JP2007138722A - Valve timing adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing adjusting device with high operational responsiveness by improving sealability between the valve member and the valve seat of a check valve. <P>SOLUTION: The valve member 93 of the check valve 90 is restricted so as not to move in the radial direction of a check valve passage 92 by abutting on the projection part 98 of a holder 94. Therefore, even if a centrifugal force is applied to the valve member 93 of the check valve 90 according to the rotation of a vane rotor 21, the valve member 93 is obstructed so as not to move in the radial direction of the vane rotor 21 by the projection part 98. Therefore, when the valve member 93 is seated on the valve seat 96, the valve member 93 is not moved by the centrifugal force, and any space is not formed between the valve member 93 and the valve seat 96. Consequently, the sealability of the check valve 90 can be improved, and hydraulic oil is prevented from leaking through the clearance between the valve member 93 and the valve seat 96. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

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

  2. Description of the Related Art Conventionally, there is known a valve timing adjusting device including a housing that receives a driving force of an engine crankshaft, and a vane rotor that is housed in the housing and transmits the driving force of the crankshaft to a camshaft. In this valve timing adjusting device, the camshaft phase relative to the crankshaft, that is, the valve timing, is driven by rotating the vane rotor relative to the housing toward the retard side or the advance side by the working fluid pressure in the retard chamber and the advance chamber. (For example, refer to Patent Document 1).

  In the valve timing adjustment device, when the intake valve or exhaust valve is driven to open or close, the torque fluctuation received by the camshaft from the intake valve or exhaust valve is transmitted to the vane rotor, and the vane rotor causes torque fluctuation to the retard side or advance side with respect to the housing. receive. When the vane rotor receives torque fluctuations on the retard side, the working fluid in the advance chamber receives a force flowing out from the advance chambers, and when the vane rotor receives torque fluctuations on the advance side, the working fluid in the retard chamber becomes retarded. Receives the power flowing out of the room. Then, for example, when the pressure of the working fluid supplied from the fluid supply source is low, the working fluid is supplied to the advance chamber, and the phase of the camshaft with respect to the crankshaft is changed from the retard side to the target phase on the advance side. When changing, the vane rotor is pushed back to the retard side due to torque fluctuation. As a result, the response time until the camshaft phase reaches the target phase becomes longer.

  Therefore, as disclosed in Patent Document 1, a check valve is provided in a supply passage for supplying the working fluid to the retard chamber and the advance chamber, and when the vane rotor receives torque fluctuation, the retard chamber or the advance It is conceivable to prevent the working fluid from flowing out of the chamber. Thus, it is known that the vane rotor is prevented from returning to the opposite side of the target phase with respect to the housing during the phase control, and the response of the phase control is improved.

JP 2003-106115 A

  In the case of the invention disclosed in Patent Document 1, the check valve is installed inside the vane rotor. That is, the check valve includes a check valve passage that penetrates the vane rotor in the axial direction and a valve member that opens and closes the check valve passage. In this case, the valve member reciprocates in the axial direction of the vane rotor through the check valve passage. And a valve member interrupts | blocks a non-return valve channel | path by sitting on the valve seat installed in the non-return valve channel | path.

  However, the vane rotor rotates together with the camshaft. Therefore, centrifugal force is applied to the valve member housed inside the vane rotor as the vane rotor rotates. For example, when a spherical valve member is used as the valve member of the embodiment disclosed in Patent Document 1, the valve member moves outward in the radial direction of the vane rotor when a centrifugal force is applied. To do. As a result, when the valve member blocks the check valve passage, the movement of the valve member causes leakage of the working fluid from between the valve member and the valve seat, resulting in a decrease in responsiveness due to a decrease in the pressure of the working fluid. Invite.

  Therefore, an object of the present invention is to provide a valve timing adjusting device that improves the sealing performance between the valve member and the valve seat of the check valve and has high operation responsiveness.

  In the first aspect of the present invention, the check valve has a guide portion. The guide part restricts the movement of the valve member due to the centrifugal force accompanying the rotation of the vane rotor. Thereby, even if a centrifugal force is applied to the valve member as the vane rotor rotates, the movement of the valve member inside the check valve passage, that is, the movement due to the centrifugal force, is restricted by the guide portion. Therefore, when the valve member is seated on the valve seat and the check valve passage is blocked, no gap is formed between the valve member and the valve seat. Accordingly, the sealing performance of the check valve is improved and the leakage of the working fluid from between the valve member and the valve seat is prevented, so that the pressure drop of the working fluid can be suppressed and the operation responsiveness can be improved.

  In the invention according to claim 2 or 3, the valve member is movable in the axial direction or the circumferential direction of the vane rotor. That is, the valve member moves in the axial direction or the rotational circumferential direction of the vane rotor. As a result, when the vane rotor rotates, centrifugal force is applied to the valve member accommodated in the check valve passage formed by the vane rotor on the radially outer side of the vane rotor. At this time, even if centrifugal force is applied to the valve member, the valve member is restricted from moving radially outward by the guide portion. Therefore, the sealing performance of the check valve is improved and the operation response can be improved.

In the invention according to claim 4, the guide portion is a convex portion protruding inward in the radial direction of the check valve passage installed in the vane rotor. Therefore, the radially inner end of the convex portion can slide with the valve member. Thereby, even if a centrifugal force is applied to the valve member as the vane rotor rotates, the valve member is restricted from moving in the radial direction by contacting the convex portion. Therefore, the sealing performance of the check valve is improved and the operation response can be improved.
In the invention according to claim 4, the convex part is at least one projecting part projecting radially inward of the check valve passage. Therefore, a passage through which the working fluid can pass is formed in a portion where the convex portion is not formed. Therefore, even when the convex portion is formed, the flow of the working fluid in the check valve passage can be ensured.

  In the fifth aspect of the present invention, the valve member comprises a seal portion that sits on the valve seat and blocks hydraulic oil, and an inner wall that forms a check valve passage and a slidable guide portion. The guide portion is a protruding portion that protrudes radially outward of the check valve passage from the valve member. Therefore, the radially outer end of the protrusion is slidable with the inner wall forming the check valve passage. Thereby, even if a centrifugal force is applied to the valve member as the vane rotor rotates, the valve member is restricted from moving in the radial direction because the protruding portion contacts the inner wall forming the check valve passage. Therefore, the sealing performance of the check valve is improved and the operation response can be improved.

  In the invention according to claim 5, the diameter of the guide part is set larger than the diameter of the seal part of the valve member. That is, since the diameter of the inner wall forming the check valve passage is larger than the diameter of the seal portion, a passage through which the working fluid can pass is formed between the seal portion and the inner wall forming the check valve passage. Therefore, even when the protrusion part which is a guide part is formed in the valve member, the flow of the working fluid in the check valve passage can be ensured.

  In the invention according to claim 6, the guide portion is formed by shifting the central axis of the valve seat and the central axis of the check valve passage. The central axis of the valve seat is displaced from the central axis of the check valve passage in the direction in which centrifugal force is applied, that is, radially outward of the vane rotor. Thereby, a valve member contacts the inner wall which forms a non-return valve channel | path. The inner wall in contact with the valve member is located outside the valve member in the radial direction of the vane rotor. Therefore, even when centrifugal force is applied to the valve member, the movement of the valve member is restricted by contacting the inner wall that forms the check valve passage. Therefore, the sealing performance of the check valve is improved and the operation response can be improved.

According to the sixth aspect of the present invention, the working fluid is provided between the valve member and the inner wall forming the check valve passage on the inner side in the radial direction of the vane rotor by shifting the central axis of the valve seat and the check valve passage. A passage through which can pass is formed. Therefore, the valve member does not block the check valve passage, and the flow of the working fluid in the check valve passage can be ensured.
Furthermore, in the invention described in claim 6, the guide portion is formed only by shifting the central axis of the valve seat and the check valve passage. Therefore, special processing is not required for the valve member and the guide portion. Therefore, the processing man-hour is not increased.

Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
A valve timing adjusting device according to a first embodiment of the present invention is shown in FIGS. The valve timing adjusting device 10 of this embodiment is a hydraulic control type that uses hydraulic oil as a working fluid, and adjusts the valve timing of the intake valve.

  As shown in FIG. 2, the housing 11 that is the drive side rotating body has a chain sprocket 12, a shoe housing 13, and a front plate 15. The shoe housing 13 includes shoes 131, 132, 133, and 134 as partition members shown in FIG. 3 and an annular peripheral wall 14. The chain sprocket 12, the shoe housing 13 and the front plate 15 are fixed coaxially by bolts 16. The chain sprocket 12 is coupled to a crankshaft as a drive shaft of an engine (not shown) by a chain (not shown) to transmit a driving force, and rotates in synchronization with the crankshaft.

The camshaft 20 as the driven shaft is transmitted with the driving force of the crankshaft via the valve timing adjusting device 10. The camshaft 20 opens and closes an intake valve (not shown). The camshaft 20 is inserted into the chain sprocket 12 so as to be rotatable with a predetermined phase difference with respect to the chain sprocket 12.
The vane rotor 21 as the driven side rotating body is in contact with the end surface in the rotation axis direction of the camshaft 20. The camshaft 20 and the vane rotor 21 are fixed on the same axis by bolts 22. Positioning of the vane rotor 21 and the camshaft 20 in the rotational direction is performed by inserting positioning pins 23 into the vane rotor 21 and the camshaft 20. The camshaft 20, the housing 11, and the vane rotor 21 rotate in the clockwise direction when viewed from the arrow X direction shown in FIG. Hereinafter, this rotational direction is defined as the advance direction of the camshaft 20 with respect to the crankshaft.

  As shown in FIG. 3, the shoes 131, 132, 133, 134 formed in a trapezoidal shape extend radially inward from the peripheral wall 14. The shoes 131, 132, 133, 134 are arranged at substantially equal intervals in the rotation direction of the peripheral wall 14. Four fan-shaped storage chambers 135 for storing vanes are formed in the gaps formed at four positions within a predetermined angular range in the rotation direction by the shoes 131, 132, 133, and 134, respectively.

  The vane rotor 21 includes a boss portion 24 that is coupled to the camshaft 20 at an axial end surface, and vanes 211, 212, 213, and 214 that are disposed on the outer peripheral side of the boss portion 24 at substantially equal intervals in the rotational direction. . The vane rotor 21 is accommodated in the housing 11 so as to be rotatable relative to the housing 11. The vanes 211, 212, 213, and 214 are rotatably accommodated in the respective accommodation chambers 135. The vanes 211, 212, 213, and 214 partition each storage chamber 135 into a retard hydraulic chamber and an advanced hydraulic chamber. The arrows representing the retard direction and the advance direction shown in FIG. 3 indicate the retard direction and the advance direction of the vane rotor 21 with respect to the housing 11.

  The seal member 25 is formed between the radially facing shoes 131, 132, 133, 134 and the boss portion 24, and between the vanes 211, 212, 213, 214 and the inner peripheral wall of the peripheral wall 14. It is arranged in the gap. The seal member 25 is fitted into the grooves provided in the tips of the shoes 131, 132, 133, and 134 and the outer peripheral walls of the vanes 211, 212, 213, and 214. For example, the outer peripheral wall and the peripheral wall of the boss portion 24 by a spring or the like. It is pressed toward 14 inner peripheral walls. With this configuration, the seal member 25 prevents hydraulic oil from leaking between each retarded hydraulic chamber and each advanced hydraulic chamber.

  As shown in FIG. 2, the stopper piston 31 formed in a cylindrical shape is accommodated in the vane 211 so as to be slidable in the rotation axis direction. The fitting ring 32 is press-fitted and held in a recess 17 formed in the chain sprocket 12. The stopper piston 31 can be fitted to the fitting ring 32. The fitting side of the stopper piston 31 and the fitting ring 32 is tapered. Therefore, the stopper piston 31 is smoothly fitted to the fitting ring 32. The spring 33 which is a pressing means presses the stopper piston 31 against the fitting ring 32 side. The stopper piston 31, the fitting ring 32, and the spring 33 constitute a restraining means that restrains the relative rotation of the vane rotor 21 with respect to the housing 11.

  The pressure of the hydraulic fluid supplied to the hydraulic chamber 34 formed on the chain sprocket 12 side of the stopper piston 31 and the hydraulic chamber 35 formed on the outer periphery of the stopper piston 31 causes the stopper piston 31 to come out of the fitting ring 32. To work. The hydraulic chamber 34 communicates with any of the advance hydraulic chambers described later, and the hydraulic chamber 35 communicates with any of the retard hydraulic chambers. The distal end portion of the stopper piston 31 can be fitted into the fitting ring 32 when the vane rotor 21 is located on the most retarded side with respect to the housing 11. In a state where the stopper piston 31 is fitted in the fitting ring 32, the relative rotation of the vane rotor 21 with respect to the housing 11 is restricted.

When the vane rotor 21 rotates with respect to the housing 11 from the most retarded side to the advanced side, the rotational positions of the stopper piston 31 and the fitting ring 32 shift. Therefore, the stopper piston 31 cannot be fitted to the fitting ring 32.
As shown in FIG. 3, a retard hydraulic chamber 41 is formed between the shoe 131 and the vane 211, and a retard hydraulic chamber 42 is formed between the shoe 132 and the vane 212, and the shoe 133 and the vane 213 A retard hydraulic chamber 43 is formed between them, and a retard hydraulic chamber 44 is formed between the shoe 134 and the vane 214. Further, an advance hydraulic chamber 51 is formed between the shoe 134 and the vane 211, an advance hydraulic chamber 52 is formed between the shoe 131 and the vane 212, and an advance hydraulic pressure is provided between the shoe 132 and the vane 213. A chamber 53 is formed, and an advance hydraulic chamber 54 is formed between the shoe 133 and the vane 214. Here, the retard hydraulic chambers 41, 42, 43, and 44 are the retard chambers in the claims, and the advance hydraulic chambers 51, 52, 53, and 54 are the advance chambers in the claims.

  As shown in FIG. 2, the oil pump 1 as a fluid supply source supplies hydraulic oil pumped from the oil tank 2 to the supply passage 3. The switching valve 60 is a known electromagnetic spool valve, and is installed between the supply passage 3 and the discharge passage 4 and the retard passage 70 and the advance passage 80 on the oil pump 1 side of the bearing 6 of the camshaft 20. Has been. The switching valve 60 is switching-controlled by a duty ratio-controlled driving current supplied from the electronic control unit (ECU) 5 to the electromagnetic driving unit 61. The spool 62 of the switching valve 60 is displaced based on the duty ratio of the drive current. Depending on the position of the spool 62, the switching valve 60 supplies hydraulic oil to the retard hydraulic chambers 41, 42, 43, 44 and the advance hydraulic chambers 51, 52, 53, 54, and the retard hydraulic chambers 41, 42. , 43 and 44 and hydraulic oil discharge from the advance hydraulic chambers 51, 52, 53 and 54 are switched. When the energization to the switching valve 60 is turned off, the spool 62 is in the position shown in FIGS. 2 and 4 by the pressing force of the spring 63.

  As shown in FIG. 2, annular passages 26 and 27 are formed on the outer peripheral wall of the camshaft 20 that is supported for rotation by the bearing 6. The retard passage 71 is formed from the switching valve 60 through the annular passage 26, and the advance passage 81 is formed from the switching valve 60 through the annular passage 27 in the camshaft 20 and in the boss portion 24 of the vane rotor 21.

  As shown in FIGS. 4 and 5, the retard passage 70 is branched into retard passages 72, 73, 74, 75 connected to the retard hydraulic chambers 41, 42, 43, 44. The retarding passages 72, 73, 74, and 75 supply hydraulic oil to the retarding hydraulic chambers 41, 42, 43, and 44 and are discharge passages that are on the fluid discharge side from the retarding hydraulic chambers 41, 42, 43, and 44 The hydraulic oil is discharged via 4. Accordingly, the retard passages 72, 73, 74, and 75 serve as a retard supply passage and a retard discharge passage.

  The advance passage 80 is branched into advance passages 82, 83, 84, 85 connected to the advance hydraulic chambers 51, 52, 53, 54. The advance passages 82, 83, 84, 85 supply hydraulic oil to the advance hydraulic chambers 51, 52, 53, 54 and from the advance hydraulic chambers 51, 52, 53, 54 via the discharge passage 4. Drain the hydraulic oil. Therefore, the advance passages 82, 83, 84, and 85 serve as an advance supply passage and an advance discharge passage.

  The check valve 90 is installed in the advance passage 83 connected to the advance hydraulic chamber 53, and is installed closer to the advance hydraulic chamber 53 than the bearing 6. That is, the advance hydraulic chamber 53 is a control advance chamber within the scope of the claims, and the advance passage 83 connected to the advance hydraulic chamber 53 is a control advance passage. The check valve 90 allows hydraulic oil to flow from the oil pump 1 through the advance passage 83 into the advance hydraulic chamber 53 and from the advance hydraulic chamber 53 through the advance passage 83 to the oil pump 1 side. Regulates backflow of hydraulic oil to

An advance passage 86 connecting the advance passage 83 and the advance passage 80 branches off from the advance hydraulic chamber 53 side of the check valve 90. A control valve 100 is installed in the advance passage 86. As shown in FIG. 2, the control valve 100 is a spool valve in which a spool 101 is accommodated in the vane rotor 21 so as to be reciprocally movable. The control valve 100 is installed closer to the advance hydraulic chamber 53 than the bearing 6. The control valve 100 is connected to a retard pilot oil passage 102 branched from the retard passage 70 and an advance pilot oil passage 103 branched from the advance passage 80. The spool 101 of the control valve 100 moves by the pressure balance of the hydraulic oil supplied from the retard pilot oil passage 102 and the advance pilot oil passage 103. Thereby, the control valve 100 opens and closes the advance passage 86 connecting the advance hydraulic chamber 53 and the discharge passage 4.
With the above-described passage configuration, hydraulic oil can be supplied from the oil pump 1 to the retarded hydraulic chambers 41, 42, 43, 44, the advanced hydraulic chambers 51, 52, 53, 54, the hydraulic chamber 34, and the hydraulic chamber 35. The hydraulic oil can be discharged from each hydraulic chamber to the discharge passage 4.

Next, the check valve 90 will be described in detail.
The check valve 90 is installed in the vane 213 of the vane rotor 21 as shown in FIG. As shown in FIGS. 1 and 2, the vane 213 has a hole portion 91 penetrating from the end on the chain sprocket 12 side to the oil passage 87 on the front plate 15 side in the axial direction of the vane rotor 21. The hole 91 forms a check valve passage 92 therein, and the check valve passage 92 communicates with the advance passage 83 and the oil passage 87. The check valve 90 includes a valve member 93, a holder 94, and a spring 95 as pressing means. The holder 94 is accommodated in the hole 91 of the vane 213. The holder 94 is fixed to the hole 91 by press fitting, for example. The holder 94 is formed in a cylindrical shape, and a check valve passage 92 is formed on the inner peripheral side. The holder 94 forms a valve seat 96 on the oil passage 87 side opposite to the advance hydraulic chamber 53. The oil passage 87 is connected to the advance passage 80 on the side opposite to the advance hydraulic chamber 53 with respect to the check valve passage 92.

  The valve member 93 is formed in a spherical shape and is accommodated on the inner peripheral side of the holder 94 so as to be movable in the axial direction of the vane rotor 21. The valve member 93 is pressed against the valve seat 96 side by a spring 95. When the valve member 93 is seated on the valve seat 96, the check valve passage 92 is blocked. Therefore, the check valve 90 blocks the oil passage 87 connected to the advance passage 80 and the advance passage 83 connected to the advance hydraulic chamber 53. One end of the spring 95 is in contact with the valve member 93, and the other end is fixed to the cap 97. The cap 97 is installed at the end of the hole 91 on the chain sprocket 12 side. The cap 97 seals the end of the hole 91 opposite to the oil passage 87.

  When the force received from the hydraulic oil in the oil passage 87 acting on the valve member 93 becomes larger than the pressing force of the spring 95, the valve member 93 moves toward the cap 97 against the pressing force of the spring 95. As a result, the valve member 93 is separated from the valve seat 96 and the check valve passage 92 is opened. As a result, the oil passage 87 and the advance passage 83 communicate with each other, and the hydraulic oil in the advance passage 80 is supplied to the advance hydraulic chamber 53.

  The holder 94 has a convex portion 98 as a guide portion that protrudes radially inward of the check valve passage 92 as shown in FIG. The convex portion 98 protrudes inward in the radial direction from the holder 94, and the inner peripheral end is in contact with the valve member 93. A plurality of convex portions 98 are provided in the circumferential direction of the holder 94, that is, in the circumferential direction of the check valve passage 92. Thereby, between the convex parts 98 adjacent in the circumferential direction, the channel | path through which hydraulic oil can pass is formed. When the end portion on the inner peripheral side of the convex portion 98 is in contact with the valve member 93, the movement of the valve member 93 in the radial direction of the holder 94 shown in FIG. 1A, that is, the direction perpendicular to the axis of the vane rotor 21 is restricted. The Therefore, even if a centrifugal force is applied to the valve member 93 due to the rotation of the vane rotor 21, the valve member 93 is in contact with the convex portion 98, thereby preventing the check valve passage 92 from moving in the radial direction.

Next, the operation of the valve timing adjusting device 10 will be described.
When the engine is stopped, the stopper piston 31 is fitted in the fitting ring 32. In the state immediately after starting the engine, the retarded hydraulic chambers 41, 42, 43, 44, the advanced hydraulic chambers 51, 52, 53, 54, the hydraulic chamber 34, and the hydraulic chamber 35 are operated with sufficient pressure from the oil pump 1. Oil is not supplied. Therefore, the stopper piston 31 remains fitted to the fitting ring 32, and the camshaft 20 is held at the most retarded position with respect to the crankshaft. Thereby, the generation of noise due to the collision between the housing 11 and the vane rotor 21 due to the torque fluctuation received by the camshaft 20 until the hydraulic oil is supplied to each hydraulic chamber is prevented.

  When the engine is started and hydraulic oil is sufficiently supplied from the oil pump 1, the stopper piston 31 comes out of the fitting ring 32 by the hydraulic pressure of the hydraulic oil supplied to the hydraulic chamber 34 or the hydraulic chamber 35. Therefore, the vane rotor 21 can rotate with respect to the housing 11. Then, the phase difference of the camshaft 20 with respect to the crankshaft is adjusted by controlling the hydraulic oil supplied to the retarded hydraulic chambers 41, 42, 43, 44 and the advanced hydraulic chambers 51, 52, 53, 54.

  When the energization to the switching valve 60 is off, the spool 62 is in the position shown in FIG. 4 by the pressing force of the spring 63. In this state, hydraulic fluid is supplied from the supply passage 3 to the retard passage 70, and hydraulic fluid is supplied from the retard passage 70 to the retard hydraulic chambers 41, 42, 43, 44. In this state, the hydraulic oil in the advance hydraulic chambers 51, 52, 53, 54 passes from the advance passages 82, 83, 84, 84 to the discharge passage 4 via the advance passage 80 and the switching valve 60. Discharged. The hydraulic oil in the advance hydraulic chamber 53 flows into the check valve 90 connected to the advance passage 83. At this time, in the check valve 90, the hydraulic oil pressure in the advance passage 83 on the advance hydraulic chamber 53 side becomes higher than that on the oil passage 87 side. Therefore, in the check valve 90, the valve member 93 is seated on the valve seat 96, and the check valve passage 92 that connects the advance hydraulic chamber 53 and the oil passage 87 is blocked. On the other hand, at this time, hydraulic oil is supplied to the control valve 100 from a retard pilot oil passage 102 connected to the retard passage 74. Therefore, the control valve 100 opens the advance passage 86 by the force received from the supplied hydraulic oil. As a result, the hydraulic oil discharged from the advance hydraulic chamber 53 is discharged to the discharge passage 4 via the advance passage 83, the advance passage 86, the control valve 100, the advance passage 80, and the switching valve 60. As described above, the hydraulic oil is supplied to the retarded hydraulic chambers 41, 42, 43, and 44, and the hydraulic oil is discharged from the advanced hydraulic chambers 51, 52, 53, and 54, so that the vane rotor 21 has four chambers. Force is received from the hydraulic oil in the angular hydraulic chambers 41, 42, 43, and 44. As a result, the vane rotor 21 rotates to the retard side with respect to the housing 11.

  When the energization of the switching valve 60 is turned on, the spool 62 moves to the position shown in FIG. 5 by the driving force of the electromagnetic driving unit 61 applied against the pressing force of the spring 63. In this state, hydraulic fluid is supplied from the supply passage 3 to the advance passage 80 and is supplied to the advance hydraulic chambers 51, 52, 53, 54 via the advance passage 80. In the case of the advance hydraulic chamber 53, hydraulic oil is supplied from the oil passage 87 via the check valve 90. On the other hand, the hydraulic oil in the retard hydraulic chambers 41, 42, 43, 44 is discharged from the retard passages 72, 73, 74, 75 to the discharge passage 4 via the retard passage 70, the switching valve 60, and the discharge passage 4. Is done. In this way, the hydraulic oil is supplied to the advance hydraulic chambers 51, 52, 53, 54, and the hydraulic oil is discharged from the retard hydraulic chambers 41, 42, 43, 44, so that the vane rotor 21 has four chambers. Force is received from the hydraulic oil in the angular hydraulic chambers 51, 52, 53, 54. As a result, the vane rotor 21 rotates toward the advance side with respect to the housing 11. At this time, hydraulic fluid is supplied to the control valve 100 from an advance pilot oil passage 103 connected to the advance passage 80. Therefore, the control valve 100 blocks the advance passage 86 by the force received from the supplied hydraulic oil.

  The hydraulic oil is supplied to the advance hydraulic chambers 51, 52, 53, 54, and the hydraulic oil is discharged from the retard hydraulic chambers 41, 42, 43, 44, so that the vane rotor 21 is phase-controlled to the target phase on the advance side. At this time, the vane rotor 21 receives torque fluctuations on the retard side and the advance side with respect to the housing 11. At this time, the torque fluctuation received by the vane rotor 21 greatly acts on the retard side when averaged. When the vane rotor 21 receives torque fluctuations on the retard side, the hydraulic oil in the advance hydraulic chambers 51, 52, 53, 54 receives the force that flows out to the advance passages 82, 83, 84, 85. However, the advance passage 83 is blocked by the check valve 90, and the advance passage 86 is blocked by the control valve 100. Therefore, the hydraulic oil in the advance hydraulic chamber 53 is not discharged to the advance passage 83 side. Therefore, when the hydraulic pressure of the hydraulic oil supplied from the oil pump 1 is low, the vane rotor 21 is not returned to the retard side with respect to the housing 11 even if the vane rotor 21 receives torque fluctuations on the retard side. As a result, the hydraulic oil is not discharged also from the advance hydraulic chambers 51, 52, and 54. Thereby, even if the vane rotor 21 receives torque fluctuation from the camshaft 20 to the retard side, the vane rotor 21 can be prevented from returning to the retard side opposite to the target phase with respect to the housing 11. As a result, the vane rotor 21 quickly reaches the target phase on the advance side.

  When the vane rotor 21 reaches the target phase, the ECU 5 controls the duty ratio of the drive current supplied to the switching valve 60 and holds the spool 62 at an intermediate position between FIG. 4 and FIG. As a result, the switching valve 60 cuts off the connection between the retard passage 70 and the advance passage 80, the oil pump 1 and the discharge passage 4, and the retard hydraulic chambers 41, 42, 43, 44 and the advance hydraulic chamber 51. , 52, 53, 54 is prevented from being discharged into the discharge passage 4. Accordingly, the vane rotor 21 is held at the target phase.

In the first embodiment, the valve member 93 of the check valve 90 is restricted from moving in the radial direction of the check valve passage 92 by the convex portion 98 of the holder 94. Therefore, even if a centrifugal force is applied to the valve member 93 of the check valve 90 by the rotation of the vane rotor 21, the valve member 93 is prevented from moving in the radial direction of the vane rotor 21. Thereby, when the valve member 93 is seated on the valve seat 96, the valve member 93 is not moved by the centrifugal force, and no gap is formed between the valve member 93 and the valve seat 96. Therefore, the sealing performance of the check valve 90 is improved, and hydraulic fluid leakage from between the valve member 93 and the valve seat 96 can be prevented. Further, by preventing the hydraulic oil from leaking between the valve member 93 and the valve seat 96, the pressure drop of the hydraulic oil can be suppressed, and the operation responsiveness of the valve timing adjusting device 10 can be enhanced.
In the first embodiment, a plurality of convex portions 98 are provided in the circumferential direction of the holder 94. Therefore, a passage through which hydraulic oil can pass is formed between the adjacent convex portions 98. Therefore, even if the convex portion 98 is formed, the flow of hydraulic oil in the check valve passage 92 is not hindered.

(Second Embodiment)
The principal part of the valve timing adjusting apparatus according to the second embodiment of the present invention is shown in FIG. In addition, the same code | symbol is attached | subjected to the component substantially the same as 1st Embodiment, and description is abbreviate | omitted.
In the second embodiment, as shown in FIG. 6, the valve member 93 serves as a guide portion at an end portion on the valve seat 96 side as a seal portion and an end portion on the opposite side to the valve seat 96, that is, an end portion on the spring 95 side. The protrusion 99 is provided. The protrusion 99 protrudes radially outward from the valve member 93, and the outer peripheral end is in contact with the inner wall of the holder 94. As a result, the end on the outer peripheral side of the projecting portion 99 is in contact with the inner wall of the holder 94, so that the valve member 93 is restricted from moving in the radial direction of the holder 94, that is, in the direction perpendicular to the axis of the vane rotor 21. Therefore, even if a centrifugal force is applied to the valve member 93 due to the rotation of the vane rotor 21, the valve member 93 moves in the radial direction of the check valve passage 92 because the protruding portion 99 of the valve member 93 contacts the inner wall of the holder 94. Be regulated.

  In the second embodiment, the diameter of the projecting portion 99 is larger than the diameter of the end portion on the valve seat 96 side as the seal portion of the valve member 95. That is, the diameter of the inner wall of the holder 94 is larger than the diameter of the seal portion. Therefore, since a passage through which the working fluid can pass is formed between the seal portion and the inner wall of the holder 94, the flow of the working oil in the check valve passage 92 is not hindered.

(Third embodiment)
The principal part of the valve timing adjusting apparatus according to the third embodiment of the present invention is shown in FIG. In addition, the same code | symbol is attached | subjected to the component substantially the same as 1st Embodiment, and description is abbreviate | omitted.
In the third embodiment, as shown in FIG. 7, the center axis C1 of the valve seat 96 formed on the holder 94 and the center axis C2 of the cylindrical holder 94 forming the guide portion are shifted. At this time, the central axis C <b> 1 of the valve seat 96 is shifted to the radially outer side of the vane rotor 21, that is, the side where the centrifugal force applied to the valve member 93 due to the rotation of the vane rotor 21 acts. That is, the center axis C2 of the holder 94 is shifted from the center axis C1 of the valve seat 96 in the direction opposite to the direction in which the centrifugal force is applied. Thus, when centrifugal force is applied, the valve member 93 comes into contact with the inner wall of the holder 94 on the outer side in the radial direction of the vane rotor 21. As a result, even if a centrifugal force is applied to the valve member 93, the movement of the valve member 93 is restricted by contacting the inner wall of the holder 94.

In the third embodiment, it is possible to prevent leakage of hydraulic oil from between the valve member 93 and the valve seat 96, and between the valve member 93 and the inner wall of the holder 94 on the inner side in the radial direction of the vane rotor 21. A gap is formed. The gap forms a passage through which the hydraulic oil can pass, and does not hinder the flow of the hydraulic oil in the check valve passage 92.
In the third embodiment, the sealing performance of the check valve 90 is improved by shifting the central axis of the inner wall of the holder 94 and the valve seat 96. Therefore, no special processing is required for the valve member 93 and the holder 94, and the number of processing steps is not increased.

(Other embodiments)
In the embodiments described above, the configuration in which the check valve passage 92 is opened and closed by the valve member 93 of the check valve 90 reciprocating in the axial direction of the vane rotor 21 has been described. However, the check valve 90 forms the check valve passage 92 in the circumferential direction of the vane rotor 21 or the direction corresponding to the string of the vane rotor 21, and the valve member 93 reciprocates in the rotation circumferential direction of the vane rotor 21 or the direction corresponding to the string. The check valve passage 92 may be opened and closed by moving. As described above, when the check valve passage 92 is formed in the rotation circumferential direction of the vane rotor 21 or the direction corresponding to the string, the rotation of the vane rotor 21 applies a force to the valve member 93 radially outward of the vane rotor 21. Therefore, by adopting the configuration described in the above embodiments, the radial movement of the valve member 93 is restricted even if a centrifugal force is applied to the valve member 93. Therefore, even when the check valve passage 92 is formed in the rotation circumferential direction of the vane rotor 21 or the direction corresponding to the string, the sealing performance of the check valve 90 can be improved.

  As described above, the present invention is not limited to the above-described embodiment, and can be applied to various embodiments without departing from the gist thereof.

It is the figure which expanded the vicinity of the non-return valve of the valve timing adjustment apparatus by 1st Embodiment of this invention, Comprising: (A) is the schematic seen from the chain sprocket side, (B) is B of (A) Sectional drawing in the -B line. 1 is a cross-sectional view illustrating an outline of a valve timing adjusting device according to a first embodiment of the present invention. Sectional drawing cut | disconnected by the III-III line of FIG. FIG. 3 is a schematic diagram showing the configuration of the valve timing adjusting device and the hydraulic circuit thereof according to the first embodiment of the present invention, and showing a state where the phase of the vane rotor is on the retard side. FIG. 3 is a schematic diagram showing the configuration of the valve timing adjusting device and the hydraulic circuit thereof according to the first embodiment of the present invention, and showing a state in which the phase of the vane rotor is on the advance side. It is the figure which expanded the vicinity of the non-return valve of the valve timing adjustment apparatus by 2nd Embodiment of this invention, Comprising: Sectional drawing corresponding to the position of FIG. 1 (B). It is the figure which expanded the vicinity of the non-return valve of the valve timing adjustment apparatus by 3rd Embodiment of this invention, Comprising: (A) is the schematic seen from the chain sprocket side, (B) is B of (A) Sectional drawing in the -B line.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Oil pump, 10 Valve timing adjustment apparatus, 11 Housing, 20 Cam shaft (driven shaft), 21 Vane rotor, 41, 42, 43, 44 Retarded hydraulic chamber (retarded chamber), 51, 52, 54 Advanced hydraulic chamber (Advance angle chamber), 53 advance angle hydraulic chamber (control advance angle chamber), 70, 71, 72, 73, 74 retard passage, 80, 81, 82, 84, 85 advance passage, 83 advance passage (control) Advance valve), 90 check valve, 92 check valve passage, 93 valve member, 94 holder (guide part), 96 valve seat, 98 convex part (guide part), 99 projecting part (guide part), 135 accommodation chamber , 211, 212, 213, 214

Claims (6)

Provided in a driving force transmission system for transmitting a driving force from a drive shaft of an internal combustion engine to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve, and opens and closes at least one of the intake valve and the exhaust valve In the valve timing adjusting device for adjusting the timing,
A housing that rotates together with one of the drive shaft or the driven shaft and has a plurality of storage chambers formed in the rotation direction within a predetermined angle range in the rotation direction;
Working fluid pressures of a plurality of retarding chambers and advance chambers that rotate together with the other of the drive shaft or the driven shaft and have vanes that are accommodated in the accommodating chambers and that are partitioned by the vanes. A vane rotor that is driven to rotate relative to the housing at a retarded angle side or an advanced angle side with respect to the housing;
At least one of the advance chambers is a control advance chamber, and the working fluid is supplied to each retard chamber or each advance chamber via the control advance chamber and the retard passage or advance passage. When the advance passage connecting the fluid supply source is a control advance passage, the advance passage is installed in the control advance passage, allowing the flow of working fluid from the fluid supply source to the control advance chamber, A check valve for restricting the flow of the working fluid from the control advance chamber to the fluid supply source side,
The check valve is separated from a check valve passage installed in the vane and a valve seat that is reciprocally movable in a direction different from the radial direction of the vane rotor and formed in the check valve passage, or A valve timing adjustment comprising: a valve member that opens and closes the check valve passage by being seated on a valve seat; and a guide portion that restricts movement of the valve member due to centrifugal force accompanying rotation of the vane rotor. apparatus.   The valve timing adjusting device according to claim 1, wherein the valve member is movable in an axial direction of the vane rotor.   The valve timing adjusting device according to claim 1, wherein the valve member is movable in a rotational circumferential direction of the vane rotor.   4. The valve timing adjusting device according to claim 2, wherein the guide portion has at least one protruding portion protruding radially inward of the check valve passage.   The valve timing adjusting device according to claim 2, wherein the valve member has a protruding portion that protrudes radially outward. 4. The valve timing adjusting device according to claim 2, wherein the guide portion is formed by shifting a central axis of the valve seat in a direction in which a centrifugal force is applied from a central axis of the check valve passage. .

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