JP4487263B2 - Valve timing adjustment device - Google Patents

Description

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

  2. Description of the Related Art Conventionally, there is known a valve timing adjusting device that adjusts a valve timing by changing a relative rotational phase between a drive shaft and a driven shaft of an internal combustion engine by relatively rotating and driving a vane rotor with a working fluid pressure in a housing. Yes. In general, in this type of valve timing adjusting device, the vane rotor is provided with a plurality of vanes so that the operation can be performed even when the working fluid pressure is low, such as immediately after the start of the internal combustion engine. The increase of is planned. On the other hand, as the number of vanes increases, a larger amount of working fluid is required, and as a result, the operation responsiveness decreases. For example, in the technique disclosed in Patent Document 1, the number of vanes that act on the working fluid pressure is set to It is changed according to. Here, when the working fluid pressure is low, it is desirable to make the working fluid pressure act on many vanes to ensure the desired operation. Conversely, when the working fluid pressure is high, the number of vanes on which the working fluid pressure acts is set. It is desirable to improve the operation responsiveness by limiting.

JP-A-2005-36760

In the case of the technique disclosed in Patent Document 1, a vane that does not act on the working fluid pressure is driven together with a vane that acts on the working fluid pressure. At this time, the fluid chamber between the former vane and the housing is blocked by a shutoff valve. Since no working fluid is introduced, an internal pressure drop occurs in the fluid chamber. Such a decrease in internal pressure becomes an operating resistance when the vane rotor rotates relative to the housing, and therefore becomes an obstacle to improving the operating response.
The present invention has been made in view of such problems, and an object thereof is to provide a valve timing adjusting device that realizes an operation according to a working fluid pressure.

  According to the first aspect of the present invention, the second vane rotor is more sensitive to the first vane rotor on the condition that the working fluid pressure supplied from the fluid pressure supply means (hereinafter simply referred to as working fluid pressure) is less than the set pressure. At this time, supply of working fluid pressure from the fluid pressure supply means to the second storage chamber is allowed. Accordingly, both the first and second vane rotors can be rotated relative to the housing in accordance with the working fluid pressures acting on the first and second vanes in the first and second storage chambers, respectively. Therefore, when the working fluid pressure is lower than the set pressure, the number of vanes driven by the action of the working fluid pressure can be increased to ensure a desired operation.

Further, according to the first aspect of the present invention, the lock of the second vane rotor to the first vane rotor (hereinafter simply referred to as the lock of the second vane rotor) is released on the condition that the working fluid pressure is equal to or higher than the set pressure. At this time, the supply of the working fluid pressure from the fluid pressure supply means to the second storage chamber is restricted. Accordingly, the first vane rotor can be rotated relative to the housing in accordance with the working fluid pressure acting on the first vane in the first storage chamber. The relative pressure with respect to the housing can be stopped by suppressing the fluid pressure action on the vane. Accordingly, when the working fluid pressure is higher than the set pressure, not only can the number of vanes driven by the action of the working fluid pressure be reduced to reduce the required amount of working fluid, but also the fluid pressure supply is regulated. A decrease in internal pressure due to the operation of the second vane can be suppressed in the second storage chamber. Therefore, according to such an invention, the operation responsiveness can be enhanced.
The number of the first and second storage chambers and the number of the first and second vanes may be singular or plural.

  According to the second aspect of the present invention, the lock member is moved to the lock position fitted to both the first and second vane rotors by the working fluid pressure, thereby locking the second vane rotor with respect to the first vane rotor. be able to. Moreover, the lock member can unlock the second vane rotor by moving to the release position where the lock member is released from one of the first and second vane rotors by the working fluid pressure. According to such an invention, the lock for realizing the lock of the second vane rotor on the essential condition that the working fluid pressure is lower than the set pressure and releasing the lock on the essential condition that the working fluid pressure is equal to or higher than the set pressure. The means can be constructed by a simple configuration in which the lock member is a piston, for example.

  According to the third aspect of the present invention, the lock member locks the second vane rotor with respect to the housing by fitting into the fitting hole of the housing at the release position where the lock member is detached from the first vane rotor. Thereby, at the time of high pressure at which the lock member is detached from the first vane rotor and unlocks the second vane rotor, the relative rotation of the second vane rotor with respect to the housing can be surely stopped to sufficiently enhance the operation responsiveness.

According to the fourth aspect of the present invention, the lock member is provided in the housing while being pressed toward the second sliding hole side of the second vane rotor by the working fluid pressure and detached from the first sliding hole of the first vane rotor. The fitting hole is taper-fitted in the axial direction of the housing. As a result, even if the lock member is pressed by the working fluid pressure from the state in which the second sliding hole and the fitting hole are displaced in the rotation direction of the housing, the second vane rotor is relatively rotated with respect to the first vane rotor. It is possible to fit into the fitting hole while detaching from the one sliding hole. As a result of the relative rotation of the second vane rotor with respect to the first vane rotor, the first sliding hole and the second sliding hole are displaced in the rotation direction of each vane rotor. It is possible to prevent the lock member from returning to the first sliding hole by mistake due to fluctuations in the working fluid pressure or the like.

According to the invention described in claim 5, the first sliding hole of the first vane of the first vane rotor and the second sliding hole of the third vane of the second vane rotor housed together with the first vane in the first housing chamber. The position at which the lock member is fitted to each other can be determined as the lock position. Further, a position where the lock member slides in the first and second sliding holes and is separated from one of the sliding holes can be defined as a release position. According to such an invention, the lock member disposed by effectively utilizing the inside of the first and third vanes can be provided with the function of locking and releasing the second vane rotor, so that the apparatus can be easily downsized. Can be planned.
The number of third vanes may be singular or plural.

When the second vane rotor is locked, torque transmission between the vane rotors is performed through the lock member, so that shear stress may be generated in the lock member.
According to the sixth aspect of the present invention, the protruding portion that protrudes in the axial direction of the first vane rotor rather than the hole forming portion that forms the first sliding hole in the first vane is formed on the first vane rotor when the second vane rotor is locked. It contacts the third vane from one side in the rotational direction. As a result, torque transmission between the vane rotors can be realized through the contact interface between the protrusion and the third vane, so that the shearing stress is prevented from being generated in the locking member and the durability of the locking member is increased. Can do.

  According to the seventh aspect of the present invention, the supply control member moves from the fluid pressure supply means to the second storage chamber by moving to the communication position for communicating between the fluid pressure supply means and the second storage chamber by the working fluid pressure. The supply of the working fluid pressure can be permitted. Further, the supply control member is moved by the working fluid pressure to a blocking position that cuts off the communication between the fluid pressure supply means and the second storage chamber, thereby supplying the working fluid pressure from the fluid pressure supply means to the second storage chamber. Can be regulated. According to such an invention, the supply control means for permitting the supply of the fluid pressure to the second storage chamber when the second vane rotor is locked and restricting the supply of the fluid pressure to the second storage chamber when the lock is released is provided, for example, It can be constructed with a simple configuration in which the control member is a piston.

According to the seventh aspect of the present invention, the lock member moves by receiving the driving force due to the working fluid pressure via the supply control member. It can be controlled at once by pressure. Therefore, the movement controllability of the lock member and the supply control member is improved.
In addition, in the invention according to claim 7, the movement form of the lock member may be realized only when the lock member receives the driving force by the working fluid pressure via the supply control member. The case where the lock member is realized by receiving the driving force due to the fluid pressure via the supply control member and the case where it is realized by other cases, for example, when the working fluid pressure is directly applied to the lock member, depending on the conditions. May change.

When the lock of the second vane rotor is released, the first vane rotor that rotates relative to the housing also rotates relative to the second vane rotor.
According to the eighth aspect of the present invention, the supply control member having at its end a tapered portion that abuts on the lock member and transmits the driving force causes the lock member to enter the second sliding hole. Remove from the first sliding hole. Therefore, when the first vane rotor attempts to rotate relative to the housing and the second vane rotor from the state in which the tapered portion enters the second sliding hole, the force in the direction to escape from the second sliding hole is Acts on the tapered portion. Due to the action of this force, the first vane rotor can be rotated relative to the housing and the second vane rotor while the taper part escapes from the second sliding hole, so that the taper part completely escapes from the second sliding hole. When it does, the 1st sliding hole and the 2nd sliding hole will shift in the rotation direction of each vane rotor. Therefore, it is possible to prevent a situation in which the lock member immediately after being detached from the first sliding hole returns to the first sliding hole by mistake due to a change in working fluid pressure or the like.

  According to the ninth aspect of the present invention, the supply control member moves from the fluid pressure supply means to the second storage chamber by moving to the communication position where the fluid pressure supply means and the second storage chamber communicate with each other by the working fluid pressure. The supply of the working fluid pressure can be permitted. Further, the supply control member is moved by the working fluid pressure to a blocking position that cuts off the communication between the fluid pressure supply means and the second storage chamber, thereby supplying the working fluid pressure from the fluid pressure supply means to the second storage chamber. Can be regulated. According to such an invention, the supply control means for permitting the supply of the fluid pressure to the second storage chamber when the second vane rotor is locked and restricting the supply of the fluid pressure to the second storage chamber when the lock is released is provided, for example, It can be constructed with a simple configuration in which the control member is a piston.

  According to the tenth aspect of the present invention, the supply control member can be locked to the housing by moving the supply control member to the position where the supply control member is fitted to both the housing and the first vane rotor by the working fluid pressure. . Further, the supply control member moves to a communication position and a cutoff position where the supply control member separates from one of the housing and the first vane rotor by operating fluid pressure, thereby releasing the lock on the housing of the first vane rotor and locking the second vane rotor and The operation at the time of release can be smoothly advanced. According to such an invention, since the fluid pressure supply control function and the lock control function can be achieved by the same member, simplification of the configuration can be promoted.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description is abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment.
(First embodiment)
1 and 2 show a valve timing adjusting apparatus 10 according to a first embodiment of the present invention. The valve timing adjusting device 10 is a hydraulic control type that uses hydraulic oil as a working fluid, and is installed in a torque transmission system between the crankshaft and the camshaft 20 of the internal combustion engine to adjust the valve timing of an intake valve (not shown). To do. The valve timing adjusting device 10 includes a housing 11, a first vane rotor 21, a second vane rotor 31, a first piston 41 and a second piston 51, and a hydraulic pressure supply system 60.

  The housing 11 includes a sprocket 12, a shoe housing 13 and a front plate 14. An annular fitting ring 120 is provided on the sprocket 12 on the shoe housing 13 side. The sprocket 12 is connected to a crankshaft (not shown) via a timing chain (not shown), and rotates together with the crankshaft when the output torque of the crankshaft is transmitted. Here, the rotation direction of the housing 11 is the clockwise direction of FIG.

  As shown in FIGS. 1 and 2, the shoe housing 13 includes a cylindrical peripheral wall 130 and shoes 131, 132, 133, and 134 that protrude radially inward from the peripheral wall 130. The shoes 131, 132, 133, and 134 are provided at predetermined intervals in the rotation direction of the housing 11, and fan-shaped storage chambers 111, 112, 113, and 114 are formed therebetween. Here, the storage chamber 111 is disposed between the shoes 131 and 134, the storage chamber 112 is disposed between the shoes 131 and 132, the storage chamber 113 is disposed between the shoes 132 and 133, and the storage chamber 114 is disposed between the shoes 133 and 134. Arranged between. The front plate 14 is disposed on the opposite side of the sprocket 12 with the shoe housing 13 interposed therebetween, and is screwed to the sprocket 12 and the shoe housing 13. The front plate 14 is provided with a fitting hole 140 that opens to the wall surface on the shoe housing 13 side. The fitting hole 140 has a tapered hole shape and has an inner peripheral surface that expands toward the opening side.

  The camshaft 20 shown in FIG. 1 drives the intake valve to open and close when the output torque of the internal combustion engine is transmitted from the crankshaft through the valve timing adjusting device 10. The cam shaft 20 is disposed coaxially with the housing 11 and is fitted to the inner peripheral side of the sprocket 12 so as to be rotatable relative to the housing 11. As shown in FIGS. 1 and 2, the first vane rotor 21 is accommodated in the housing 11 so as to be rotatable relative to the housing 11. The first vane rotor 21 is bolted coaxially to the cam shaft 20 and rotates together with the cam shaft 20. Here, the rotation directions of the first vane rotor 21 and the camshaft 20 are clockwise in FIG. Therefore, the relative rotational direction in which the first vane rotor 21 is advanced with respect to the housing 11 is the clockwise direction in FIG. 2, and the relative rotational direction in which the first vane rotor 21 is relative to the housing 11 is the counterclockwise direction in FIG. .

  As shown in FIGS. 1 and 2, the first vane rotor 21 has a cylindrical boss portion 210 fixed to the camshaft 20, and vanes 213 and 214 that protrude radially outward from the boss portion 210. The vanes 213 and 214 are provided at predetermined intervals in the rotation direction of the first vane rotor 21 and are accommodated in the corresponding accommodating chambers 113 and 114, respectively. The vane 213 abuts the peripheral wall 130 in the storage chamber 113 to partition the storage chamber 113 into an advance chamber 63 between the shoe 132 and a retard chamber 73 between the shoe 133. The vane 214 abuts the peripheral wall 130 in the storage chamber 114 to partition the storage chamber 114 into an advance chamber 64 between the shoe 133 and a retard chamber 74 between the shoe 134. As shown in FIGS. 2 and 3, the vane 214 protrudes more than the hole forming portion 215 on the side of the front plate 14 in the axial direction of the first vane rotor 21. And a protrusion 216. The first sliding hole 219 has a cylindrical hole shape penetrating the hole forming portion 215 in the axial direction of the first vane rotor 21, and the relative rotation position of the first vane rotor 21 with respect to the housing 11 is the most retarded position as shown in FIG. Then, as shown in FIG. 1, they are arranged substantially coaxially with the inner peripheral hole (hereinafter referred to as a fitting hole) 121 of the fitting ring 120. As shown in FIGS. 2 and 3, the protruding portion 216 is disposed on the retarding chamber 74 side of the hole forming portion 215, and abutment protrusion 218 that protrudes from the side wall surface of the trapezoidal main body 217 toward the advanced angle chamber 64. have.

  As shown in FIGS. 1 and 2, the second vane rotor 31 is accommodated in the housing 11 so as to be relatively rotatable with respect to the housing 11 on the front plate 14 side of the first vane rotor 21. The second vane rotor 31 is disposed coaxially with the first vane rotor 21 and the housing 11, and is fitted to the outer peripheral side of the boss portion 210 so as to be rotatable relative to the first vane rotor 21. When the second vane rotor 31 is locked with respect to the first vane rotor 21 by the action of the second piston 51, the second vane rotor 31 rotates integrally with the first vane rotor 21 as shown in FIGS. Therefore, the rotation direction of the second vane rotor 31 is the clockwise direction in FIG. 2, and the relative rotation directions in which the first vane rotor 21 is advanced and retarded with respect to the housing 11 are the clockwise direction and the counterclockwise direction in FIG. . Note that, with respect to the relative rotational position of the second vane rotor 31 with respect to the housing 11, the most retarded angle position due to the hydraulic pressure supplied from the hydraulic pressure supply system 60 is the position shown in FIG. 2. The position of FIG. 6 that is, for example, about 1 ° behind the most retarded position is realized. Therefore, in the following description of the present embodiment, the relative rotational position of the second vane rotor 31 with respect to the housing 11 is simply referred to as the “most retarded angle position” and represents the position shown in FIG. In this case, the position shown in FIG.

  As shown in FIGS. 1 and 2, the second vane rotor 31 includes a cylindrical boss portion 310 that fits into the boss portion 210, and vanes 311, 312, and 314 that protrude radially outward from the boss portion 310. Yes. The vanes 311, 312, and 314 are provided at predetermined intervals in the rotation direction of the second vane rotor 31, and are accommodated in the corresponding accommodating chambers 111, 112, and 114, respectively. The vane 311 abuts the peripheral wall 130 in the storage chamber 111 to partition the storage chamber 111 into an advance chamber 61 between the shoe 134 and a retard chamber 71 between the shoe 131. The vane 312 abuts the peripheral wall 130 in the storage chamber 112 to partition the storage chamber 112 into an advance chamber 62 between the shoe 131 and a retard chamber 72 between the shoe 132. The vane 314 is disposed in the advance chamber 64 between the protrusion 216 and the shoe 133, and a gap 640 is formed between the vane 314 and the peripheral wall 130 in the advance chamber 64. The vane 314 is sandwiched between the hole forming portion 215 and the front plate 14 in the axial direction of the second vane rotor 31. The vane 314 has a second sliding hole 315 formed therein. The second sliding hole 315 has a cylindrical hole shape that penetrates the vane 314 in the axial direction of the second vane rotor 31, and the relative rotational position of the second vane rotor 31 with respect to the housing 11 is a special most retarded angle position as shown in FIG. 6. Then, as shown in FIG. 7, they are arranged substantially coaxially with the fitting holes 140.

  When the second vane rotor 31 is locked with respect to the first vane rotor 21, as shown in FIGS. 2 and 3, the vane 314 has a contact protrusion 218 of the protrusion 216 from one side in the rotational direction of each vane rotor 21, 31. Abut. As a result of this contact, a gap 641 is formed between the vane 314 and the main body 217 of the protrusion 216, and communicates with the gap 640 through the contact protrusion 218 and the hole forming part 215. As shown in FIG. 6, when the second vane rotor 31 is locked at the special most retarded angle position with respect to the housing 11 by the action of the second piston 51, the vane 314 comes into contact with the shoe 133 and the contact protrusion 218. And the gap 641 is enlarged.

  As shown in FIGS. 8 and 9, the first piston 41 has a columnar shape, and slides by being coaxially fitted in the first sliding hole 219. As shown in FIG. 1, the first piston 41 is fitted to the fitting ring 120 of the sprocket 12 while being fitted to the first sliding hole 219, so that the first vane rotor 21 is moved to the housing 11. Lock to the retarded position. The first piston 41 is provided with an annular groove 410 that opens to the outer peripheral wall surface. At the end of the first piston 41 on the sprocket 12 side, a pressure receiving portion 411 that receives a hydraulic pressure corresponding to an operating state out of the hydraulic pressure supplied to the fitting hole 121 and the hydraulic pressure supplied to the first sliding hole 219 is provided. Yes. A pressure receiving portion 412 that receives the hydraulic pressure supplied to the first sliding hole 219 is provided on the outer peripheral wall of the first piston 41. When hydraulic pressure acts on at least one of the pressure receiving portions 411 and 412, an axial force from the sprocket 12 side toward the second vane rotor 31 side is generated in the first piston 41. At the end of the first piston 41 on the second vane rotor 31 side, a pressure receiving portion 413 that receives the hydraulic pressure corresponding to the operating state of the hydraulic pressure supplied to the first sliding hole 219 and the hydraulic pressure of the advance chamber 64 (see FIG. 8). ) Is provided. When the oil pressure acts on the pressure receiving portion 413, an axial force from the second vane rotor 31 side toward the sprocket 12 side is generated in the first piston 41.

  As shown in FIGS. 1 and 2, the second piston 51 has a stepped cylindrical shape with a bottom and slides coaxially with the first and second sliding holes 219 and 315. A fitting portion 510 having a tapered outer peripheral surface whose diameter is reduced toward the most distal surface is provided at the large-diameter end portion of the second piston 51 on the front plate 14 side. Here, the taper angle of the fitting portion 510 is substantially the same as the taper angle of the fitting hole 140. As shown in FIG. 7, the second piston 51 is fitted to the fitting hole 140 of the front plate 14 by the fitting portion 510 in a state of being fitted to the second sliding hole 315, so that the housing 11 The second vane rotor 31 is locked at the special most retarded position. In the present embodiment, the axial length of the second piston 51 is substantially equal to the sum of the axial lengths of the fitting hole 140 and the second sliding hole 315. Therefore, when the second piston 51 moves to a position where it does not fit with the fitting hole 140 as shown in FIG. 1, the second piston 51 is fitted into both the first and second sliding holes 219 and 315 and the second vane rotor 31 is moved. The first vane rotor 21 is locked. On the other hand, when the second piston 51 moves to a position where the second piston 51 is fitted to the fitting hole 140 as shown in FIG. 7, the second piston 51 is fitted only to the second sliding hole 315 to the second vane rotor 31 with respect to the first vane rotor 21. unlock.

  As shown in FIG. 7, a pressure receiving portion 511 that receives a hydraulic pressure corresponding to an operating state out of the hydraulic pressure supplied to the first sliding hole 219 and the hydraulic pressure of the advance chamber 64 at the small diameter end portion on the bottom side of the second piston 51. Is provided. A pressure receiving portion 512 that receives the hydraulic pressure supplied to the second sliding hole 315 is provided on the outer peripheral wall of the second piston 51. When the hydraulic pressure acts on at least one of the pressure receiving portions 511 and 512, an axial force from the first vane rotor 21 side to the front plate 14 side is generated in the second piston 51. Further, the second piston 51 receives the axial force from the first piston 41 by contacting the first piston 41 in which the axial force is generated by the hydraulic action on at least one of the pressure receiving portions 411 and 412. Furthermore, the second piston 51 receives the restoring force of the elastic member 514 interposed between the front plate 14 and the first vane rotor 21 from the front plate 14 side. Note that the elastic member 514 of the present embodiment is composed of a compression coil spring, and the end opposite to the second piston 51 is configured to slide with respect to the front plate 14.

  The hydraulic pressure supply system 60 shown in FIG. 1 is composed of, for example, a pump, a switching valve and the like. The hydraulic pressure supply system 60 generates a hydraulic pressure that increases and decreases following the rotational speed of the internal combustion engine, and switches between a passage for supplying the hydraulic pressure and a passage for releasing the hydraulic pressure between the advance passage 80 and the retard passage 90. Here, the advance passage 80 and the retard passage 90 are provided in the camshaft 20 and are always in communication with the output port of the hydraulic pressure supply system 60.

  1-3, the sprocket 12 is provided with an advance passage 85, the first vane rotor 21 is provided with advance passages 83, 84, 86, 87, 88, and the second vane rotor 31 is advanced. An angular passage 89 is provided. The advance passage 85 connects between the advance chamber 64 and the fitting hole 121, the advance passage 83 connects between the advance passage 80 and the advance chamber 63, and the advance passage 84 serves as the advance passage. 80 is connected between the advance chamber 64 and the advance passage 86 is connected between the advance chamber 64 and the first sliding hole 219. Therefore, the hydraulic pressure is supplied from the advance passage 80 to the advance chambers 63 and 64 through the advance passages 83 and 84, and further from the advance chamber 64 through the advance passages 85 and 86, respectively, and the fitting hole 121 and the first slide. It is supplied to the hole 219. The advance passage 87 is connected between the advance chamber 64 and the first sliding hole 219, and the advance passage 88 is connected to the first sliding hole 219. The advance passages 87 and 88 communicate with each other through the groove 410 by overlapping with the groove 410 in the radial direction of the first sliding hole 219 as shown in FIG. Since the overlap with the path 410 is eliminated, the mutual communication is blocked. As shown in FIGS. 2 and 8, the advance passage 89 connected to the advance chambers 61 and 62 overlaps the advance passage 88 in the axial direction of the vane rotors 21 and 31 in an arbitrary operation state, so that the passage 88 Always in communication. As described above, the hydraulic pressure supplied to the advance chamber 64 is supplied to the advance chambers 61 and 62 through the advance passages 87, 88 and 89 when the advance passages 87 and 88 communicate with each other. On the other hand, when the communication between the advance passages 87 and 88 is blocked, the hydraulic pressure supply from the advance chamber 64 to the advance chambers 61 and 62 is restricted.

  As shown in FIGS. 1 and 2, the sprocket 12 is provided with retardation passages 91, 92, 93, 94, the first vane rotor 21 is provided with a retardation passage 95, and the second vane rotor 31 is provided with a retardation passage. 96 is provided. The retard passage 91 connects between the retard passage 90 and the retard chamber 71, the retard passage 92 connects between the retard passage 90 and the retard chamber 72, and the retard passage 93 serves as the retard passage. 90 and the retarding chamber 73 are connected, and the retarding passage 94 connects between the retarding passage 90 and the retarding chamber 74. Therefore, the hydraulic pressure is supplied from the retard passage 90 to the retard chambers 71, 72, 73, 74 through the retard passages 91, 92, 93, 94, respectively. The retard passage 95 is connected to the first sliding hole 219, and particularly when the first and second pistons 41 and 51 are separated as shown in FIG. 7, a pressure chamber 97 formed between the pistons 41 and 51 and Communicate. The retard passage 96 connected to the storage chamber 113 communicates with the passage 95 by overlapping with the retard passage 95 in the axial direction of the vane rotors 21 and 31 as shown in FIG. 2, as shown in FIG. The communication with the passage 95 is blocked by eliminating the overlap with the retard passage 95. Further, in the present embodiment, as the passages 95 and 96 are cut off from each other, the vane 213 blocks the connection portion 98 between the accommodation chamber 113 and the retarding passage 96 as shown in FIGS. The communication between the retard chamber 73 and the retard passage 96 is blocked. As described above, when a communication state is ensured between the retard chamber 73 and the retard passage 96, the hydraulic pressure supplied to the retard chamber 73 is supplied to the first sliding hole 219 through the retard passages 95 and 96. On the other hand, when the communication between the retard chamber 73 and the retard passage 96 is interrupted, the hydraulic pressure supply from the retard chamber 73 to the first sliding hole 219 is restricted.

Next, the operation of the first embodiment will be described.
(1) While the internal combustion engine is stopped, the vane rotors 21 and 31 are held at the most retarded position with respect to the housing 11 as shown in FIG. 2, so that the holes 121, 140, and 219 as shown in FIGS. , 315 are arranged substantially coaxially. At this time, since the hydraulic pressure supply system 60 stops the supply of hydraulic pressure, the first piston 41 is fitted into the first sliding hole 219 and the fitting ring 120, and the second piston 51 is fed into the first and second slides. The moving holes 219 and 315 are fitted, but not fitted into the fitting holes 140.

(2) When the internal combustion engine is started, first, the hydraulic pressure supply system 60 supplies hydraulic pressure to the retarding passage 90. As a result, the hydraulic pressure is supplied to the retarding chambers 71, 72, 73, 74. Further, the hydraulic pressure supplied to the retarding chamber 73 is supplied to the first sliding hole 219 through retarding passages 95 and 96 communicating with each other as shown in FIG. At this time, as shown in FIG. 1, the first sliding hole 219 communicates with the second sliding hole 315 around the pressure receiving portion 512, so that the hydraulic pressure supplied to the first sliding hole 219 passes through the second sliding hole 315. It acts on the pressure receiving part 512. Here, since the hydraulic pressure supplied from the hydraulic pressure supply system 60 in the initial stage of the start is lower than the set pressure P _th (for example, 200 kPa), the second piston 51 that receives the restoring force of the elastic member 514 is engaged with the moving holes 219 and 315. The combined state and the non-fitted state with the fitting hole 140 are maintained. Accordingly, the second vane rotor 31 is locked to the first vane rotor 21, but is not locked to the housing 11. At this time, since the hydraulic pressure is not supplied to the fitting hole 121 around the pressure receiving portion 411 and the first sliding hole 219 around the pressure receiving portion 412 through the advance passages 85 and 86, the first piston 41 has the fitting ring 120. And the first vane rotor 21 is locked to the housing 11. Since the first vane rotor 21 locked with the second vane rotor 31 is locked with respect to the housing 11, the vane rotors 21 and 31 collide with the housing 11 due to fluctuating torque transmitted from the intake valve to the camshaft 20. A situation where sound is generated can be prevented.

(3) Subsequently, the hydraulic pressure supply system 60 supplies the hydraulic pressure to the advance passage 80 while releasing the hydraulic pressure from the retard passage 90. Accordingly, the hydraulic pressure is supplied to the advance chambers 63 and 64 while the hydraulic pressure is released from the surroundings of the retard chambers 71, 72, 73 and 74 and the pressure receiving portion 512. Further, the hydraulic pressure supplied to the advance chamber 64 communicates with the advance passages 87 and 88 that communicate with each other through the groove 410 as shown in FIGS. 1 and 3, and with the advance passage 88 as shown in FIGS. To the advance chambers 61 and 62 through the advance passage 89. Further, the hydraulic pressure supplied to the advance chamber 64 is supplied to the fitting hole 121 and the first sliding hole 219 through the advance passages 85 and 86 and acts on the pressure receiving portions 411 and 412. As a result, as shown in FIG. 10, the first piston 41 is engaged with the fitting ring while pressing the second piston 51 against the restoring force of the elastic member 514 by the axial force generated toward the second vane rotor 31 side. Leave 120. Here, the second piston 51 pressed by the first piston 41 moves to the front plate 14 side, but since the hydraulic pressure supplied from the hydraulic pressure supply system 60 is lower than the set pressure P _{th in the} initial stage of the start, It does not come off from the first sliding hole 219. Therefore, the second piston 51 cannot be fitted into the fitting hole 140. As described above, the first vane rotor 21 is unlocked with respect to the housing 11, and the second vane rotor 31 is locked with respect to the first vane rotor 21, but not with respect to the housing 11.

(4) Immediately after the first piston 41 is detached, the hydraulic pressure supply system 60 continues to supply hydraulic pressure less than the set pressure P _th to the advance passage 80. As a result, the hydraulic pressure supply to the advance chambers 61, 62, 63, 64 proceeds, so that the first vane rotor 21 rotates relative to the advance side with respect to the housing 11 as shown in FIG. 4. At this time, since the second piston 51 is sandwiched between the sprocket 12 and the front plate 14 together with the first piston 41 as shown in FIG. 5, the sliding hole 219 does not depend on the hydraulic pressure around the pressure receiving portions 411, 412, 512. , 315 is maintained in the fitted state. As a result, the second vane rotor 31 remains locked with respect to the first vane rotor 21, so that both the vane rotors 21 and 31 are integrally rotated relative to the advance side with respect to the housing 11 as shown in FIG. 4. Thus, the valve timing is advanced.

(5) After this, while the hydraulic pressure supplied from the hydraulic pressure supply system 60 is less than the set pressure _Pth , an operation suitable for the operation of the internal combustion engine is performed among the low pressure holding operation, the low pressure advance operation, and the low pressure retard operation. Is done. Here, the low pressure holding operation is an operation in which the hydraulic pressure supply system 60 blocks communication between the output port and the passages 80 and 90. According to this low pressure holding operation, the internal pressures of the advance chambers 61, 62, 63, 64 and the retard chambers 71, 72, 73, 74 are held, so that the first and second vane rotors 21, 31 are moved relative to the housing 11. Thus, the relative rotation stops and the valve timing is maintained. On the other hand, the low pressure advance operation is an operation in which the hydraulic pressure supply system 60 supplies the hydraulic pressure to the advance passage 80 while extracting the hydraulic pressure from the retard passage 90. According to this low pressure advance operation, both the vane rotors 21 and 31 rotate relative to the advance side with respect to the housing 11 in accordance with the operation (4), and the valve timing is advanced. On the other hand, the low pressure retarding operation is an operation in which the oil pressure supply system 60 supplies the oil pressure to the retarding passage 90 while removing the oil pressure from the advancement passage 80. According to this low-pressure retarding operation, the hydraulic pressure is supplied to the retarding chambers 71, 72, 73, 74 while the hydraulic pressure is being removed from the advance chambers 61, 62, 63, 64, but the same as in the case of (4) above. In principle, the second piston 51 maintains the fitted state with the sliding holes 219 and 315. Therefore, the vane rotors 21 and 31 are integrally rotated relative to the retard side with respect to the housing 11, and the valve timing is retarded.

(6) After the supply hydraulic pressure becomes equal to or higher than the set pressure P _th , when the vane rotors 21 and 31 reach the most retarded position in FIG. The axial force generated in the second piston 51 by the hydraulic pressure overcomes the restoring force of the elastic member 514. At this time, the second piston 51 is slightly eccentric with respect to the fitting hole 140 as shown in FIG. 11, but the second piston 51 receiving the axial force is the first piston 41 as shown in FIGS. Then, the tapered fitting portion 510 is fitted into the tapered hole fitting hole 140 while being separated from the first sliding hole 219. Accordingly, the second piston 51 relatively rotates the second vane rotor 31 located at the most retarded position with respect to the housing 11 to the special most retarded position in FIG. Here, since the first vane rotor 21 from which the second piston 51 is detached remains in the most retarded position, the second vane rotor 31 also rotates relative to the first vane rotor 21. As a result, the second piston 51 is slightly decentered with respect to the first sliding hole 219 as shown in FIG. 13 and is sandwiched between the first vane rotor 21 and the front plate 14. Return to the first sliding hole 219 is prevented. As a result, the lock of the second vane rotor 31 with respect to the first vane rotor 21 is released, and the second vane rotor 31 is locked with respect to the housing 11.

  As shown in FIG. 12, the hydraulic pressure in the pressure chamber 97 generated by the separation of the second piston 51 from the first piston 41 acts on the pressure receiving portion 511 to generate axial force, thereby fitting the second piston 51. The insertion into the hole 140 is promoted. At the same time, the hydraulic pressure in the pressure chamber 97 acts on the pressure receiving portion 413 to generate an axial force on the first piston 41, thereby fitting the first piston 41 into the fitting ring 120 as shown in FIGS. As a result of the fitting between the first piston 41 and the fitting ring 120, the first vane rotor 21 is reliably held at the most retarded position, although the second vane rotor 31 rotates relative to the housing 11.

(7) Immediately after the second piston 51 is disengaged, when the hydraulic pressure supply system 60 releases the hydraulic pressure from the retard passage 90 and supplies the hydraulic pressure higher than the set pressure P _th to the advance passage 80, the retard chambers 71, 72, The hydraulic pressure is supplied to the advance chambers 63 and 64 while the hydraulic pressure is released from around 73 and 74 and the pressure receiving portions 511 and 512. Accordingly, the first piston 41 is detached from the fitting ring 120 as shown in FIG. 14 on the same principle as in the case of (3) above, so that the lock of the first vane rotor 21 with respect to the housing 11 is released. At this time, since the hydraulic pressure supplied to the fitting hole 121 and the first sliding hole 219 through the advance passages 85 and 86 is high, the first piston 41 receiving the hydraulic pressure at the pressure receiving portions 411 and 412 is The two-vane rotor 31 moves until it is locked to the second piston 51 between the elements 21 and 14. As a result, the first piston 41 blocks communication between the advance passages 87 and 88, so that the hydraulic pressure supply from the advance chamber 64 to the advance chambers 61 and 62 is restricted.

(8) After the first piston 41 is disengaged, the hydraulic pressure supply system 60 continues to supply the hydraulic pressure above the set pressure P _th to the advance passage 80. As a result, the hydraulic pressure supply to the advance chambers 63 and 64 proceeds, so that the first vane rotor 21 rotates relative to the advance side with respect to the housing 11 as shown in FIG. At this time, the vane 314 in the advance chamber 64 is pressed against the retard-side shoe 133 by the hydraulic pressure of the gap 641 between the advance chamber 64 and the vane 214. At this time, as shown in FIG. 9, the second piston 51 is held between the first vane rotor 21 and the front plate 14 to maintain the fitting state with the fitting hole 140. Further, at this time, a part of the pressure receiving part 413 is exposed to the advance angle chamber 64, so that the hydraulic pressure in the advance angle chamber 64 is supplied not only around the pressure receiving parts 411 and 412 but also around the pressure receiving part 413. Here, since the axial force generated by the hydraulic pressure around the pressure receiving portion 413 is smaller than the axial force generated by the hydraulic pressure around the pressure receiving portions 411 and 412, as shown in FIG. , 88 is blocked at the position where the supply of hydraulic pressure to the advance chambers 61, 62 is restricted. From these things, even if the 1st vane rotor 21 rotates relatively with respect to the housing 11, the 2nd vane rotor 31 is locked to the special most retarded angle position, without following it. Thus, the valve timing is advanced.

(9) Thereafter, an operation suitable for the operation of the internal combustion engine among the high pressure holding operation, the high pressure advance operation, and the high pressure retard operation is performed. Here, the high pressure holding operation conforms to the low pressure holding operation of (5) above. On the other hand, the high pressure advance operation is an operation in which the hydraulic pressure supply system 60 supplies a hydraulic pressure equal to or higher than the set pressure P _{th to the} advance angle passage 80 while releasing the oil pressure from the retard angle passage 90. According to this high pressure advance operation, only the first vane rotor 21 rotates relative to the advance side with respect to the housing 11 in accordance with the operation of (8), and the valve timing is advanced. On the other hand, the high-pressure retarding operation is an operation in which the hydraulic pressure supply system 60 supplies a hydraulic pressure equal to or higher than the set pressure _Pth to the retarding passage 90 while extracting the hydraulic pressure from the advancement passage 80. According to this high pressure retarding operation, hydraulic pressure is supplied to the retarding chambers 71, 72, 73, 74 while the hydraulic pressure is being removed from around the advance chambers 63, 64 and the pressure receiving portions 411, 412, 413. The second piston 51 maintains the fitting state with the fitting hole 140 on the same principle as in the case of. Therefore, only the first vane rotor 21 rotates relative to the retard side with respect to the housing 11 while the second vane rotor 31 is locked to the housing 11, and the valve timing is retarded. At this time, since the communication between the retard chamber 73 and the retard passage 96 is cut off as shown in FIG. 8 except for the vicinity of the most retarded position of the first vane rotor 21, the hydraulic pressure supplied to the retard chamber 73. Can be prevented from reaching the advance chamber 64 through the first sliding hole 219.

According to a first embodiment described above, a predetermined time to supply from the hydraulic supply system 60 hydraulic pressure becomes less than the set pressure P _th, the second vane rotor 31 is locked to the first vane rotor 21. At the same time, the hydraulic pressure supply to all of the advance chambers 61, 62, 63, 64 and the retard chambers 71, 72, 73, 74 is allowed. As a result, both of the vane rotors 21 and 31 can be rotated relative to the housing 11, but the vanes 214 and 314 oscillate like a single vane in the storage chamber 114 during the relative rotation. It can be considered that the number of vanes contributing to the relative rotation is substantially four.

On the other hand, when the supply hydraulic pressure from the hydraulic supply system 60 is equal to or higher than the set pressure P _th , the second vane rotor 31 is locked to the housing 11, but the first vane rotor 21 is unlocked. The At the same time, the hydraulic pressure supply to the advance chambers 61 and 62 that are in contact with the second vane rotor 31 among the advance chambers 61, 62, 63, and 64 is restricted. As a result, the second vane rotor 31 can be held at the most retarded position with respect to the housing 11 and only the first vane rotor 21 can be relatively rotated, so that the number of vanes contributing to the relative rotation can be reduced to two. . Further, since the vanes 311 and 312 do not oscillate in the advance chambers 61 and 62 in which the hydraulic pressure supply is restricted, it is possible to prevent the internal pressure of the advance chambers 61 and 62 from being lowered.

  According to the first embodiment, when the hydraulic pressure supplied from the hydraulic pressure supply system 60 is low, the desired operation is ensured by substantially setting the number of vanes to four, and when the hydraulic pressure is high, the number of vanes is reduced to two. It is possible to increase the operation responsiveness by suppressing the generation of the operating resistance while reducing the required amount of hydraulic oil to a minimum.

  Furthermore, according to the first embodiment, when the second vane rotor 31 is locked with respect to the first vane rotor 21, the vanes 214 and 314 of the respective vane rotors 21 and 31 abut on each other in the rotation direction. Thereby, for example, when both the vane rotors 21, 31 rotate relative to the retard side with respect to the housing 11, the rotational torque due to the hydraulic pressure in the retard chamber 74 passes from the first vane rotor 21 to the second vane rotor 31 through the contact interface of the vanes 214, 314. Is transmitted to. Therefore, at this time, since the rotational torque is not transmitted through the second piston 51 fitted to both the vanes 214 and 314, it is possible to avoid a decrease in durability caused by the occurrence of shear stress in the second piston 51. it can.

  In the first embodiment thus far, the storage chambers 113 and 114 correspond to the “first storage chamber” described in the claims, respectively, and the vanes 213 and 214 respectively correspond to the “first storage chamber” described in the claims. Equivalent to “one vane”. In the first embodiment, the storage chambers 111 and 112 correspond to the “second storage chamber” described in the claims, respectively, and the vanes 311 and 312 each correspond to the “second vane” described in the claims. The vane 314 corresponds to the “third vane” recited in the claims. Furthermore, in 1st embodiment, the 2nd piston 51 is equivalent to the "lock means" and "lock member" as described in a claim, and the fitting hole 140 is a "fitting hole" as described in a claim. The first piston 41 corresponds to “supply control means” and “supply control member” recited in the claims. In the first embodiment, the crankshaft corresponds to the “drive shaft” recited in the claims, the camshaft 20 corresponds to the “driven shaft” recited in the claims, and the hydraulic pressure supply system 60 includes This corresponds to “fluid pressure supply means” recited in the claims.

(Second embodiment)
As shown in FIGS. 15 and 16, the second embodiment of the present invention is a modification of the first embodiment.
In 2nd embodiment, the fitting hole 146 provided in the front plate 14 is cylindrical hole shape, and the outer peripheral surface of the fitting part 516 of the 2nd piston 51 is cylindrical surface shape. When the relative rotation position of the second vane rotor 31 with respect to the housing 11 is the most advanced angle position as shown in FIG. 15, the second sliding hole 315 is substantially coaxial with the fitting hole 146 as shown in FIGS. line up. The second piston 51 is fitted in the fitting hole 146 by the fitting portion 516 in a state where the second piston 51 is fitted in the second sliding hole 315, so that the second vane rotor 31 is moved to the most advanced position with respect to the housing 11. Lock it. In the present embodiment, the axial length of the second piston 51 is longer than the axial length of the second sliding hole 315 and shorter than the sum of the axial lengths of the fitting hole 140 and the second sliding hole 315. . Therefore, when the second piston 51 moves to a position where it does not fit in the fitting hole 146 as shown in FIG. 16, it fits in both the first and second sliding holes 219 and 315 to cause the second vane rotor 31 to move. The first vane rotor 21 is locked. On the other hand, when the second piston 51 moves to a position where it is fitted with the fitting hole 146 as shown in FIG. 17, the second piston 51 is fitted into only the second sliding hole 315 and the second vane rotor 31 with respect to the first vane rotor 21. unlock.

  At the end of the second sliding hole 315 on the first vane rotor 21 side, a tapered hole 316 having an inner peripheral surface whose diameter increases toward the most distal surface is provided. In addition, a tapered portion 416 having an outer peripheral surface whose diameter is reduced toward the foremost surface is provided at the end of the first piston 41 on the second vane rotor 31 side. In the present embodiment, since the axial length of the second piston 51 is set as described above, when the second piston 51 is fitted into the fitting hole 146 as shown in FIG. It can enter the second sliding hole 315 from the hole 316 side and can contact the second piston 51. In this embodiment, the taper angle of the taper hole 316 and the taper part 416 is substantially the same, and the minimum diameter of the taper part 416 is smaller than the minimum diameter of the taper hole 316. Therefore, in a state where the tapered portion 416 enters the second sliding hole 315, a gap 317 is formed between the tapered hole portion 316 and the tapered portion 416.

  As shown in FIG. 15, the protruding portion 220 of the vane 214 of the first vane rotor 21 has a configuration in which the abutting protrusion 218 protrudes from the side wall surface of the main body 217 toward the retarding chamber 74 and advances more than the hole forming portion 215. It is arranged on the corner chamber 64 side. The vane 314 is not provided in the second vane rotor 31, and instead, a vane 318 disposed in the retardation chamber 74 between the protrusion 220 and the shoe 134 is provided. The vane 318 has a second sliding hole 315, and a gap 740 is formed between the vane 318 and the peripheral wall 130 in the retard chamber 74. When the second vane rotor 31 is locked with respect to the first vane rotor 21 by the action of the second piston 51, the contact protrusion 218 of the protrusion 220 is arranged in the rotational direction of each vane rotor 21, 31 as shown in FIGS. It abuts on the vane 318 from one side. By this contact, a gap 741 is formed between the vane 318 and the main body 217 of the protrusion 220 so as to communicate with the gap 740 between the contact protrusion 218 and the hole forming portion 215.

The first vane rotor 21 is not provided with the advance passage 86, and instead, is provided with a retard passage 99 that connects between the retard chamber 74 and the first sliding hole 219. Therefore, the hydraulic pressure supplied to the retard chamber 74 is supplied to the first sliding hole 219 through the retard passage 99. As shown in FIGS. 18 and 19, the vane rotors 21 and 31 are not provided with the retard passages 95 and 96 to which the hydraulic pressure is supplied from the retard chamber 73.
In the present embodiment, the communication between the advance passages 88 and 89 is blocked when the operation state shown in FIGS. 21 and 25 is reached, and the advance passages 88 and 89 are connected in other operation states.

Next, the operation of the second embodiment will be described.
(I) While the internal combustion engine is stopped, a state according to (1) of the first embodiment except that only the fitting hole 121 and the sliding holes 219 and 315 are arranged substantially coaxially as shown in FIG. It becomes.
(II) When the hydraulic pressure supply system 60 starts supplying hydraulic pressure to the retarding passage 90 by starting the internal combustion engine, the hydraulic pressure is supplied to the retarding chambers 71, 72, 73, 74. At this time, as shown in FIG. 19, the first piston 41 blocks communication between the retarding passage 99 and the first sliding hole 219, so that the hydraulic pressure in the retarding chamber 74 is not supplied around the pressure receiving portion 412. Therefore, the second piston 51 maintains the fitted state with the sliding holes 219 and 315 by the restoring force of the elastic member 514. At this time, since the hydraulic pressure is not supplied to the fitting hole 121, the first piston 41 maintains the fitting state with the fitting ring 120. As described above, the second vane rotor 31 is locked to the first vane rotor 21 and the first vane rotor 21 is locked to the housing 11.

(III) Subsequently, when the hydraulic pressure supply system 60 releases the hydraulic pressure from the retard passage 90 and supplies the hydraulic pressure to the advance passage 80, the advance chamber is released while the hydraulic pressure is released from the retard chambers 71, 72, 73, 74. Oil pressure is supplied to 63 and 64. Further, the hydraulic pressure supplied to the advance chamber 64 communicates with the advance passages 87 and 88 that communicate with each other via the groove 410 as shown in FIGS. 19 and 20 and the advance passage 88 as shown in FIGS. To the advance chambers 61 and 62 through the advance passage 89. Further, since the hydraulic pressure supplied to the advance chamber 64 is supplied to the fitting hole 121 around the pressure receiving portion 411 through the advance passage 85, the first piston 41 resists the restoring force of the elastic member 514 and the second piston 51. While being pressed, it is detached from the fitting ring 120 as shown in FIG. Since this time the oil pressure supplied from the hydraulic supply system 60 is lower than the set pressure P _th, the second piston 51 does not lead to disengaged from the first sliding hole 219. Accordingly, the first vane rotor 21 is unlocked with respect to the housing 11, but the second vane rotor 31 remains locked with respect to the first vane rotor 21.

(IV) Immediately after the first piston 41 is detached, if the hydraulic pressure supply system 60 continues to release the hydraulic pressure from the retard passage 90 and supply the hydraulic pressure less than the set pressure P _th to the advance passage 80, the advance chambers 61, 62, Since the hydraulic pressure supply to 63 and 64 proceeds, the first vane rotor 21 rotates relative to the advance side with respect to the housing 11 as shown in FIG. At this time, as shown in FIG. 16, since the first piston 41 allows the retard passage 99 and the first sliding hole 219 to communicate with each other, the hydraulic pressure is applied from the first sliding holes 219 around the pressure receiving portions 411 and 412. It is pulled out through the retarding chamber 74. As a result, the second piston 51 is in a state where the first piston 41 is pressed against the sprocket 12 by the restoring force of the elastic member 514. Therefore, even if the second sliding hole 315 is aligned with the fitting hole 146 when the relative rotational position of the second vane rotor 31 with respect to the housing 11 is the most advanced angle position, the second piston 51 is fitted with the fitting hole 146. Instead, the fitted state with the sliding holes 219 and 315 is maintained. Thereby, since the second vane rotor 31 remains locked with respect to the first vane rotor 21, both the vane rotors 21, 31 are integrally rotated relative to the advance side with respect to the housing 11, as shown in FIG. The valve timing is advanced.

(V) Thereafter, as long as the hydraulic pressure supplied from the hydraulic pressure supply system 60 is less than the set pressure _Pth , an operation suitable for the operation of the internal combustion engine is performed among the low pressure holding operation, the low pressure advance operation, and the low pressure retard operation. Is done. Here, the low pressure holding operation conforms to the low pressure holding operation (5) of the first embodiment. On the other hand, in the low pressure advance operation, both vane rotors 21, 31 are moved relative to the advance side with respect to the housing 11 in accordance with the operation (IV) by releasing the hydraulic pressure from the retard passage 90 and supplying the hydraulic pressure to the advance passage 80. Rotates and the valve timing advances. On the other hand, in the low pressure retarded operation, the hydraulic pressure is released from the advance chambers 61, 62, 63, 64 and the retard chambers 71, 72, The hydraulic pressure is supplied to the first sliding holes 219 around the pressure receiving portions 411 and 412 through 73 and 74 and the retarding passage 99. At this time, since the hydraulic pressure supply around the pressure receiving portions 411 and 412 is low, the second piston 51 presses the first piston 41 against the sprocket 12 by the restoring force of the elastic member 514 and is fitted to the sliding holes 219 and 315. To maintain. Therefore, the vane rotors 21 and 31 are integrally rotated relative to the retard side with respect to the housing 11, and the valve timing is retarded.

(VI) After the supply hydraulic pressure becomes equal to or higher than the set pressure P _th , when the vane rotors 21 and 31 reach the most advanced angle position in FIG. In accordance with the operation, the hydraulic pressure supply system 60 releases the hydraulic pressure from the advance passage 80 and supplies the hydraulic pressure to the retard passage 90. Thereby, since the hydraulic pressure is supplied from the retard chamber 74 around the pressure receiving portions 411 and 412, the first piston 41 presses the second piston 51 toward the front plate 14, but the supplied hydraulic pressure is high. Therefore, as shown in FIG. 17, the tapered portion 416 enters the tapered hole portion 316 of the second sliding hole 315. As a result, the second piston 51 is fitted into the fitting hole 146 at the same time as it is detached from the first sliding hole 219. Accordingly, the lock of the second vane rotor 31 with respect to the first vane rotor 21 is released, and the second vane rotor 31 is locked with respect to the housing 11.

(VII) Immediately after the second piston 51 is disengaged, if the hydraulic pressure supply system 60 continues to supply the hydraulic pressure equal to or higher than the set pressure P _th to the retard passage 90, the first vane rotor 21 at the most advanced angle position is retarded chambers 71, 72. , 73, 74 receives rotational torque on the retard side with respect to the housing 11 by the hydraulic pressure supplied to the housing 11. As a result, the first vane rotor 21 rotates relative to the retard side with respect to the housing 11 by the gap 317 between the taper hole 316 and the taper part 416, and the taper part 416 contacts the taper hole 316 as shown in FIG. Let At this time, since the second vane rotor 31 is locked at the most retarded position by fitting the second piston 51 into the fitting hole 146, when the tapered portion 416 comes into contact with the tapered hole portion 316, The rotational torque transmitted to one piston 41 is converted into an axial force toward the sprocket 12 side. As a result, since the axial force due to the rotational torque becomes larger than the axial force due to the hydraulic pressure around the pressure receiving portions 411 and 412, the first vane rotor 21 is moved while the taper portion 416 escapes from the taper hole portion 316 as shown in FIG. It further rotates relative to the housing 11. Therefore, even if the second piston 51 is pressed against the first vane rotor 21 side by the restoring force of the elastic member 514, it is difficult to return to the first sliding hole 219 that is off-axis.

(VIII) Immediately after the taper portion 416 escapes, if the hydraulic pressure supply system 60 continues to supply the hydraulic pressure higher than the set pressure P _th to the retard passage 90, the hydraulic pressure supply to the retard chambers 71, 72, 73, 74 proceeds. Therefore, as shown in FIG. 21, the first vane rotor 21 rotates relative to the retard side with respect to the housing 11. At this time, the second piston 51 in which the pressure receiving portion 511 is exposed to the retard chamber 74 receives the axial force toward the front plate 14 and maintains the fitted state with the fitting hole 146. At this time, the vane 318 in the retarding chamber 74 is pressed against the shoe 134 on the advance side by the hydraulic pressure in the gap 741 between the vane 214 and the vane 214. From these things, even if the 1st vane rotor 21 rotates relatively with respect to the housing 11, the 2nd vane rotor 31 is locked to the most advanced position without following it. As a result, the valve timing is retarded. In this retarding operation, a part of the pressure receiving portion 413 is exposed to the retarding chamber 74, so that the hydraulic pressure in the retarding chamber 74 is supplied not only around the pressure receiving portions 411 and 412 but also around the pressure receiving portion 413. The Here, since the axial force generated by the hydraulic pressure around the pressure receiving portion 413 is smaller than the axial force generated by the hydraulic pressure around the pressure receiving portions 411 and 412, the first piston 41 has an advance passage 87 as shown in FIG. 25. , 88 are blocked at a position where communication between them is blocked. As a result, even if the first vane rotor 21 is pushed toward the retard side with respect to the housing 11 by fluctuating torque or the like and the advance chamber 64 is compressed, the advance chamber 64 is advanced to the advance chambers 61 and 62. Hydraulic leakage can be regulated.

(IX) Thereafter, an operation suitable for the operation of the internal combustion engine among the high pressure holding operation, the high pressure retarding operation, and the high pressure advance operation is performed. Here, the high pressure holding operation is in accordance with the low pressure holding operation (5) of the first embodiment. On the other hand, in the high pressure retarded operation, only the first vane rotor 21 is moved to the housing 11 in accordance with the operation of (VIII) by _releasing the hydraulic pressure from the advance passage 80 and supplying the hydraulic pressure higher than the set pressure P _th to the retard passage 90. The valve timing is retarded by relative rotation to the retarded angle side. On the other hand, in the high pressure advance operation, the hydraulic pressure is released from the retard chambers 71, 72, 73, 74 and advanced by supplying the hydraulic pressure from the retard passage 90 and supplying the hydraulic pressure higher than the set pressure P _th to the advance passage 80. Hydraulic supply to the corner chambers 63 and 64 is realized. At this time, the hydraulic pressure is released from around the pressure receiving portions 411, 412, and 413 through the retard chamber 74, so that the first piston 41 is held at the communication blocking position between the advance passages 87 and 88 and advanced from the advance chamber 64. The hydraulic pressure supply to the corner chambers 61 and 62 is restricted. At this time, the second piston 51 is completely disengaged from the fitting hole 146 during the high pressure advance operation because the hydraulic pressure release from the retard chamber 74 is made slower than the hydraulic pressure supply to the advance chambers 63 and 64. There is no way to leave. Therefore, only the first vane rotor 21 rotates relative to the advance side with respect to the housing 11 while the second vane rotor 31 is locked to the housing 11, and the valve timing is advanced.

Also according to the second embodiment described above, when the supply hydraulic pressure from the hydraulic supply system 60 is low, a desired operation is ensured by substantially setting the number of vanes to four, and when the supply hydraulic pressure is high, two vanes are used. It is possible to increase the operation responsiveness by suppressing the generation of operating resistance while reducing the required amount of hydraulic oil.
In the second embodiment thus far, the vane 318 corresponds to the “third vane” recited in the claims, and the fitting hole 146 corresponds to the “fitting hole” recited in the claims. .

(Third embodiment)
As shown in FIGS. 26 and 27, the third embodiment of the present invention is a modification of the first embodiment.
In the third embodiment, the fitting hole 140 is not provided in the front plate 14, and the fitting part 510 is not provided in the second piston 51 accordingly. Therefore, in this embodiment, the second piston 51 does not have a function of fitting the front plate 14 and locking the second vane rotor 31 with respect to the housing 11.

  The axial length of the second piston 51 is substantially equal to the axial length of the second sliding hole 315 in the present embodiment. Therefore, when the second piston 51 is moved to a position away from the front plate 14 as shown in FIG. 27, the second piston 51 is fitted into both the first and second sliding holes 219 and 315 and the second vane rotor 31 is moved to the first. Locks to the vane rotor 21. On the other hand, as shown in FIG. 28, when the second piston 51 moves to a position where it abuts against the front plate 14, it fits only in the second sliding hole 315 to lock the second vane rotor 31 with respect to the first vane rotor 21. To release.

  As shown in FIG. 26, the vane rotors 21 and 31 are not provided with the retard passages 95 and 96 to which the hydraulic pressure is supplied from the retard chamber 73. In the present embodiment, the arrangement positions of the set of the storage chamber 112 and the vane 312 and the set of the storage chamber 113 and the vane 213 are interchanged. That is, the storage chamber 112 that stores the vane 312 is disposed between the shoes 132 and 133, and the storage chamber 113 that stores the vane 213 is disposed between the shoes 131 and 132. Therefore, the vane 312 partitions the storage chamber 112 into an advance chamber 62 between the shoe 132 and a retard chamber 72 between the shoe 133, and the vane 213 connects the storage chamber 113 with the shoe 131. It is divided into an advance angle chamber 63 and a retard angle chamber 73 between the shoe 132.

Next, the operation of the third embodiment will be described.
(I) While the internal combustion engine is stopped, a state according to (1) of the first embodiment, except that only the fitting hole 121 and the sliding holes 219 and 315 are arranged substantially coaxially as shown in FIG. It becomes.
(Ii) When the hydraulic pressure supply system 60 starts supplying hydraulic pressure to the retarding passage 90 by starting the internal combustion engine, the hydraulic pressure is supplied to the retarding chambers 71, 72, 73, 74. At this time, since the hydraulic pressure is not supplied to the fitting hole 121 and the first sliding hole 219 around the pressure receiving portions 411 and 412, the second piston 51 receiving the restoring force of the elastic member 514 itself And the fitting state between the first piston 41 and the fitting ring 120 are maintained. Thus, the second vane rotor 31 is locked to the first vane rotor 21 and the first vane rotor 21 is locked to the housing 11.

(Iii) Subsequently, when the hydraulic pressure supply system 60 releases hydraulic pressure from the retard passage 90 and supplies hydraulic pressure to the advance passage 80, the advance chamber is released while the hydraulic pressure is released from the retard chambers 71, 72, 73, 74. Oil pressure is supplied to 63 and 64. In addition, the hydraulic pressure supplied to the advance chamber 64 is advanced to the advance passages 87 and 88 that communicate with each other via the groove 410 as shown in FIG. 27 and the advance passage 88 that communicates with the advance passage 88 as shown in FIGS. It is supplied to the advance chambers 61 and 62 through the angular passage 89. Furthermore, since the hydraulic pressure supplied to the advance chamber 64 is supplied around the pressure receiving portions 411 and 412 through the advance passages 85 and 86, the first piston 41 presses the second piston 51 as shown in FIG. Detach from the fitting ring 120. Since this time the oil pressure supplied from the hydraulic supply system 60 is lower than the set pressure P _th, the second piston 51 without departing from the first sliding hole 219. Accordingly, the first vane rotor 21 is unlocked with respect to the housing 11, but the second vane rotor 31 remains locked with respect to the first vane rotor 21.

(Iv) Immediately after the first piston 41 is disengaged, if the hydraulic pressure supply system 60 continues to supply hydraulic pressure less than the set pressure P _th to the advance passage 80, the hydraulic pressure supply to the advance chambers 61, 62, 63, 64 proceeds. Therefore, as shown in FIG. 30, the first vane rotor 21 rotates relative to the advance side with respect to the housing 11. At this time, since the hydraulic pressure supplied from the advance chamber 64 around the pressure receiving portions 411 and 412 is lower than the set pressure P _th , the restoring force of the elastic member 514 causes the second piston 51 to move as shown in FIG. The piston 41 is pressed against the sprocket 12 to maintain the fitted state with the sliding holes 219 and 315. As a result, since the second vane rotor 31 remains locked with respect to the first vane rotor 21, both the vane rotors 21, 31 are integrally rotated relative to the advance side with respect to the housing 11, as shown in FIG. The valve timing is advanced.

(V) Thereafter, as long as the hydraulic pressure supplied from the hydraulic pressure supply system 60 is less than the set pressure _Pth , an operation suitable for the operation of the internal combustion engine is performed among the low pressure holding operation, the low pressure advance operation, and the low pressure retard operation. Is done. Here, the low pressure holding operation conforms to the low pressure holding operation (5) of the first embodiment. On the other hand, in the low pressure advance operation, both the vane rotors 21 and 31 are moved relative to the advance side with respect to the housing 11 in accordance with the operation (iv) by releasing the hydraulic pressure from the retard passage 90 and supplying the hydraulic pressure to the advance passage 80. Rotates and the valve timing advances. On the other hand, in the low pressure retarded operation, the hydraulic pressure is released from the advance chambers 61, 62, 63, 64 and the retard chambers 71, 72, Hydraulic supply to 73 and 74 is realized. At this time, since the hydraulic pressure is released from the pressure receiving portions 411 and 412 through the advance chamber 64, the second piston 51 presses the first piston 41 against the sprocket 12 by the restoring force of the elastic member 514 and the sliding holes 219 and 315. And maintain the mating state. Therefore, the vane rotors 21 and 31 are integrally rotated relative to the retard side with respect to the housing 11, and the valve timing is retarded.

(Vi) After the supply hydraulic pressure becomes equal to or higher than the set pressure P _th , when the vane rotors 21 and 31 reach the most retarded position in FIG. Since the hydraulic pressure is released, the first piston 41 is once fitted into the fitting ring 120. Thereafter, the hydraulic pressure supply system 60 releases the hydraulic pressure from the retard passage 90 and supplies the hydraulic pressure to the advance passage 80 according to the low pressure advance operation (v). As a result, hydraulic pressure is supplied around the pressure receiving portions 411 and 412, so that the first piston 41 separates from the fitting ring 120 while pressing the second piston 51. However, since the supply hydraulic pressure is high at this time, the first piston 41 separates the second piston 51 from the first sliding hole 219 and communicates between the advance passages 87 and 88 as shown in FIG. Move to the blocking position. Thus, the lock of the first vane rotor 21 to the housing 11 and the lock of the second vane rotor 31 to the first vane rotor 21 are released, and the hydraulic pressure supply from the advance chamber 64 to the advance chambers 61 and 62 is restricted. Note that, during the period from when the first piston 41 is detached from the fitting ring 120 to when the second piston 51 is separated from the first sliding hole 219, the both vane rotors 21 are supplied by hydraulic pressure supplied to the advance chambers 63 and 64. , 31 may slightly rotate relative to the housing 11 toward the advance side.

(Vii) Immediately after the second piston 51 is disengaged, if the hydraulic pressure supply system 60 continues to supply the hydraulic pressure above the set pressure _Pth to the advance passage 80, the hydraulic pressure supply to the advance chambers 63 and 64 proceeds. As shown, the first vane rotor 21 rotates relative to the advance side with respect to the housing 11. At this time, the second piston 51 is sandwiched between the first vane rotor 21 and the front plate 14 as shown in FIG. At this time, since a part of the pressure receiving portion 413 is exposed to the advance chamber 64, the first piston 41 communicates between the advance passages 87 and 88 according to the same principle as in the case of (8) of the first embodiment. And the hydraulic pressure supply to the advance chambers 61 and 62 is restricted. For these reasons, the second vane rotor 31 does not follow even if the first vane rotor 21 rotates relative to the housing 11. Thus, the valve timing is advanced.

(Viii) Thereafter, an operation suitable for the operation of the internal combustion engine among the high pressure holding operation, the high pressure advance operation and the high pressure retard operation is performed. Here, the high pressure holding operation is in accordance with the low pressure holding operation (5) of the first embodiment. On the other hand, in the high pressure advance operation, only the first vane rotor 21 is moved to the housing 11 in accordance with the operation (vii) by _releasing the hydraulic pressure from the retard passage 90 and supplying the hydraulic pressure higher than the set pressure P _th to the advance passage 80. The valve timing is retarded by relative rotation to the retarded angle side. On the other hand, in the high pressure retarding operation, the hydraulic pressure is released from the advance passage 80 and the hydraulic pressure is supplied to the retard passage 90 at a set pressure _Pth or more, so that the advance chambers 63 and 64 and the pressure receiving portions 411, 412 and 413 are around. The hydraulic pressure is removed and the hydraulic pressure is supplied to the retarding chambers 71, 72, 73, 74. At this time, since the second piston 51 is sandwiched between the first vane rotor 21 and the front plate 14, only the first vane rotor 21 is retarded with respect to the housing 11 while the second vane rotor 31 is locked to the housing 11. The valve timing is retarded.

  Also according to the third embodiment described above, when the supply hydraulic pressure from the hydraulic supply system 60 is low, the number of vanes is substantially four to ensure a desired operation, and when the supply hydraulic pressure is high, the number of vanes is two. It is possible to increase the operation responsiveness by suppressing the generation of operating resistance while reducing the required amount of hydraulic oil.

Although a plurality of embodiments of the present invention have been described so far, the present invention is not construed as being limited to these embodiments, and can be applied to various embodiments without departing from the scope of the present invention. .
For example, in the first to third embodiments, the sliding holes 219 and 315 may be provided in the boss portions 210 and 310 of the vane rotors 21 and 31.

In the first to third embodiments, the number of vanes of the vane rotors 21 and 31 may be set as appropriate according to the required characteristics.
Furthermore, in 1st-3rd embodiment, without providing the fitting ring 120, you may make it not implement | achieve the lock | rock with respect to the housing 11 of the 1st vane rotor 21, and its release function with the 1st piston 41. Alternatively, in the first to third embodiments, the disposition position of the fitting ring 120 is changed, and a piston different from the first and second pistons 41 and 51 is fitted to the fitting ring 120, thereby You may implement | achieve the lock | rock of the one vane rotor 21, and its cancellation | release function.

In the first to third embodiments, the housing 11 may be rotated together with the camshaft 20, and the vane rotors 21 and 31 may be rotated together with the crankshaft.
In addition, in the first to third embodiments, the relationship between “advance angle” and “retard angle” may be reversed.
In addition, the present invention can be applied not only to a device that adjusts the valve timing of the intake valve, but also to a device that adjusts the valve timing of the exhaust valve, and a valve timing adjustment device that adjusts both the intake valve and the exhaust valve. is there.

It is sectional drawing which shows the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. 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 sectional drawing which shows the operation state different from FIG. It is the VV sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is the VII-VII sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is the IX-IX sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. 3, Comprising: It is the XIII-XIII sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the valve timing adjustment apparatus by 2nd embodiment of this invention, Comprising: It is the XV-XV sectional view taken on the line of FIG. It is the XVI-XVI sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is the XIX-XIX sectional view taken on the line of FIG. It is the XX-XX sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is the XXV-XXV sectional view taken on the line of FIG. It is sectional drawing which shows the valve timing adjustment apparatus by 3rd embodiment of this invention, Comprising: It is the XXVI-XXVI sectional view taken on the line of FIG. It is the XXVII-XXVII sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the operation state different from FIG. It is the XXXI-XXXI sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. FIG. 33 is a sectional view taken along line XXXIII-XXXIII in FIG. 32.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Valve timing adjustment apparatus, 11 Housing, 12 Sprocket, 13 Shoe housing, 14 Front plate, 20 Cam shaft (driven shaft), 21 1st vane rotor, 31 2nd vane rotor, 41 1st piston (supply control means, supply control member) ), 51 Second piston (locking means, locking member), 60 Hydraulic supply system (fluid pressure supply means), 61, 62, 63, 64 Advance chamber (accommodating chamber), 71, 72, 73, 74 Retarded chamber (Accommodating chamber), 80, 83, 84, 85, 86, 87, 88, 89 advance passage, 90, 91, 92, 93, 94, 95, 96, 99 retard passage, 97 pressure chamber, 98 connection part 111, 112 storage chamber (second storage chamber), 113, 114 storage chamber (first storage chamber), 120 fitting ring, 121 inner peripheral hole / fitting hole, 131, 132, 133 134 shoe, 140, 146 fitting hole (fitting hole), 210, 310 boss part, 213, 214 vane (first vane), 215 hole forming part, 216, 220 protruding part, 217 main body, 218 abutting protrusion, 219 First sliding hole, 311, 312 vane (second vane), 314, 318 vane (third vane), 315 Second sliding hole, 316 taper hole, 410 groove, 411, 412, 413, 511 , 512 pressure receiving portion, 416 taper portion, 510, 516 fitting portion, 514 elastic member, 641, 741 clearance, P _th set pressure

Claims (10)

Valve timing that is installed in a torque transmission system that transmits torque 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 adjusts an opening / closing timing of at least one of the intake valve and the exhaust valve An adjustment device,
A housing that rotates with one of the drive shaft and the driven shaft and forms a plurality of storage chambers in the rotational direction;
A first vane that rotates together with the other of the drive shaft and the driven shaft and is accommodated in a first accommodating chamber that is the accommodating chamber, is supplied from the fluid pressure supply means to the first accommodating chamber, and is A first vane rotor that rotates relative to the housing by a working fluid pressure acting on the vane;
A second vane housed in a second housing chamber that is a separate housing chamber from the first housing chamber, and is supplied from the fluid pressure supply means to the second housing chamber and acts on the second vane; A second vane rotor that rotates relative to the housing by a working fluid pressure;
The working fluid pressure supplied from the fluid pressure supply means by locking the second vane rotor with respect to the first vane rotor on condition that the working fluid pressure supplied from the fluid pressure supply means is less than a set pressure. Lock means for releasing the lock of the second vane rotor with respect to the first vane rotor as an essential condition that is equal to or higher than the set pressure;
When the second vane rotor is locked with respect to the first vane rotor, supply of working fluid pressure from the fluid pressure supply means to the second storage chamber is allowed, and the second vane rotor is locked with respect to the first vane rotor. Supply control means for restricting the supply of working fluid pressure from the fluid pressure supply means to the second storage chamber when released;
A valve timing adjusting device comprising:   The lock means is a lock that fits both the first vane rotor and the second vane rotor and locks the second vane rotor with respect to the first vane rotor by the working fluid pressure supplied from the fluid pressure supply means. 2. A lock member that moves to a position and a release position that releases the lock of the second vane rotor from the first vane rotor and the second vane rotor to the first vane rotor. The valve timing adjusting device according to 1. Said housing, a fitting hole is provided,
3. The valve according to claim 2, wherein the lock member locks the second vane rotor with respect to the housing by fitting into the fitting hole at the release position where the lock member is detached from the first vane rotor. Timing adjustment device. It said first vane rotor has a first sliding hole for sliding fit is the locking member,
The second vane rotor has a second sliding hole in which the lock member is fitted and slid,
The locking member is pressed toward the second sliding hole side by the working fluid pressure supplied from the fluid pressure supply means, and is disengaged from the first sliding hole, and is inserted into the fitting hole in the axial direction of the housing. The valve timing adjusting device according to claim 3, wherein the valve timing adjustment is performed. The first vane rotor has a first sliding hole in the first vane in which the lock member is fitted and slid,
The second vane rotor has a third vane accommodated together with the first vane in the first accommodating chamber, and the second vane has a second sliding hole into which the lock member is fitted and slid. The valve timing adjusting device according to any one of claims 2 to 4, wherein   The first vane protrudes from the hole forming portion in the axial direction of the first vane rotor and the hole forming portion that forms the first sliding hole, and the second vane rotor is locked to the first vane rotor. 6. The valve timing adjusting device according to claim 5, further comprising a protruding portion that comes into contact with the third vane from one side in the rotational direction of the first vane rotor. The supply control means includes a communication position for communicating between the fluid pressure supply means and the second storage chamber by a working fluid pressure supplied from the fluid pressure supply means, the fluid pressure supply means, and the second storage. A supply control member that moves to a blocking position that blocks communication between the chambers;
The said lock member moves by receiving the driving force by the working fluid pressure supplied from the said fluid pressure supply means via the said supply control member, The Claim 1 characterized by the above-mentioned. Valve timing adjustment device. The first vane rotor has a first sliding hole in which the lock member and the supply control member are fitted and slid,
The second vane rotor has a second sliding hole in which the lock member is fitted and slid,
The supply control member has a tapered portion at an end thereof that abuts on the locking member and transmits the driving force, and the locking member is moved into the second sliding hole by moving the tapered member into the first sliding hole. The valve timing adjusting device according to claim 7, wherein the valve timing adjusting device is separated from the sliding hole. The supply control means includes a communication position for communicating between the fluid pressure supply means and the second storage chamber by a working fluid pressure supplied from the fluid pressure supply means, the fluid pressure supply means, and the second storage. The valve timing adjusting device according to any one of claims 1 to 6 , further comprising a supply control member that moves to a blocking position that blocks communication between the chambers. The supply control member is fitted to both the housing and the first vane rotor by the working fluid pressure supplied from the fluid pressure supply means, and the first vane rotor is locked with respect to the housing. The detachment from one of the housing and the first vane rotor moves to the communication position and the blocking position where the lock of the first vane rotor with respect to the housing is released. The valve timing adjusting device according to 1.

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