JP2009222037A - Valve timing regulating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing regulating device, in which a vane rotor can be smoothly actuated relative to a housing by reducing the actuation resistance of the vane rotor caused by contact with an energization means. <P>SOLUTION: The vane rotor 5 that rotates with a camshaft 2 is housed in a housing chamber 40 of the housing 3, and a support member 6 is fastened by a bolt inserted to a bolt hole 4 to be rotatable with the vane rotor 5. One end of a spring 7 is locked to a fixing pin 350 of the housing, and the other end 72 is movably or lockably inserted to a slit 640 formed in the support member 6. A part close to one end of the spring 7 is guided to an arc surface 302 of a sector part 301 of the housing 3, and a part close to the other end is guided to the fixing pin 371 of the housing 3. The spring 7 in the form of a coil is thus prevented from becoming diametrically inwardly eccentric, and friction contact between the spring 7 and the support member 6 is avoided, thereby actuation resistance of the vane rotor to the housing 3 can be greatly reduced. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

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

  2. Description of the Related Art Conventionally, there has been known a valve timing adjusting device including a housing that receives a driving force from an engine crankshaft and a vane rotor that is housed in the housing and transmits the driving force of the crankshaft to a camshaft. This valve timing adjustment device changes the phase of the camshaft relative to the crankshaft by rotating the vane rotor relative to the retard side and the advance side relative to the housing by the hydraulic pressure of the retard chamber and the advance chamber. The timing is adjusted.

  As an example of such a vane type valve timing adjustment device, when the engine is stopped, an intermediate force between the phase change width of the vane rotor is obtained by the hydraulic force supplied into the advance chamber and the urging force by the return spring toward the advance side. There is a valve timing adjusting device that enables the engine to be started at the phase of (see, for example, Patent Document 1). When this valve timing adjustment device is applied to the intake valve, the vane rotor can be advanced to restore the intermediate phase at the start even when the oil pressure at the time of failure is low, so the intake air that is optimal for starting when the engine is cold Valve timing can be provided so that a suitable engine start can be achieved.

By the way, when the urging force is applied between the most retarded angle and the intermediate phase, one end of the return spring contacts the housing side, the other end contacts the vane rotor side, and a load acts on the contact portion. To do. Further, the return spring is in contact with the constituent members of the valve timing adjusting device at least at one point other than the one end and the other end so as to prevent eccentricity due to the spring load. However, since the friction force is generated by the spring load of the return spring at the contacted portion, for example, when the return spring is held on the housing side and the contact portion is on the vane rotor side, the operating resistance due to the friction of the vane rotor with respect to the housing Becomes larger. That is, there is a possibility that the smooth operation of the valve timing adjusting device is hindered due to an increase in hysteresis generated in the swing torque of the return spring.
JP 2002-227621 A

  SUMMARY OF THE INVENTION An object of the present invention is to provide a valve timing adjusting device that can reduce an operating resistance due to friction of a vane rotor generated by contact of an urging means and that allows the vane rotor to operate smoothly with respect to a housing.

  According to the first aspect of the present invention, the housing that rotates together with one of the drive shaft and the driven shaft accommodates the vane rotor that rotates relative to the pressure of the working fluid, and has the bearing portion and the protruding portion, and the fastening member , As well as biasing means. The bearing portion of the support member is in contact with the surface of the vane rotor on the side of the counter driven shaft, and rotatably supports the housing. The protruding portion is formed integrally with the bearing portion and protrudes from the housing toward the anti-vane rotor side. The fastening member couples the vane rotor and the support member on the rotation shaft of the driven shaft. Therefore, the support member rotates integrally with the vane rotor. A biasing means having a coil shape is provided around the protruding portion of the support member. One end of the urging means is locked to the housing, and the other end can urge the support member in the advance direction, thereby urging the vane rotor toward the advance side. The housing includes first guide means for supporting the vicinity of one end of the biasing means in the radially outward direction, and second guide means for supporting the vicinity of the other end of the biasing means in the radially outward direction.

  Conventionally, as described above, when the coil-shaped urging means is provided around the support member, when the center axis of the spring is eccentric due to the spring load always acting on the urging means, the coil is wound in a coil shape. There is a possibility that the vicinity of one end of the biasing means may come into contact with the support member protruding from the end surface of the housing. As a result, there is a concern of affecting the operation of the vane rotor.

  On the other hand, in the present invention in which the housing has the first and second guide means, the vicinity of one end of the urging means abuts on the first guide means, and the vicinity of the other end of the urging means abuts on the second guide means. The biasing means does not come into contact with the support member. For this reason, the first guide means and the second guide means function as friction reducing means, and friction between the biasing means and the support member does not occur, and the operating resistance of the vane rotor with respect to the housing can be greatly reduced. As a result, according to the valve timing adjusting device of the present invention, it is possible to reduce the operating resistance of the vane rotor caused by the contact friction between the urging means and the support member, and to smoothly operate the vane rotor with respect to the housing.

  According to the second aspect of the present invention, one end of the biasing means is locked to the first locking means provided on the housing. The other end of the urging means has a bent portion that is bent in the radially inward direction in the vicinity thereof, and an endmost portion that is formed on the distal end side of the bent portion. This extreme end can be locked to the second locking means provided on the support member. When the vane rotor is in the range from the most retarded phase to a predetermined intermediate phase with respect to the housing, the extreme end of the other end is locked to the second locking means of the support member, so that the vane rotor is advanced in the advance direction. Giving the energizing power. On the other hand, in the range from the intermediate phase to the most advanced angle phase, the bent portion is locked to the second guide means of the housing, so that the outermost end portion is released from the second locking means and attached in the advance angle direction. No power is given.

  Thereby, the range in which the urging force of the urging means acts is limited between the most retarded phase and the predetermined intermediate phase. For example, when the working fluid pressure in the advance direction decreases when the vane rotor is retarded due to the drive torque of the driven shaft during engine stall, the vane rotor is advanced to an intermediate position suitable for restart. The biasing force of the biasing means works. While the vane rotor is operated to the advance side by the working fluid pressure, it is not necessary to urge the advance direction in the advance direction by the urging means. Torque can be eliminated. At this time, since the urging means is locked to the housing at both one end and the other end and does not contact the support member, it does not interfere with the operation of the vane rotor. Therefore, the operating resistance of the vane rotor can be reduced, and the valve timing adjusting device can be operated smoothly.

  According to a third aspect of the present invention, the second guide means has a fixing portion and a locking portion. The fixing portion is fixed to the housing, and the locking portion can rotate with respect to the fixing portion and can lock the bent portion of the urging means. For example, the fixed portion is a columnar shaft portion provided in the housing, and the locking portion is a bearing that can rotate on the shaft portion.

  In this way, when the locking of the bent portion to the second guide portion is released and the other end of the urging means moves together with the second locking means of the support member, even if the coil outer peripheral portion near the other end Even if it comes into contact with the second guide means, the frictional force can be suppressed because it is rotated and guided by the locking portion. As a result, the operating resistance of the vane rotor caused by the contact of the urging means can be further reduced.

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

  A valve timing adjusting device 1 shown in FIG. 1 is used for a camshaft 2 as a driven shaft. As shown in FIG. 2, the camshaft 2 is rotationally driven to open and close the intake valve 10. The valve timing adjusting device 1 adjusts the valve timing of the intake valve 10 by changing the phases of the crankshaft 8 and the camshaft 2 as the drive shaft of the engine 80.

  As shown in FIG. 1, the valve timing adjusting device 1 includes a housing 3, a vane rotor 5, a support member 6, and a spring 7 as an urging means. The housing 3 includes a substantially annular plate-like chain sprocket 20 and a substantially cylindrical shoe housing 30 disposed on the front end face of the chain sprocket 20. The chain sprocket 20 has a gear 21 on the outer periphery. The chain sprocket 20 and the shoe housing 30 are coaxially fixed by a bolt 41 and constitute an outer wall of a storage chamber 40 that is a space in which the vane rotor 5 is rotatably accommodated.

  The vane rotor 5 is fixed coaxially with the camshaft 2 by passing a bolt (not shown) as a fastening member through the bolt hole 4. With this configuration, the vane rotor 5 rotates together with the camshaft 2 and can rotate relative to the housing 3. During operation, the housing 3, the vane rotor 5 and the camshaft 2 rotate in the clockwise direction when viewed from the direction of the arrow IV shown in FIG. Hereinafter, this rotation direction is referred to as an advance direction.

  As shown in FIG. 2, a chain 82 is wound around the gear 21 of the housing 3, the gear 81 fixed coaxially to the crankshaft 8, and the gear 91 fixed coaxially to the camshaft 9. . Therefore, the crankshaft 8 described above is connected to the housing 3 via the chain 82. As a result, the housing 3 receives driving force from the crankshaft 8 and rotates in synchronization with the crankshaft 8. On the other hand, the driving force of the crankshaft 8 is also transmitted to the camshaft 2 via the housing 3. The camshaft 2 drives the intake valve 20 and the camshaft 9 opens and closes the exhaust valve 90.

  As shown in FIG. 3, which is a cross-sectional view taken along line III-III in FIG. 1, the shoe housing 30 of the housing 3 includes three shoes 32, 33, 34 projecting radially inward from the peripheral wall. Have at intervals. In the gap between the shoes adjacent to each other in the rotation direction, three storage chambers 40 partitioned in a fan shape are formed.

  The vane rotor 5 is formed, for example, by sintering or forging with iron, and includes a boss portion 51 and vanes 52, 53, and 54 formed in a radially outward direction of the boss portion 51. The vanes 52, 53, and 54 are arranged at substantially equal intervals in the circumferential direction, and are formed integrally with the boss portion 51. As shown in FIG. 1, the boss portion 51 of the vane rotor 5 and the camshaft 2 are in contact with each other at the end surfaces in the rotation axis direction. Positioning of the vane rotor 5 and the camshaft 2 in the rotational direction is performed by fitting positioning pins into pin holes (not shown) provided in the boss portion 51 and pin holes (not shown) provided in the camshaft 2.

  As shown in FIG. 3, the vanes 52, 53, 54, each vane storage chamber 40, advance hydraulic chambers 42, 43, 44 as advance chambers and retard hydraulic chambers 45, 46 as retard chambers. , 47. Specifically, the advance hydraulic chamber 42 and the retard hydraulic chamber 45 are partitioned by the vane 52, the advance hydraulic chamber 43 and the retard hydraulic chamber 46 are partitioned by the vane 53, and similarly, the advance hydraulic chamber 43 and the retard hydraulic chamber 46 are advanced by the vane 54. The angular hydraulic chamber 44 and the retarded hydraulic chamber 47 are partitioned.

  In addition, a seal member 55 is disposed on the surface of the boss portion 51 of the vane rotor 5 that faces the shoes 32, 33, 34 and the surface of the vanes 52, 53, 54 that faces the tube portion of the shoe housing 30. Has been. The seal member 55 is fitted into a groove formed in the boss portion 51 and the vanes 52, 53, 54, and is urged against the shoes 32, 33, 34 and the tubular portion of the shoe housing 30 by a spring or the like. ing. With this configuration, the liquid tightness of each advance hydraulic chamber 42, 43, 44 and each retard hydraulic chamber 45, 46, 47 is increased.

  Furthermore, inside the camshaft 2 and the vane rotor 5, there are formed an advance oil passage 48 for supplying hydraulic oil to each advance oil pressure chamber 42, 43, 44, and a retard oil passage (not shown). . By switching between supply and discharge of hydraulic oil to the advance oil passage 48 and the retard oil passage, the vane rotor 5 rotates relative to the housing 3, and the phase difference of the camshaft 2 with respect to the crankshaft 8 is adjusted. The Between the adjacent hydraulic chambers, the above-described seal member 55 prevents hydraulic fluid from leaking.

  As shown in FIG. 1, the vane rotor 5 has a recess 50 that is recessed in a substantially annular shape in the axial direction on the end surface of the boss portion 51 on the side opposite to the camshaft 2. The support member 6 is press-fitted almost coaxially with the vane rotor 5 in the recess 50. The support member 6 has a substantially annular bottom 60 and is in contact with the recess 50. A bolt (not shown) inserted into the hole 601 of the bottom portion 60 is inserted into the bolt hole 4 of the vane rotor 5 and fastened to the end surface of the camshaft 2. As a result, the support member 6 is coaxially fixed to the vane rotor 5 and the camshaft 2. Positioning of the support member 6 and the vane rotor 5 is performed by fitting a positioning pin into a hole 63 provided in the bottom portion 60 and a hole (not shown) provided in the vane rotor 5.

  The support member 6 further includes a bearing portion 61 that rises in the axial direction from the bottom portion 60, and a protruding portion 62 that is formed integrally with the bearing portion 61 in the axial direction. The bearing portion 61 has a substantially cylindrical shape, and is inserted into the inner wall 31 that rotatably supports the support member 6 formed on the front plate 303 of the shoe housing 30. The diameter of the outer peripheral wall of the bearing portion 61 is set slightly smaller than the diameter of the inner wall 31. Thereby, the bearing portion 61 of the support member 6 rotatably supports the housing 3. On the extension of the shaft, a projecting portion 62 projects from the end surface (hereinafter referred to as the front end surface) of the housing 3 on the side opposite to the camshaft 2 to the outside and is formed in a substantially cylindrical shape having the same or different diameter as the bearing portion 61. Has been.

  As shown in FIG. 4, the spring 7 as an urging means is provided around the protrusion 62. In the present embodiment, the spring 7 is a coil spring and has one end 71, the other end 72, and a winding portion 78 wound between the one end 71 and the other end 72 in a substantially cylindrical shape. Here, the one end 71 is an end closer to the housing 3 in the axial direction, and the position of the other end 72 in the circumferential direction is substantially opposite to the one end 71.

  One end 71 of the spring 7 extends by being bent radially outward on a circumference 73 near one end, and is locked to a fixing pin 350 of the first locking means 35 provided on the front end surface of the housing 3. In the present embodiment, the first locking means 35 includes a fixing pin 350 and a large-diameter pin head 351 formed at the tip thereof, and one end 71 is hooked and locked by the first locking means 35.

  The other end 72 of the spring 7 has a bent portion 75 in which a circumference 74 in the vicinity of the other end is bent inward and an outermost end portion 76 formed on the distal end side from the bent portion 75. This end 76 can be locked to the second locking means 64 provided on the support member 6. The 2nd latching means 64 has the long groove 640 which notched the opening end of the protrusion part 62 at the predetermined angle in the circumferential direction. The opening angle of the long groove 640 cut out in the protrusion 62 of the support member 6 is set to be slightly larger than the angle in the maximum advance angle range from the intermediate phase to the most advanced angle phase shown in FIG. The most end portion 76 is inserted into the long groove 640 of the second locking means 64 so as to be movable in the circumferential direction, and can be locked by contacting the inner wall 641 on the most advanced angle side of the locking means 64.

  In the vicinity of one end 71 of the spring 7, the circumference 73 is substantially in contact with the front plate 303 on the front end surface of the housing 3. The front end surface of the housing 3 is provided with first guide means 36 that abuts on the inner side of the circumference 73 and supports the vicinity of the one end 71 of the spring 7 away from the protruding portion 62. In the present embodiment, the first guide means 36 has an annular shape in which the front plate 303 of the housing 3 surrounds the base of the protruding portion 62 and protrudes toward the side opposite to the camshaft 2 by the thickness of one turn of the spring 7. The protrusion 300 and a part of the outer periphery of the annular protrusion 300 extend in the radially outward direction, and have a fan portion 301 formed so as to form a part of a fan shape having a point O shown in FIG. 4 as a vertex. The arc surface 302 of the fan portion 301 has a diameter substantially the same as the inner diameter of the wound portion 78 of the spring 7 in an appropriate angular range around the point O at a substantially intermediate position from one end 71 to the other end 72 in the circumferential direction. It is formed with.

  A fixing pin 371 is provided on the front end surface of the housing 3 as second guide means capable of locking the bent portion 75 of the other end 72. In the present embodiment, the fixing pin 371 is a cylindrical pin installed on the substantially opposite side of the first locking means 35. The fixing pin 371 is disposed so as to be able to support the circumference 74 near the other end of the spring 7 in the radially outward direction. Further, the distance between the contact point between the fixing pin 371 and the circumference 74 near the other end and the center point O of the front plate 303 is substantially the same as the length of the radius of the inner circumference of the wound portion 78 of the spring 7. Is set.

  Next, the operation of the valve timing adjusting device 1 will be described with reference to FIGS. FIG. 4 shows a state of the valve timing adjusting device 1 before the engine is started, that is, when the engine 80 is stopped. Further, the operational effects of the present embodiment can be explained by the hysteresis of the spring swing torque in the characteristic diagram of FIG. 7 representing the operating torque generated in the spring 7 with the control of the rotational phase of the vane rotor 5. For comparison with the present invention, the spring swing torque of the conventional valve timing adjusting device is shown by a dotted line in FIG.

<When the engine is stopped>
In the state where the engine 80 is stopped, as shown in FIG. 4, the end 76 of the spring 7 is in contact with the inner wall 641 of the second locking means 64, but the urging force in the advance direction is applied to the inner wall 641. The bent portion 75 is also hooked and locked to the fixing pin 371 so as not to be hung. The spring 7 always receives a load that is eccentric in the radially inward direction at the position of the first guide means 36, and the first guide means 36 receives this load on the arc surface 302 that contacts the spring 7 and the other end. The vicinity of 72 is supported. Therefore, the spring 7 is held by the valve timing adjusting device 1 by the first guide means 36 and the fixing pin 371 so that the central axis of the winding portion 78 is positioned substantially coaxially with the central axis of the housing 3 and is not eccentric. .

<After starting the engine>
When the hydraulic oil is sufficiently supplied from the hydraulic pump 11 shown in FIG. 1 after the engine is started, the hydraulic pressure supplied to the advance hydraulic chambers 42, 43, 44 and the retard hydraulic chambers 45, 46, 47 shown in FIG. Thus, the vane rotor 5 rotates relative to the housing 3. The phase difference of the camshaft 2 with respect to the crankshaft 8 is adjusted by controlling the hydraulic pressure applied to each advance hydraulic chamber and each retard hydraulic chamber.

<Advance angle operation>
When the valve timing adjustment device 1 operates in the advance direction, the electronic control unit (ECU) 14 shown in FIG. 1 controls the drive current supplied to the switching valve 13. The switching valve 13 connects the hydraulic pump 11 and the advance oil passage 48 and connects the retard oil passage (not shown) and the oil pan 12. The hydraulic oil discharged from the hydraulic pump 11 is supplied to the advance hydraulic chambers 42, 43, and 44 shown in FIG. The hydraulic pressure in the advance hydraulic chambers 42, 43, and 44 acts on the vanes 52, 53, and 54, and generates torque that urges the vane rotor 5 in the advance direction. The hydraulic oil in the retarded hydraulic chambers 45, 46, 47 is discharged to the oil pan 12 via a retarded oil passage (not shown).

  As shown in FIG. 5, when operating in the advance direction, the support member 6 on the front end surface rotates relative to the housing 3 in the advance direction integrally with the vane rotor 5, and the spring 7 is bent on the fixing pin 371. The part 75 contacts the circumferential direction, and the rotational movement in the advance direction is restricted. At this time, the groove wall surface of the second locking means 64 of the support member 6 advances away from the outermost end 76 and the locking of the other end 72 is released. Thereby, the spring 7 does not apply an urging force in the advance direction to the vane rotor 5. Therefore, the advance position of the vane rotor 5 is controlled to the target position only by the hydraulic pressure supplied to the advance chamber or the retard chamber.

  At this time, according to the conventional valve timing adjusting device, the operating torque of the spring 7 becomes negative as shown by the broken line L10 portion of the graph of FIG. 7, and the vane rotor 5 returns from the most advanced angle phase to the starting phase. Sometimes, the operating torque increases to the magnitude indicated by the broken line L20, and a large hysteresis occurs. Conventionally, when the outer periphery of the protruding portion 62 of the support member 6 directly contacts the spring 7, the periphery 73 near one end presses the protruding portion 62, so that the operation due to friction when the supporting member 6 slides is performed. This is because resistance occurs.

  Therefore, according to the valve timing adjusting device 1 of the first embodiment, the first guide portion 36 is provided to separate the spring 7 and the support member 6, and the circumference 73 near one end of the spring 7 is an arc. The shape and axial position are maintained along the surface 302. For this reason, the friction by the contact with the support member 6 mentioned above does not occur, and the operating resistance of the vane rotor 5 is greatly reduced. As a result, as shown in FIG. 7, the swing torque at the advance position of the spring 7 is represented by L11 when rotating in the advance direction, and L21 when returning to the retard direction, and is close to zero in either case. The effect of reducing torque hysteresis can be obtained.

<At retarded angle operation>
Before the engine is stopped, for example, when the engine speed is an idle speed, the ECU 14 is retarded and the camshaft 2, the vane rotor 5 and the support member 6 are stopped in the vicinity of the maximum retarded phase as shown in FIG. It becomes. When the control in the retarding direction is started, the switching valve 13 connects the hydraulic pump 11 and a retarding oil passage (not shown), and connects the oil pan 12 and the leading oil passage 48, which is shown in FIG. Thus, the hydraulic oil is supplied to the retarded hydraulic chambers 45, 46, 47, and the vanes 52, 53, 54 that have received the hydraulic pressure rotate to the maximum retarded phase against the biasing force of the spring 7 in the advanced direction. To do. When the engine is stopped normally, that is, when the ignition switch is turned off, the advance control is performed by the ECU 14 to return to the initial intermediate phase.

  As shown in FIG. 6, when the valve timing adjusting device 1 operates in the retarding direction, the outermost end 76 of the spring 7 is pressed by the inner wall 641 of the second locking means 64 and moves in the retarding direction. As a result, the bent portion 75 moves away from the fixed pin 371 and moves to the retarded position, and the circumference 74 near the other end is supported radially outward by the fixed pin 371 and rotates while being regulated to prevent eccentricity. The swinging torque of the spring 7 at this time is maximum in any case, as shown by L30 in FIG. 7 according to the prior art and as shown by a one-dot chain line L31 according to the present embodiment.

  Here, after the operation in the retarding direction described above, when an engine stall occurs in the most retarded phase, the hydraulic oil is not immediately supplied to the advance hydraulic chambers 42, 43, and 44, and the hydraulic pressure decreases. Occurs. At this time, when the force acting on the hydraulic oil in the retarded hydraulic chambers 45, 46, 47 is lower than the biasing force of the spring 7 in the advance direction, the inner wall 641 of the second locking means 64 in FIG. The outermost end portion 76 applies an urging force in the advance direction to rotate the support member 6. Thereby, the vane rotor 5 is advanced by receiving the urging force of the spring 7 in the advance direction. This urging force in the advance direction acts until the other end 72 reaches the position of the fixed pin 371. When the bent portion 75 comes into contact with the fixed pin 371 and is locked, the initial state shown in FIG. Return to. That is, the vane rotor 5 stops at an intermediate phase optimum for starting with respect to the housing 3 in the same manner as when the engine is stopped.

  While the vane rotor 5 is advanced by the urging force of the spring 7 from the most retarded phase, conventionally, the swing torque of the spring 7 is smaller than L30 when it is retarded as indicated by L40 in FIG. . As described above, in the conventional valve timing adjusting device, since friction occurs between the support member 6 and the spring 7 as described above, friction loss occurs in the biasing force of the spring 7 acting in the advance direction. Here, according to the present embodiment, since the generation of the frictional force is suppressed by the first guide means 36 as described above, the friction loss can be reduced as compared with the conventional case as indicated by L41. Therefore, the hysteresis of the acting torque of the spring 7 can be reduced as compared with the conventional one, and the smooth operation of the valve timing adjusting device can be realized.

(Second Embodiment)
Subsequently, a valve timing adjusting device according to a second embodiment is shown in FIGS. As shown in FIG. 8, in the second embodiment, instead of the fixing pin 371 of the first embodiment, a fixing pin 381 and a bearing roller 382 rotatably attached around the fixing pin 381 are provided as the second guide means. Have as. The fixing pin 381 is attached to the annular protrusion 300 of the housing 3, and the bearing roller 382 supports the vicinity of the other end of the spring 7 in the radially outward direction. For other configurations, members having substantially the same configurations as those of the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
FIG. 9 shows the phase of the engine stop state, FIG. 10 shows the advance angle phase, and FIG. 11 shows the retard angle phase.

  The effect of the second embodiment is explained by the fact that the swinging torque of the spring 7 varies with the magnitudes indicated by the solid line portions L11, L121, L32, and L42 in FIG. That is, between the engine stop state shown in FIG. 9 and the state of the most advanced angle phase shown in FIG. 10, the operational effects of the first embodiment shown in L11 and L12 are the same. As shown in FIG. 11, when operating in the retarding direction, the locking of the bent portion 75 to the bearing roller 382 is released, and the circumference 74 near the other end is supported by the bearing roller 382 and moves in the retarding direction. To do. Further, even when the hydraulic pressure decreases at the retarded phase and the biasing force in the advance direction of the spring 7 acts, the circumference 74 near the other end moves while being supported by the bearing roller 382, and the inner wall 641 is moved at the outermost end 76. The support member 6 is rotated in the advance direction in contact with.

  In the case of the present embodiment, the circumference 74 in the vicinity of the other end is smoothly rolled by the rotation of the bearing roller 382 during operation in the advance angle direction and the retard angle direction in such a retard angle phase. The frictional force can be reduced as compared with the case of sliding directly on a fixed pin such as the fixed pin 371. Therefore, during the operation in the retarding direction and during the application of the urging force in the advance direction, as shown by L32 and L42 in FIG. To do. For this reason, in addition to the fact that the operating resistance due to the friction between the spring 7 and the support member 6 hardly occurs, the operating resistance due to the friction with the second guide portion of the housing 3 is also greatly reduced. And the operation of the vane rotor 5 becomes smooth.

(Third embodiment)
In the third embodiment, instead of the fixing pin 371 of the first embodiment, a fixing pin 372 is attached to the front plate 303 of the housing 3 at a position displaced by a clearance δ in the radially inward direction.
Further, a fixing pin 391 is provided on the fan portion 301 of the first embodiment, and a bearing roller 392 that can rotate with respect to the fixing pin 391 and guides the spring 7 in the radially outward direction is provided.
At this time, since the fixing pin 372 is positioned radially inward by the clearance δ, the circumference 74 in the vicinity of the other end of the spring 7 is unlikely to contact the fixing pin 372, and the operating resistance due to friction is further reduced.

(Other embodiments)
In the above-described embodiments, the example in which the vane rotor of the valve timing adjusting device rotates with the driven shaft has been described. However, the valve timing adjusting device according to the present invention may be such that the vane rotor rotates in synchronization with the drive shaft, and the housing rotates relative to the driven shaft. In the above-described embodiments, an example in which the valve timing adjusting device is applied to an intake valve of an engine has been described. However, the valve timing adjusting device according to the present invention may be applied to an exhaust valve.

Sectional drawing which shows the valve timing adjustment apparatus by 1st Embodiment of this invention. The schematic diagram which shows the valve timing adjustment apparatus of this invention. It is a figure equivalent to the III-III line section of Drawing 1, and is a sectional view showing the most retarded state of a valve timing adjustment device. It is the top view which looked at FIG. 1 from IV direction, Comprising: The figure which shows the state of the intermediate phase before an engine start. It is the top view which looked at FIG. 1 from IV direction, Comprising: The figure which shows the state of the most advance angle phase. It is the top view which looked at FIG. 1 from IV direction, Comprising: The figure which shows the state of the most retarded angle phase. The characteristic view which compares the torque which generate | occur | produces in the conventional valve timing adjustment apparatus with the torque which generate | occur | produces in the valve timing adjustment apparatus of this invention. Sectional drawing corresponding to FIG. 1 which shows the valve timing adjustment apparatus by 2nd Embodiment of this invention. It is the top view which looked at FIG. 8 from IX direction, Comprising: The figure which shows the state of the intermediate | middle phase before engine starting. It is the top view which looked at FIG. 8 from IX direction, Comprising: The figure which shows the state of the most advanced angle phase. It is the top view which looked at FIG. 8 from IX direction, Comprising: The figure which shows the state of the most retarded angle phase. The top view which shows the valve timing adjustment apparatus by other embodiment of this invention.

Explanation of symbols

  1: valve timing adjusting device, 2: camshaft, 3: housing, 4: bolt hole, 5: vane rotor, 6: support member, 7: spring, 20: chain sprocket, 21: gear, 30: shoe housing, 300: Annular protrusion, 301: fan part, 302: arc surface, 303: front plate, 32, 33, 34: shoe, 35: first locking means, 350: fixing pin, 351: pin head, 36: first guiding means, 371: fixed pin (second guide means), 381: fixed pin, 382: bearing roller (second guide means), 40: storage chamber, 42, 43, 44: advance hydraulic chamber, 45, 46, 47: slow Angular hydraulic chamber, 48: advance oil passage, 50: recess, 51: boss, 52, 53, 54: vane, 55: seal member, 60: bottom, 601: hole, 61: bearing, 62: protrusion 64: second locking means, 640: long groove, 641: inner wall, 71: one end, 72: the other end, 75: bent portion, 76: endmost, 78:-turn portion

Claims (3)

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 A valve timing adjusting device for adjusting timing,
A housing having a storage chamber that rotates together with one of the drive shaft and the driven shaft and is formed in a predetermined angle range in the rotation direction;
It rotates together with the other of the drive shaft and the driven shaft, partitions the storage chamber into a retard chamber and an advance chamber, and is applied to the housing by the pressure of the working fluid supplied to the retard chamber and the advance chamber. A vane rotor that is driven so as to relatively rotate in a range from the retard angle phase to the most advanced angle phase;
A bearing portion that abuts against the surface of the vane rotor on the side of the anti-driven shaft and rotatably supports the housing, and a support that is formed integrally with the bearing portion and protrudes from the housing toward the anti-vane rotor side. Members,
A fastening member that couples the vane rotor and the support member on the rotation shaft of the driven shaft;
It is a biasing means that is provided around the protruding portion of the support member and forms a coil shape. One end is locked to the housing, and the other end can bias the support member in the advance direction. Urging means for urging the vane rotor in the advance direction,
The housing has first guide means for supporting the vicinity of the one end of the biasing means in the radially outward direction, and second guide means for supporting the vicinity of the other end of the biasing means in the radially outward direction. A valve timing adjusting device characterized by that. The urging means has a bent portion that is bent in a radially inward direction in the vicinity of the other end, and an outermost end portion that is formed on a distal end side of the bent portion,
The housing has first locking means for locking the one end of the biasing means,
The support member has second locking means capable of locking the extreme end of the other end of the biasing means,
In the range from the most retarded phase to a predetermined intermediate phase, the endmost portion is locked by the second locking means of the support member, thereby giving a biasing force in the advance direction to the vane rotor;
In the range from the intermediate phase to the most advanced angle phase, the bent portion is locked to the second guide means, and the endmost portion is released from the second locking means. 2. The valve timing adjusting device according to claim 1, wherein The second guiding means includes
A fixing portion fixed to the housing;
The valve timing adjusting device according to claim 2, further comprising a locking portion that is rotatably supported with respect to the fixed portion and capable of locking the bent portion.

Images