camshaft 2 rotate clockwise as viewed from the direction of arrow II shown in FIG. Hereinafter, this rotation direction is referred to as an advance direction, and the counter rotation direction is referred to as a retard direction.

The shoe housing 33 has a cylindrical peripheral wall 36, shoes 37, 38, 39 extending radially inward from the peripheral wall 36, and a front plate 31 provided on the opposite side of the chain sprocket across the peripheral wall 36. And integrally formed. The shoe housing 33 is fixed coaxially with the chain sprocket 31 by bolts 34.
The shoes 37, 38, 39 are provided at substantially equal intervals in the rotation direction of the peripheral wall 36. A storage chamber 41 is provided between the shoe 37 and the shoe 38, a storage chamber 42 is provided between the shoe 38 and the shoe 39, and a storage chamber 43 is provided between the shoe 39 and the shoe 37.
The front plate 31 is formed in a disk shape, and a fixing pin 35 is provided outside the housing 3. The front plate 31 has a circular hole 40 that communicates from the outside to the inside of the housing 3 at the center of the disk.

  The vane rotor 5 which is a driven side rotating body is in contact with the end surface of the camshaft 2 in the rotation axis direction. The vane rotor 5 is coaxially coupled to the camshaft 2 by a bolt (not shown) attached to the bolt hole 53. Positioning in the rotational direction of the vane rotor 5 and the camshaft 2 is achieved by fitting positioning pins (not shown) into the fitting holes 54 of the vane rotor 20 and the camshaft 2.

The vane rotor 5 is accommodated in the housing 3 so as to be rotatable relative to the housing 3. The vane rotor 5 includes a cylindrical rotor 51 fixed to the camshaft 2, and vanes 56, 57, 58 on the outer peripheral side of the rotor 51. The rotor 51 has a recess 52 that is recessed in a cylindrical shape toward the camshaft 2 on the surface on the front plate side. The central axis of the recessed portion 52 coincides with the central axis of the vane rotor 5. The inner periphery of the recessed portion 52 is slightly smaller than the inner periphery of the circular hole 40 of the front plate 31.
The vanes 56, 57, and 58 are rotatably accommodated in the accommodation chambers 41, 42, and 43. The vane 56 partitions the storage chamber 41 into an advance chamber 44 and a retard chamber 47. The vane 57 partitions the accommodation chamber 42 into an advance chamber 45 and a retard chamber 48. The vane 58 partitions the accommodation chamber 43 into an advance chamber 46 and a retard chamber 49. The arrows representing the advance angle direction and the retard angle direction shown in FIG. 3 represent the advance angle direction and the retard angle direction of the vane rotor 5 with respect to the housing 3.

As shown in FIGS. 4 and 5, the bushing 10 includes a cylindrical portion 11 and a bottom portion 12 that closes one end of the cylindrical portion 11. The bushing 10 is integrally formed by iron sintering.
The cylindrical portion 11 is formed in a cylindrical shape, and accommodates the assist spring 8 inside. The cylinder part 11 has the notch part 13 which notches the wall surface of the cylinder part 11 in the circumferential direction in the predetermined range. The notch 13 allows the one end 82 of the assist spring to be inserted. The notch range of the notch portion 13 corresponds to an angle range in which the vane rotor 5 rotates relative to the housing 3.
The bottom 12 is provided with a protrusion 16 that protrudes toward the opening side of the bushing 10. The protruding portion 16 is provided at a predetermined interval in the radial direction from the inner wall surface of the cylindrical portion 11. A spring body 86 of the assist spring 8 is accommodated between the protruding portion 16 and the cylindrical portion 11.

  The bottom portion 12 has a bolt hole 15 that communicates from the opening side surface of the bushing 10 to the vane rotor 5 side surface at the axial center of the bushing 10. Bolts (not shown) are inserted into the bolt holes 15 and the bolt holes 53 of the vane rotor 5, and the bushing 10 and the vane rotor 5 and the camshaft 3 are coupled. The protrusion 16 is provided with a seating surface 19 formed on a surface perpendicular to the rotation axis of the vane rotor 5 on the opening side of the bushing 10. The head of the bolt comes into contact with the seating surface 19.

The bottom portion 12 has a second concave groove portion 17 in which a part of the protruding portion 16 is cut out on the substantially opposite side of the notch portion 13 in the radial direction. The angle formed by the second concave groove portion 17 and the end portion on the retarded side of the notch portion 13 is set within a range of 90 degrees to 270 degrees. The width of the second groove portion 17 is formed to be substantially the same as the diameter of the other end 83 of the assist spring 81. The second concave groove portion 17 engages the other end 83 of the assist spring 81 and prevents the assist spring 81 from rotating in the bushing 10.
The second concave groove portion 17 opens on the radially outer side of the projecting portion 16 and the seat surface 19 side, and communicates with the bolt hole 15 on the radially inner side. The protruding portion 16 is provided with a guide portion 18 that is rounded on the radially outer side facing the second concave groove portion 17. The guide portion 18 guides the other end 83 of the assist spring 8 to the second concave groove portion 17.

  The bottom 12 has a first groove 14 that is recessed in the axial direction on the vane rotor 5 side. The first concave groove portion 14 communicates with the second concave groove portion in a direction parallel to the axis of the bushing 10 and communicates with the bolt hole 15 radially inward. The circumferential width of the first concave groove portion 14 is formed to be approximately the same as the diameter of the other end 93 of the rotation stopper pin 9. The other end 93 of the detent pin 9 is locked in the first concave groove. The other end 83 of the assist spring 8 is locked to the second recessed groove portion 17 side of the other end 93 of the rotation preventing pin 9 to prevent the rotation preventing pin 9 from coming out of the first recessed groove portion 14.

  The bushing 10 is press-fitted into the recess 52 of the rotor 51 as shown in FIGS. The bottom portion 12 contacts the surface of the recessed portion 52 on the front plate 31 side, and the outer surface of the tubular portion 11 contacts the inner peripheral surface of the recessed portion 52. Thereby, the bushing 10 is provided coaxially with the rotating shaft of the vane rotor 5. The cylindrical portion 11 of the bushing 10 is formed slightly smaller than the inner periphery of the circular hole 40 of the front plate 31, and a minute gap is formed between the cylindrical portion 11 and the circular hole 40. For this reason, the front plate 31 and the bushing 10 are slidably contacted with each other.

  One end 92 of the locking pin 9 is locked in a fitting hole 55 formed in a direction parallel to the rotation axis of the vane rotor 5. The other end 93 of the locking pin 9 is press-fitted into the first concave groove portion 14 when the bushing 10 is press-fitted into the recessed portion 52. Thereby, the rotation prevention pin 9 positions the vane rotor 5 and the bushing 10 in the relative rotational direction, and restricts the relative rotation of the vane rotor 5 and the bushing 10.

  The assist spring 8 is a torsion coil spring that is accommodated in a state where the spring body 86 is compressed in the cylindrical portion 11 of the bushing 10. One end 82 of the assist spring 8 extends radially outward from the spring body 86 and is locked to the fixing pin 35 of the front plate 31. The other end 83 extends radially inward from the spring body 86 and is locked to the second groove portion 17. The restoring force of the assist spring 8 acts as a torque for rotating the vane rotor 5 relative to the housing 3 in the advance side.

  The other end 83 of the assist spring 8 is provided on the substantially opposite side of the one end 82 in the radial direction. When the vane rotor is positioned at the most advanced angle, the angle formed by the other end 83 and the one end 82 of the assist spring 8 is set in the range of 90 to 270 degrees. For this reason, since the attitude | position of the assist spring 8 is maintained, it can prevent that the spring main body 86 and the inner wall of the cylinder part 11 rub against each other, and the cylinder part 11 wears.

  The seal members 21, 22, and 23 are provided on the surfaces of the rotor 51 that face the shoes 37, 38, and 39 in the radial direction, and are in sliding contact with the shoes 37, 38, and 39. The seal members 24, 25, and 26 are provided on the surfaces of the vanes 56, 57, and 58 that face the shoe peripheral wall 36 in the radial direction, and are in sliding contact with the shoe peripheral wall 36 and the liquid nectar. The seal members 21, 22, 23, 24, 25, 26 prevent the flow of hydraulic oil between the advance chambers 44, 45, 46 and the retard chambers 47, 48, 49.

  The stopper piston 71 formed in a cylindrical shape is accommodated in a guide ring 75 that fits into a hole formed in the vane 58. The stopper piston 71 can reciprocate in the rotation axis direction. The fitting ring 72 is press-fitted and held in a recess formed in the chain sprocket 32. The spring 76 biases the stopper piston 71 toward the fitting ring 72 side.

  The hydraulic pressure supplied to the hydraulic chamber 73 formed on the chain sprocket 32 side of the stopper piston 71 and the hydraulic chamber 74 formed on the outer periphery of the stopper piston 71 acts in a direction in which the stopper piston 71 comes out from the fitting ring 72. The hydraulic chambers 73 and 74 communicate with the retard chamber 49. The stopper piston 71 can be fitted to the fitting ring 72 when the vane rotor 5 is positioned on the most advanced angle side. In a state where the stopper piston 71 is fitted to the fitting ring 72, the relative rotation of the vane rotor 5 with respect to the housing 3 is restricted. When the vane rotor 5 moves from the most advanced position to the retard side with respect to the housing 3, the positions of the stopper piston 71 and the fitting ring 72 are shifted, and the stopper piston 71 cannot be fitted to the fitting ring 72.

The advance passages 64, 65, 66 form an oil passage between a hydraulic pump (not shown) and the advance chambers 44, 45, 46. The retard passages 61, 62, and 63 form an oil passage between the hydraulic pump and the retard chambers 47, 48, and 49. When hydraulic oil is supplied from the hydraulic pump to the advance chambers 44, 45, 46 via the advance passages 64, 65, 66, the retard passages 61, 62, 63 pass from the retard chambers 47, 48, 49. The hydraulic oil is discharged to the oil pan via. On the other hand, when hydraulic fluid is supplied from the hydraulic pump to the retard chambers 47, 48, 49 via the retard passages 61, 62, 63, the advance passages 64, 65, The hydraulic oil is discharged to the oil pan via 66. Of the advance chambers 44, 45, 46 and the retard chambers 47, 48, 49, the hydraulic chamber that supplies hydraulic oil is switched by the operation of a switching valve (not shown). The relative rotational position of the vane rotor 5 with respect to the housing 3 varies depending on the supply balance of hydraulic oil to the advance chambers 44, 45, 46 and the retard chambers 47, 48, 49.

Next, the general operation of the valve timing adjusting device 1 will be described with reference to FIGS. 1 and 3 show a state where the valve timing adjusting device 1 controls the advance of the phase of the vane rotor.
<When the internal combustion engine is stopped>
When the internal combustion engine is stopped, the stopper piston 71 is fitted in the fitting ring 72. In the state immediately after the internal combustion engine is started, the hydraulic fluid is not sufficiently supplied from the hydraulic pump to the advance chambers 44, 45, 46, the retard chambers 47, 48, 49, and the hydraulic chambers 73, 74. The camshaft 2 is maintained at the most advanced position with respect to the crankshaft while maintaining the state of being fitted to the fitting ring 72. As a result, the housing 3 and the vane rotor 5 are caused to oscillate and collide due to torque fluctuation received by the camshaft until hydraulic fluid is supplied to the hydraulic chambers, thereby preventing sound from being generated.

<After starting internal combustion engine>
When the hydraulic oil is sufficiently supplied from the hydraulic pump after the internal combustion engine is started, the stopper piston 71 comes out of the fitting ring 72 by the hydraulic pressure supplied to the hydraulic chambers 73 and 74, so that the vane rotor 5 rotates relative to the housing 3. It becomes movable. And the phase difference of the camshaft 2 with respect to a crankshaft is adjusted by controlling the hydraulic pressure applied to each advance chamber and each retard chamber.

<Advance angle operation>
When the valve timing adjusting device 1 is advanced, the control device (ECU) for the internal combustion engine controls the drive current supplied to the switching valve. The switching valve connects the hydraulic pump and the advance passages 64, 65, and 66, and connects the retard passages 61, 62, and 63 to the oil pan. The hydraulic oil discharged from the hydraulic pump is supplied to the advance chambers 44, 45, 46 via the advance passages 64, 65, 66. The hydraulic pressure in the advance chambers 44, 45, 46 acts on the vanes 56, 57, 58 and generates torque that biases the vane rotor 5 toward the advance side. At this time, the hydraulic oil in the retard chambers 47, 48, 49 is discharged to the oil pan through the retard passages 61, 62, 63. Due to the resultant force of the torque generated by the hydraulic pressure in the advance chambers 44, 45, 46 and the torque that causes the restoring force of the assist spring 8 to rotate the vane rotor 5 toward the advance side, the vane rotor 5 is advanced from the housing 3. Rotate to.

<At retarded angle operation>
When the valve timing adjusting device 1 is retarded, the ECU controls the drive current supplied to the switching valve. The switching valve connects the hydraulic pump and the retard passages 61, 62, 63, and connects the advance passages 64, 65, 66 and the oil pan. The hydraulic oil discharged from the hydraulic pump is supplied to the retard chambers 47, 48, and 49 via the retard passages 61, 62, and 63. The hydraulic pressure in the retard chambers 47, 48, 49 acts on the vanes 56, 57, 58, and generates torque that biases the vane rotor 5 toward the retard side. At this time, the hydraulic oil in the advance chambers 44, 45, 46 is discharged to the oil pan via the advance passages 64, 65, 66. The torque generated by the hydraulic pressure resists the torque generated by the assist spring 8, and the vane rotor 5 rotates toward the retard side with respect to the housing 3.

<Intermediate holding operation>
When the vane rotor 5 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 advance passages 64, 65, 66 and the retard passages 61, 62, 63, and the advance chambers 44, 45, 46 and the retard chambers 47, 48. 49, the hydraulic oil is prevented from being discharged into the oil pan. For this reason, the vane rotor 5 is held at the target phase.

The bushing 10 of this embodiment is formed by iron sintering. In order to form the first concave groove portion 14 in the bushing 10 by the sintering mold, an interval of about 2 mm is required between the first concave groove portion 14 and the cylindrical portion 11 and the protruding portion 16. In the bushing 10 of the present embodiment, the first concave groove portion 14 and the second concave groove portion 17 communicate with each other in the direction parallel to the axis of the bushing 10 and communicate with the bolt hole 15. For this reason, even if the bushing 10 is miniaturized with the miniaturization of the valve timing adjusting device 1, the first concave groove portion and the second concave groove portion can be formed by a sintering mold.
Moreover, the bushing 10 of this embodiment forms the 1st recessed groove part 14 and the 2nd recessed groove part 17 in one process, and can serve as both rotation prevention of the assist spring 8 and positioning of the bushing 10 in this groove | channel 1 place. . Thereby, even if the bushing 10 is reduced in size, an increase in manufacturing cost can be suppressed without increasing a manufacturing process for forming an extra groove.

(Other embodiments)
In the embodiment described above, the valve timing adjusting device that controls the phase at the start of the exhaust valve of the internal combustion engine to the advance side has been described. On the other hand, the present invention may be applied to a valve timing adjustment device that controls the phase at the start of the exhaust valve of the internal combustion engine to the retard side. Further, the present invention may be applied to a valve timing adjusting device that controls the phase at the time of start of the intake valve of the internal combustion engine to the retard side or the advance side.
As described above, the present invention is not limited to the above-described embodiment, and can be applied to other various embodiments in addition to combining the plurality of embodiments without departing from the gist thereof.

It is a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. It is a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is a top view from the II direction of FIG. It is a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the III-III sectional view taken on the line of FIG. The top view of the bushing of the valve timing adjustment apparatus by one Embodiment of this invention. It is a figure which shows the bushing of the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the VV sectional view taken on the line of FIG.

Explanation of symbols

  1: valve timing adjusting device, 2: camshaft (driven shaft), 3: housing, 5: vane rotor, 8: assist spring (biasing means), 9: detent pin (regulating means), 10: bushing (supporting member) ), 11: tube portion, 12: bottom portion, 14: first groove portion, 17: second groove portion

Claims (5)

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;
A cylindrical part formed of a cylindrical part and a bottom part closing one end of the cylindrical part, the bottom part abutting on the counter-driven shaft side of the vane rotor, and a support member provided coaxially with the rotation axis of the vane rotor;
One end is locked to the vane rotor, the other end is locked to the bottom of the support member, and a regulating member that positions the vane rotor and the support member in a relative rotational direction;
The support member is housed inside the cylindrical portion, one end is locked to the housing, the other end is locked to the bottom portion of the support member, and the vane rotor is advanced or retarded with respect to the housing. A biasing means for biasing to
With
The support member includes a first concave groove portion that locks the other end of the regulating member on the vane rotor side of the bottom portion, and a second groove that locks the other end of the urging means on the opposite side of the bottom portion to the vane rotor. A concave groove,
The valve timing adjusting device according to claim 1, wherein the first groove portion and the second groove portion of the support member communicate with each other in a direction parallel to the axis of the support member. The support member has a bolt hole through which a bolt for connecting the vane rotor and the driven shaft is inserted from a surface on the vane rotor side of the bottom portion to a surface on the opposite side of the vane rotor,
The valve timing adjusting device according to claim 1, wherein the first groove portion of the support member communicates with the bolt hole in a radial direction of the support member.   The valve timing adjusting device according to claim 1, wherein the support member is formed of iron sintering. The bottom of the support member has a protrusion protruding in the opening direction;
4. The valve timing adjusting device according to claim 1, wherein the second concave groove portion of the support member is formed in the projecting portion and opens toward a counter driven shaft side of the projecting portion. 5. . The cylindrical portion of the support member has a notch that passes through one end of the urging means,
The valve timing adjusting device according to any one of claims 1 to 4, wherein the second concave groove portion of the support member is provided on a radially opposite side of the notch portion.

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