JP5376219B2 - Valve timing control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve opening/closing timing control device certainly restricting a relative rotational phase to a predetermined phase suited for starting of an internal combustion engine when the internal combustion engine is stopped or started. <P>SOLUTION: This valve opening/closing timing control device includes: a drive rotor 2; a driven rotor 3; a fluid pressure chamber 4; a partition section 32 partitioning the fluid pressure chamber 4 into an advance chamber 41 and a retard chamber 42; a working fluid supply/discharge mechanism 7 supplying and discharging working fluid with respect to the fluid pressure chamber 4; a lock mechanism 6 restricting the relative rotational phase of the drive rotor 2 and the driven rotor 3 to the predetermined phase suited for the starting of the internal combustion engine, between a most advance angle phase and a most retard angle phase; and a phase displacement regulation mechanism 5 provided to at least one of the drive rotor 2 and driven rotor 3 separately from the lock mechanism 6 and regulating the displacement of the relative rotational phase to the other side from any one of an advance side and a retard side other than the predetermined phase. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a valve opening / closing timing control device that controls a relative rotation phase of a driven side rotating body with respect to a driving side rotating body that rotates in synchronization with a crankshaft of an internal combustion engine.

  Conventionally, as shown in Patent Document 1, a lock mechanism capable of fixing a relative rotation phase to a predetermined phase between a most advanced angle phase and a most retarded angle phase suitable for starting an internal combustion engine, and a relative rotation phase as a predetermined phase. There has been a valve opening / closing timing control device provided with relative rotation restricting means for restricting between the most advanced angle phase. The above-mentioned relative rotation restricting means is formed on the locking member disposed on one of the driving side rotating body or the driven side rotating body and the other rotating body, and the relative rotation phase is a predetermined phase and a most advanced angle phase. An engaging groove into which the locking member can be engaged is provided.

  In this technique, since the fluid pressure chamber and the partitioning portion are interposed in the rotation transmission path from the drive-side rotator to the driven-side rotator, a force toward the retard side always acts on the driven-side rotator. If the relative rotational phase is on the advance side with respect to the predetermined phase immediately before the internal combustion engine is stopped, the locking member is engaged in the engagement groove, and when the internal combustion engine is stopped in this state, the above-mentioned retard side is reached. Due to this force, the relative rotational phase becomes a predetermined phase. As a result, the relative rotational phase is constrained to a predetermined phase by the lock mechanism.

  On the other hand, when the relative rotation phase is on the retard side from the predetermined phase immediately before the internal combustion engine is stopped, the locking member is not engaged with the engagement groove, and therefore the relative rotation phase is not constrained to the predetermined phase. However, in this technique, both the advance chamber and the retard chamber are communicated with the drain when the internal combustion engine is started, so that the driven-side rotating body largely fluctuates with respect to the driving-side rotating body due to cam fluctuation torque. Due to this fluttering, the locking member is engaged with the locking groove, and the relative rotation phase is restricted from being displaced from the predetermined phase toward the retard side. As a result, the relative rotational phase is constrained to a predetermined phase by the lock mechanism, and the internal combustion engine can be started at the predetermined phase.

  Further, as in Patent Document 2, a lock mechanism capable of fixing the relative rotational phase to a predetermined phase and a phase determination for determining whether the relative rotational phase is on the advance side or the retard side with respect to the predetermined phase. And a valve opening / closing timing control device that performs an active lock operation to displace the relative rotational phase on the side opposite to the determination result by the phase determination mechanism when the internal combustion engine is stopped or started. The lock mechanism includes a lock piece disposed on one of the driving side rotating body and the driven side rotating body, and a locking groove formed on the other rotating body and capable of locking the lock piece. . Further, a locking auxiliary groove whose locking depth by the lock piece is shallower than the locking groove extends from the advance side and the retard side end of the locking groove toward the advance side and the retard side, respectively. ing.

  According to this technique, even when the active locking operation is performed, even if the locking piece and the locking groove are slightly displaced due to a mechanical error or the like, the locking piece is engaged with one of the auxiliary locking grooves. It can be expected to be stopped. That is, the relative rotational phase can be maintained within a phase range that approximates a predetermined phase. As a result, the relative rotational phase fluctuates due to vibration or the like generated when the internal combustion engine is started, and the lock piece is naturally locked in the locking groove adjacent to the auxiliary locking groove.

JP 11-311107 (paragraphs 0025 and 0027 to 0029, FIGS. 2 to 5) JP 2007-132272 (paragraphs 0009 and 0010, FIGS. 3 and 6)

  However, in the technique of Patent Document 1, if the internal combustion engine stops in a state where the relative rotational phase is on the retarded side with respect to the predetermined phase, the above-described retarded side force is applied, so that the cam fluctuation torque The relative rotation phase is not displaced to the advance side from the predetermined phase due to the fluttering based on the above, and there is a possibility that the locking member is not engaged with the locking groove. With this, the lock mechanism cannot restrict the relative rotational phase to a predetermined phase. In particular, when the internal combustion engine is at a low temperature, the displacement force toward the retard side based on the cam fluctuation torque is large, so that the possibility that the locking member does not engage with the locking groove increases. Furthermore, since the circumferential end face of the locking groove is in contact with the protruding portion of the locking member, the protruding portion is subjected to shear stress / bending stress when they collide. As a result, when the locking member is deformed or worn, the phase when the locking member and the end surface of the locking groove abut may be displaced from the predetermined phase.

  In the technique of Patent Document 2, since the relative rotation phase is constrained stepwise by the auxiliary locking groove, there is a possibility that it takes time until the constraining is performed. Further, since the auxiliary locking groove has a depth in the radial direction, there is a restriction that the depth is, for example, about 1 mm. For this reason, there exists a possibility that the reliability of latching with a lock piece and an auxiliary latching groove may become low.

  In view of the above circumstances, the present invention provides a valve opening / closing timing control device capable of reliably restraining a driving side rotating body and a driven side rotating body at a relative rotational phase suitable for starting an internal combustion engine when the internal combustion engine is stopped or started. The purpose is to do.

A first characteristic configuration of a valve timing control apparatus according to the present invention is a drive-side rotator that rotates synchronously with a crankshaft of an internal combustion engine, and is arranged coaxially with the drive-side rotator. A driven-side rotator that rotates synchronously with a camshaft that opens and closes either the intake valve or the exhaust valve, a fluid pressure chamber formed by the drive-side rotator and the driven-side rotator, and the fluid pressure chamber. A partition provided in one of the drive-side rotator and the driven-side rotator to partition the advance chamber and the retard chamber, and a working fluid supply for supplying and discharging a working fluid to and from the fluid pressure chamber An exhaust mechanism and a lock capable of restraining the relative rotational phase of the driving side rotating body and the driven side rotating body to a predetermined phase suitable for starting the internal combustion engine between the most advanced angle phase and the most retarded angle phase. Independent of the mechanism and the lock mechanism, It is provided on at least one of the driven-side rotator, and the one of the advance side and the retard side from the predetermined phase to the other side of the advance side and the retard side from the predetermined phase. A phase displacement regulating mechanism capable of regulating displacement of a relative rotational phase , wherein the phase displacement regulating mechanism includes a first part on the driving side rotating body side and a second part on the driven side rotating body side. And a displacement regulating member having a thickness that causes the relative rotational phase to become the predetermined phase when protruding and sandwiched between the first part and the second part. .

  As in this configuration, it is provided on at least one of the driving side rotating body and the driven side rotating body independently from the lock mechanism, and from the predetermined phase from either the advance side or the retard side from the predetermined phase. If the internal combustion engine is stopped without the relative rotational phase at the specified phase, provided with a phase displacement regulating mechanism that can regulate the displacement of the relative rotational phase to either the advance side or the retard side However, when the internal combustion engine is started next time, for example, when the relative rotational phase is going to be displaced from the advance side to the other side of the predetermined phase from the advance side, it is instantaneous. However, the relative rotation phase is surely stopped once at a predetermined phase. In this way, the lock mechanism can be operated in a state where the relative rotational phase is positioned at the predetermined phase, and the certainty of restraining the relative rotational phase to the predetermined phase is improved.

If the displacement regulating member is sandwiched between the first part and the second part as in this configuration, only the compressive stress is generated in the displacement regulating member, and no shear stress / bending stress is generated. For this reason, the durability of the displacement restricting member is improved, and when the second part comes into contact with the displacement restricting member, the relative rotational phase is surely a predetermined phase. As a result, the certainty of restraint by the lock mechanism is further improved. In addition, since the relative rotational phase can be restricted by a single contact, it can be restrained more quickly than a lock mechanism that restricts in stages.

  A second characteristic configuration of the valve timing control device according to the present invention is that the phase displacement regulating mechanism is regulated and controlled by at least one of supply and discharge of the working fluid to and from the phase displacement regulating mechanism by the working fluid supply / discharge mechanism. The point is to perform at least one of the cancellations.

  With this configuration, it is not necessary to separately provide a restriction / cancellation mechanism dedicated to the phase displacement restriction mechanism. Further, since the phase displacement regulating mechanism is linked to the control of the relative rotational phase, a highly reliable valve opening / closing timing control device can be obtained.

A third characteristic configuration of the valve opening / closing timing control device according to the present invention is that the displacement regulating member moves in and out in a radial direction of the camshaft.

  Since the first member and the second member move relative to each other in the circumferential direction of the camshaft, the rigidity of the members is higher when both members are elongated in the axial direction of the camshaft. If the displacement restricting member is configured to protrude and retract in the axial direction of the camshaft, the driving side rotating body and the driven side rotating body must be enlarged in the axial direction. If it is this structure, a 1st site | part, a 2nd site | part, and a displacement control member can be efficiently arrange | positioned in the radial space of a drive side rotary body and a driven side rotary body.

According to a fourth characteristic configuration of the valve opening / closing timing control device according to the present invention, the displacement restricting member is arranged on the driving side rotating body while being urged so as to protrude radially inward of the camshaft. It is in.

  When the displacement restricting member is urged to protrude radially inward as in this configuration and is disposed on the driving side rotating body, the centrifugal force based on the rotation of the driving side rotating body is utilized. The state where the displacement regulating member is retracted can be maintained. That is, once the displacement regulating member is retracted by supplying the working fluid from the working fluid supply / discharge mechanism, the displacement restricting member maintains the state of being retracted by the centrifugal force. Thus, since control for maintaining the retirement state is not required, the phase displacement regulating mechanism has a simple configuration.

A fifth characteristic configuration of the valve timing control device according to the present invention includes an urging mechanism that urges the relative rotation phase toward an advance side, and the displacement restricting member moves toward a retard side of the relative rotation phase. It is in the point which regulates displacement.

  According to this configuration, even when the internal combustion engine is stopped in a state where the relative rotational phase is on the retarded angle side with respect to the predetermined phase, the relative rotational phase exceeds at least the predetermined phase and is displaced to the advanced angle side. As a result, when the relative rotational phase becomes a predetermined phase, it is possible to restrain the lock mechanism. Therefore, there is no problem that the relative rotation phase is on the retard side with respect to the predetermined phase and the lock mechanism cannot be restrained. Further, if the rotation of the driving side rotating body is reduced, the displacement regulating member protrudes radially inward, and the relative rotation phase is at least on the advance side with respect to the predetermined phase. Therefore, even if the lock mechanism is not restrained, the next internal combustion engine can be started in a state where the relative rotational phase is on the advance side with respect to the predetermined phase.

A sixth characteristic configuration of the valve timing control device according to the present invention is that the urging force by the urging mechanism is larger than the displacement force to the retard side based on the cam fluctuation torque during the rotation of the camshaft. .

  Normally, for example, the intake valve of an internal combustion engine is always urged by a spring or the like so as to close, and the camshaft is urged to the retard side while the cam pushes down the intake valve. Further, after the cam has pushed down the intake valve, the camshaft is biased toward the advance side. That is, the camshaft flutters between the advance side and the retard side due to the cam fluctuation torque. However, since there is sliding friction resistance between the cam and the intake valve and between the intake valve and the spring, the fluttering toward the retard side is larger. Therefore, the displacement force based on the cam fluctuation torque acts on the camshaft and the driven-side rotator so as to displace the relative rotation phase toward the retard side.

  If the urging force by the urging mechanism is larger than the displacement force to the retarded side based on the cam fluctuation torque as in this configuration, the relative rotational phase is reliably set to the advanced side with respect to the predetermined phase when the internal combustion engine is stopped. can do.

According to a seventh characteristic configuration of the valve timing control device of the present invention, a concave portion having a circumferential length corresponding to a range from the most advanced angle phase to the most retarded angle phase is formed along the inner circumferential surface of the drive side rotating body. The second portion is configured to slide along the concave portion.

  With this configuration, it is easy to form the recess, and the configuration of the phase displacement regulating mechanism is simplified. Moreover, the surface which comprises a recessed part can be utilized as a surface which guides that a displacement control member withdraws / withdraws. At this time, the recess functions as the first member.

According to an eighth feature of the valve timing control apparatus of the present invention, the recess is formed between the fluid pressure chambers adjacent to each other, and the height of the recess in the radial direction of the camshaft is equal to the diameter of the camshaft. It is in the point set so that it may become lower than the height of the said fluid pressure chamber in the direction.

  With this configuration, a space is formed on the outer side in the radial direction of the recess, and therefore the phase displacement regulating mechanism can be disposed in the space. That is, even if the phase displacement regulating mechanism is provided, the valve opening / closing timing control device does not become unnecessarily large.

A ninth characteristic configuration of the valve timing control device according to the present invention includes a leak path that communicates the first space on the advance side of the recess and the second space on the retard side that are separated by the second part. It is in the point prepared.

  As described above, the displacement regulating member is retreated by supplying the working fluid. Since the concave portion and the second portion rotate relative to each other, the rotation of the driven side rotating body is hindered when the working fluid stays in the first space. When the leak path is provided as in this configuration, the working fluid stays in the first space due to the pressure of the advance side of the recess and the second member when the relative rotational phase is displaced to the first space side, that is, the advance side. Is returned to the second space. Therefore, the displacement of the relative rotational phase toward the advance side is not hindered.

According to a tenth characteristic configuration of the valve timing control device according to the present invention, the leak path includes an outer peripheral surface of the concave portion in the radial direction of the camshaft and an outer peripheral surface of the second portion in the radial direction of the camshaft. It is in the point prepared for at least one of these.

  Since the driving side rotating body is rotating during operation of the internal combustion engine, the working fluid remaining in the first space is pushed to the outer peripheral surface of the recess by centrifugal force. With this configuration, the working fluid easily flows into the leak path.

It is a vertical side view of a valve opening / closing timing control device. It is a vertical front view of a valve opening / closing timing control device. It is a disassembled perspective view around a phase displacement regulating mechanism. It is a perspective view which shows a protrusion part periphery. It is a figure which shows the valve opening / closing timing control apparatus at the time of engine normal operation. It is a figure which shows the valve opening / closing timing control apparatus at the time of engine normal operation. It is a figure which shows the valve opening / closing timing control apparatus at the time of an engine stop. It is a figure which shows the valve opening / closing timing control apparatus at the time of an engine stop. It is a figure which shows the valve opening / closing timing control apparatus which carried out the retard control from FIG. FIG. 10 is a diagram showing a valve opening / closing timing control device that is advanced from FIG. 9. It is a perspective view which shows the protrusion part periphery of another embodiment. It is a perspective view which shows the protrusion part periphery of another embodiment.

  Hereinafter, an example in which the valve timing control device according to the present invention is applied to an intake valve of an automobile engine will be described with reference to the drawings.

(overall structure)
As shown in FIGS. 1 and 2, the valve opening / closing timing control device 1 is disposed coaxially with the housing 2 as a drive side rotating member that rotates synchronously with a crankshaft (not shown) of the engine. The internal rotor 3 is provided as a driven side rotating member that rotates synchronously with the camshaft 101. Further, the valve opening / closing timing control device 1 is sandwiched between a lock mechanism 6 that locks the relative rotation phase to a predetermined phase suitable for engine start (hereinafter referred to as “intermediate lock phase”), the housing 2 and the internal rotor 3. Thus, a phase displacement restricting mechanism 5 having a displacement restricting member that restricts the relative rotational phase from being displaced more retarded than the intermediate lock phase is provided.

  The intermediate lock phase is a phase between the most advanced angle phase and the most retarded angle phase, and is a limit phase capable of starting the engine. If the engine is started with the intermediate lock phase and the relative rotational phase is displaced to the retard side of the intermediate lock phase when idling after the engine is started, exhaust gas emission suppression, engine fuel efficiency and output will be improved, etc. Can do.

  The internal rotor 3 is integrally assembled with the tip of the camshaft 101 and rotates synchronously with the same axis as the camshaft 101. That is, the radial direction, the circumferential direction, and the axial direction of the inner rotor 3 coincide with the radial direction, the circumferential direction, and the axial direction of the camshaft 101. Although not shown, the camshaft 101 is rotatably assembled to the engine cylinder head.

  The housing 2 includes a rear plate 22 on the side to which the camshaft 101 is connected, a front plate 23 on the side opposite to the side to which the camshaft 101 is connected, and an external rotor 21 having a timing sprocket 24 formed on the outer periphery. I have. The outer rotor 21 is externally mounted on the inner rotor 3, and the outer rotor 21 is sandwiched between the front plate 23 and the rear plate 22. The front plate 23, the external rotor 21, and the rear plate 22 are fastened with bolts 25. The housing 2 is rotatable relative to the inner rotor 3 within a certain range.

  The radial direction, circumferential direction, and axial direction of the housing 2 coincide with the radial direction, circumferential direction, and axial direction of the internal rotor 3. Therefore, in the following description, the terms “radial direction”, “circumferential direction”, and “axial direction” are used as common to the camshaft 101, the housing 2, and the internal rotor 3.

  A power transmission member 102 is installed between the timing sprocket 24 and a gear attached to the crankshaft. The power transmission member 102 is, for example, a timing chain or a timing belt. When the crankshaft is rotationally driven, the rotational driving force is transmitted to the timing sprocket 24 through the power transmission member 102, and the housing 2 is rotationally driven in the driving direction S shown in FIG. As the housing 2 rotates, the inner rotor 3 rotates and the camshaft 101 rotates. As a result, the cam provided on the camshaft 101 pushes down the intake valve of the engine to open it.

Although not shown, as described above, typically, so as to displace the relative rotational phase to the retarded angle side, it acts on the displacement force painter Mushafuto 101 and the internal rotor 3 based on the cam fluctuation torque.

  As shown in FIG. 2, a plurality of projecting portions 21 b projecting radially inward are formed on the outer rotor 21 so as to be separated from each other along the circumferential direction. A fluid pressure chamber 4 is formed by the protruding portion 21 b and the internal rotor 3. In the present embodiment, three fluid pressure chambers 4 are formed, but the present invention is not limited to this.

  A vane groove 31 is formed along the radial direction on the outer peripheral surface 3 a of the inner rotor 3 facing the fluid pressure chamber 4. A vane 32 as a partition portion is inserted into the vane groove 31. The fluid pressure chamber 4 is partitioned into an advance chamber 41 and a retard chamber 42 along the drive direction S by the vane 32. As shown in FIG. 1, the vane 32 is biased radially outward by a spring 33.

  As shown in FIGS. 1 and 2, an advance oil passage 43 is formed in the inner rotor 3 and communicates with the advance chamber 41. A retard oil passage 44 is formed in the inner rotor 3 and communicates with the retard chamber 42. As shown in FIG. 1, the advance oil passage 43 and the retard oil passage 44 are connected to a working fluid supply / discharge mechanism 7 described later.

  The working fluid supply / discharge mechanism 7 supplies or discharges the working fluid to the advance chamber 41 and the retard chamber 42, and displaces the relative rotational phase between the housing 2 and the internal rotor 3 in the advance direction S1 or the retard direction S2. Or held at an arbitrary phase. This working fluid corresponds to so-called working oil. The advance angle direction S1 is a direction in which the vane 32 moves relative to the external rotor 21 and the volume of the advance angle chamber 41 increases, and is indicated by an arrow S1 in the drawing. The retardation direction S2 is a direction in which the volume of the retardation chamber 42 increases, and is indicated by an arrow S2 in the figure.

  A certain range in which the housing 2 and the inner rotor 3 can be rotated relative to each other corresponds to a range in which the vane 32 can be displaced inside the fluid pressure chamber 4. It is the most retarded phase that the volume of the retard chamber 42 is maximized, and the most advanced angle phase that the volume of the advance chamber 41 is maximized. That is, the relative rotational phase can be displaced between the most advanced phase and the most retarded phase.

  As shown in FIG. 1, a torsion spring 26 is provided across the inner rotor 3 and the front plate 23. The internal rotor 3 and the housing 2 are biased by the torsion spring 26 so that the relative rotational phase is displaced in the advance angle direction S1. The inactive force of the torsion spring 26 is set to be larger than the displacement force to the retard side based on the cam fluctuation torque described above, at least when the relative rotational phase is between the most retarded phase and the intermediate lock phase. It is. For this reason, immediately after the engine is stopped, when the relative rotation phase is between the most retarded phase and the intermediate lock phase, the valve opening / closing timing control device 1 determines that the relative rotation phase is at least an advanced angle phase with respect to the intermediate lock phase. It works to become.

(Working fluid supply / discharge mechanism)
The configuration of the working fluid supply / discharge mechanism 7 will be briefly described. As shown in FIG. 1, the working fluid supply / discharge mechanism 7 controls the supply and discharge of the working oil to the pump 71 that is driven by the engine and supplies the working oil, and the advance oil passage 43 and the retard oil passage 44. A flow path switching valve 72 and an oil pan 73 for storing hydraulic oil are provided.

  The pump 71 is a mechanical hydraulic pump that is driven by transmission of the driving force of the crankshaft. The pump 71 sucks the hydraulic oil stored in the oil pan 73 and discharges the hydraulic oil to the downstream side.

  The flow path switching valve 72 operates based on power supply amount control by the ECU 8 (engine control unit). By switching the flow path switching valve 72 and controlling the pump 71, the hydraulic oil is supplied to the advance chamber 41 and discharged from the retard chamber 42, and the hydraulic oil is discharged from the advance chamber 41 and the retard chamber 42. Three types of control are possible: hydraulic oil supply to the hydraulic chamber, hydraulic oil supply / discharge cutoff to the advance chamber 41 and the retard chamber 42. Control for supplying hydraulic oil to the advance chamber 41 and discharging hydraulic oil from the retard chamber 42 is “advance control”. When the advance angle control is performed, the vane 32 moves relative to the external rotor 21 in the advance angle direction S1, and the relative rotation phase is displaced toward the advance angle side. Control for discharging hydraulic oil from the advance chamber 41 and supplying hydraulic oil to the retard chamber 42 is “retard control”. When the retard control is performed, the vane 32 moves relative to the external rotor 21 in the retard direction S2, and the relative rotation phase is displaced toward the retard side. When the control for shutting off the supply and discharge of the hydraulic oil to and from the advance chamber 41 and the retard chamber 42 is performed, the vane 32 does not move relatively, and the relative rotation phase can be maintained at an arbitrary phase.

(Lock mechanism)
As shown in FIG. 2, the lock mechanism 6 is provided on the outer rotor 21 and is formed on the outer peripheral surface 3 a of the inner rotor 3. And a groove 62. The lock member 63 is urged radially inward by a spring 64. The lock groove 62 is slightly larger than the lock member 63 so that the lock member 63 can enter. When the lock member 63 enters the lock groove 62, the relative rotational phase is constrained to the intermediate lock phase, and when the lock member 63 is retracted from the lock groove 62, the restraint is released and the displacement of the relative rotational phase is allowed.

  A lock oil passage 61 formed in the inner rotor 3 is connected to the lock groove 62. The advance chamber 41 adjacent to the lock mechanism 6 and the lock oil passage 61 are communicated by an advance chamber communication passage 65 that is a groove formed in the outer peripheral surface 3 a of the internal rotor 3. When the lock member 63 enters the lock groove 62, the lock groove 62 and the advance chamber communication passage 65 are blocked. When the lock member 63 is retracted, the lock groove 62 and the advance chamber communication passage 65 communicate with each other.

  The lock oil passage 61 also serves as the advance oil passage 43 to the adjacent advance chamber 41 described above, and hydraulic oil is supplied to the lock oil passage 61 when the advance angle control is performed. When the lock member 63 is pressed radially outward by the hydraulic pressure of the hydraulic oil and the pressing force becomes larger than the urging force of the spring 64, the lock member 63 is retracted from the lock groove 62 and restrained to the intermediate lock phase. Is released. After the restraint is released, the lock oil passage 61 and the advance chamber communication passage 65 communicate with each other, and if the advance angle control is performed, the hydraulic oil is supplied to the adjacent advance chamber 41 described above.

(Phase displacement regulating mechanism)
As shown in FIG. 2, the phase displacement regulating mechanism 5 includes a recess 52 as a first part formed in the external rotor 21, a protrusion 53 as a second part formed in the internal rotor 3, and the external rotor 21. The provided displacement regulating member 51 and an accommodating portion 54 that is formed in the external rotor 21 and accommodates the displacement regulating member 51 are provided.

  As shown in FIG. 2, the recess 52 is formed over the entire axial direction along the inner peripheral surface 21 a of the outer rotor 21. As shown in FIG. 3, the concave portion includes an end surface 52 a on the advance side, an end surface 52 b on the retard side, and an outer peripheral surface 52 c.

  As shown in FIG. 4, the protrusion 53 is formed so as to protrude in a plate shape radially outward along the outer peripheral surface 3 a of the inner rotor 3. The protrusion 53 is formed over the entire area in the axial direction of the portion (see FIG. 1) in contact with the external rotor 21. The protrusion 53 includes an advanced angle side surface 53a, a retarded angle side surface 53b, and an outer peripheral surface 53c.

  As shown in FIG. 2, the protruding height of the protruding portion 53 in the radial direction is set slightly lower than the height H <b> 2 of the recessed portion 52. The outer rotor 21 and the inner rotor 3 are assembled so that the protrusion 53 is positioned inside the recess 52. When the inner rotor 3 rotates relative to the outer rotor 21, the outer peripheral surface 53c of the protrusion 53 and the outer peripheral surface 52c of the recess 52 slide with each other. Further, the space formed by the recess 52 and the outer peripheral surface 3a of the inner rotor 3 is, for example, as shown in FIG. 6, the first space 57 on the advance side and the second space 58 on the retard side by the protrusion 53. It is separated by.

  When the relative rotational phase becomes the most advanced angle phase, the side surface 53a of the protrusion 53 reaches the end surface 52a of the recess 52, and when the relative rotational phase becomes the most retarded phase, the side surface 53b reaches the end surface 52b. As such, the circumferential length of the recess 52 is set. That is, the circumferential length of the recess 52 corresponds to the range from the most advanced phase to the most retarded phase. However, the side surface 53a and the end surface 52a and the side surface 53b and the end surface 52b do not need to contact each other.

  The height H2 in the radial direction of the recess 52 is a constant height over the entire region, and is set lower than the height H1 in the radial direction of the fluid pressure chamber 4. The accommodating portion 54 is formed on the outer side of the concave portion 52 in the outer rotor 21. The accommodating portion 54 is formed over the entire axial direction of the external rotor 21. The side surface 54a of the housing portion 54 is formed by extending the end surface 52b of the recess 52 radially outward. In this way, the space 54 on the outer side in the radial direction than the recess 52 is effectively used to form the accommodating portion 54. Therefore, the phase displacement regulating mechanism 5 does not become unnecessarily large in the circumferential direction, and the influence on the circumferential arrangement of the fluid pressure chamber 4 and the lock mechanism 6 can be reduced.

  As shown in FIG. 3, the displacement regulating member 51 is a plate-like member that is slightly smaller than the internal space of the housing portion 54, and is disposed in the housing portion 54. The displacement regulating member 51 can be withdrawn and withdrawn in the radial direction with its side surface 51 b along the side surface 54 a of the accommodating portion 54 and the end surface 52 b of the recess 52. The displacement regulating member 51 is urged by a spring 59 so as to protrude inward in the radial direction. The displacement regulating member 51 protrudes until the front end portion 51 c contacts the outer peripheral surface 3 a of the internal rotor 3. A notch 51d for engaging the spring 59 is formed on the radially outer side of the displacement restricting member 51, but the notch 51d is accommodated in the accommodating portion 54 even when the displacement restricting member 51 protrudes.

  The displacement regulating member 51 is retracted to the accommodating portion 54 by supplying the working fluid from the working fluid supply / discharge mechanism 7. As shown in FIG. 4, a restriction oil passage 55 for supplying and discharging the working fluid from the working fluid supply and discharge mechanism 7 is formed in the internal rotor 3. On the outer peripheral surface 3 a of the internal rotor 3, a restriction release groove 56 is formed along the circumferential direction on the retard side with respect to the protrusion 53. The width of the restriction release groove 56 is set slightly wider than the outer diameter of the restriction oil passage 55, and the restriction oil passage 55 is opened to the restriction release groove 56.

  As shown in FIG. 1, the restriction oil passage 55 is branched from the retardation oil passage 44, and hydraulic oil is also supplied to the restriction oil passage 55 when the retardation control is performed. As a result, hydraulic oil is also supplied to the restriction release groove 56. When the restriction release groove 56 is filled with the hydraulic oil and the hydraulic pressure of the hydraulic oil becomes larger than the urging force of the spring 59, the displacement regulating member 51 is retracted to the accommodating portion 54 as shown in FIGS. When the hydraulic oil is discharged, the displacement regulating member 51 protrudes due to the urging force of the spring 59. As shown in FIG. 4, the restriction release groove 56 is formed near the center in the axial direction on the outer peripheral surface 3 a, and the displacement restricting member 51 is hydraulically applied in a well-balanced manner.

  When the displacement restricting member 51 is once retracted and the rotational speed of the housing 2 is increased, a centrifugal force outward in the radial direction acts, and the displacement restricting member 51 maintains the retracted state. However, at what speed the housing 2 rotates, such a centrifugal force is generated by adjusting the strength of the urging force of the spring 59 and the weight of the displacement regulating member 51.

  If the displacement restricting member 51 protrudes, the displacement restricting member 51 becomes an obstacle, and the inner rotor 3 cannot further rotate in the retarding direction S2. At this time, the displacement regulating member 51 is sandwiched between the end surface 52 b of the recess 52 and the side surface 53 b of the protrusion 53. In this state, the thickness t in the circumferential direction of the displacement restricting member 51 is set so that the relative rotational phase matches the intermediate lock phase. That is, the circumferential thickness t of the displacement regulating member 51 corresponds to the phase difference between the most retarded phase and the intermediate lock phase.

  As described above, the phase displacement regulating mechanism 5 is provided on the drive side rotating body independently of the lock mechanism 6, and has a relative rotational phase from the advance side to the retard side of the intermediate lock phase from the intermediate lock phase. Regulate displacement. Since the displacement regulating member 51 is sandwiched to regulate the displacement, only the compressive stress acts on the displacement regulating member 51 even if the projection 53 collides with the displacement regulating member 51 vigorously. Stress does not work. Therefore, the durability of the displacement restricting member 51 is improved, and when the protrusion 53 comes into contact with the displacement restricting member 51, the relative rotation phase surely becomes the intermediate lock phase. In addition, since displacement is regulated by contact between wide surfaces such as the side surface 51a and the side surface 53b, the reliability of phase regulation is high.

  As shown in FIG. 2, the phase displacement regulating mechanism 5 is formed in the vicinity of the bolt 25 and substantially concentrically with the bolt 25. For this reason, due to the impact caused by the collision between the projection 53 and the side surface 51a when the displacement regulating member 51 protrudes, and the impact caused by the collision between the projection 53 and the end surface 52b when the displacement regulating member 51 is retracted. Further, it is possible to reduce damage to the portion between the bolt 25 and the phase displacement regulating mechanism 5 in the protruding portion 21b.

  The restriction release groove 56 extends from the side surface 53b of the protrusion 53 to the circumferential retard side with a certain circumferential length. For this reason, when the retard control is performed from the state shown in FIG. 8, the restriction release groove 56 and the second space 58 are filled with the hydraulic oil. When the hydraulic pressure rises, the displacement regulating member 51 is retracted as shown in FIG. That is, the displacement restricting member 51 is retracted in advance from the previous stage. Therefore, the protrusion 53 does not interfere with the displacement regulating member 51, and the relative rotational phase smoothly exceeds the intermediate lock phase and is displaced to the retard side. In this case, while the retard angle control is performed, the hydraulic pressure of the hydraulic oil in the second space 58 acts on the advance side with respect to the protrusion 53. However, there are three fluid pressure chambers 4 for one recess 52. Moreover, the height H1 of the fluid pressure chamber 4 is higher than the height H2 of the recess 52. Therefore, the retarding force acting on the three locations of the vane 32 is greater in each step than the advancing force acting on the protrusion 53. As a result, even if a force toward the advance side acts on the protrusion 53, there is no problem in the retard control.

(Leak road)
Since the housing 2 and the inner rotor 3 rotate relative to each other, there is a slight gap between the recess 52 and the protrusion 53. For this reason, the hydraulic oil supplied to the second space 58 may leak into the first space 57. If the leaked hydraulic oil remains in the first space 57, when the advance angle control is performed, the leaked hydraulic oil is sandwiched between the side surface 53a and the end surface 52a, and the displacement to the vicinity of the most advanced angle phase is inhibited. Therefore, as shown in FIG. 4, a groove 53 d is formed near the center of the outer peripheral surface 53 c of the protrusion 53 as a leak path that connects the first space 57 and the second space 58. Therefore, the hydraulic oil leaked into the first space 57 is sandwiched and pressed between the side surface 53a of the projection 53 and the end surface 52a of the recess 52 based on the advance angle control, and enters the second space 58 via the leak path. The leak can be returned. Therefore, the advance angle control to the vicinity of the most advanced angle phase can be appropriately performed. However, the groove 53d is a small groove that can secure a hydraulic pressure for retracting the displacement regulating member 51.

  When the camshaft 101 rotates, the hydraulic oil leaked by the centrifugal force is pushed to the outer peripheral surface 52 c of the recess 52. Since the leak path is formed radially outward, the hydraulic oil easily flows into the groove 53d.

(Operation of valve timing control device)
Hereinafter, the operation of the valve timing control apparatus 1 will be described.

  During normal engine operation, as shown in FIGS. 5 and 6, the lock member 63 is retracted from the lock groove 62, and the relative rotational phase can be freely displaced. The advance angle control, the retard angle control, and the control for maintaining the phase are performed in accordance with the operating state of the engine. During this time, the displacement regulating member 51 is normally retracted by centrifugal force. Even if the displacement restricting member is not held in the retracted state by the centrifugal force, there is no problem even if the displacement restricting member 51 protrudes during the advance angle control that is the displacement toward the advance angle side. Further, at the time of retarding control, which is the displacement toward the retarding side, there is no problem because the displacement regulating member 51 is retracted by the retarding control.

  The operation when the engine is stopped will be described according to the state of the relative rotation phase immediately before the engine is stopped. When the engine is stopped, the hydraulic oil is discharged from the advance chamber 41, the retard chamber 42, and the second space 58, and the hydraulic pressure of the hydraulic oil does not act. However, until the rotation of the camshaft 101 is completely stopped, a displacement force toward the retard side based on the cam fluctuation torque described above acts.

  As shown in FIG. 5, immediately before the engine is stopped, when the relative rotational phase is on the retarded side with respect to the intermediate lock phase, when the engine is stopped, the torsion spring 26 is superior to the retarding force on the retarded side based on the cam fluctuation torque. Due to the urging force, the relative rotation phase exceeds the intermediate lock phase and is displaced to the advance side. At this time, the displacement regulating member 51 is blocked by the protrusion 53 and cannot protrude into the recess 52. Thereafter, when the intermediate lock phase is reached, the lock member 63 enters the lock groove 62, and the relative rotational phase is constrained to the intermediate lock phase. At the same time, the protruding portion 53 is displaced from the accommodating portion 54, and the regulating member also protrudes. That is, the valve opening / closing timing control device 1 stops in the state shown in FIG.

  If the lock member 63 cannot enter the lock groove 62 during the intermediate lock phase due to fluttering or the like based on cam fluctuation torque, as shown in FIG. 8, the relative rotation phase is more advanced than the intermediate lock phase. In this state, the valve opening / closing timing control device 1 stops.

  Immediately before the engine is stopped, as shown in FIG. 6, when the relative rotational phase is on the advance side of the intermediate lock phase, when the engine is stopped, the displacement regulating member 51 first protrudes into the recess 52 as shown in FIG. 8. When the urging force of the torsion spring 26 is larger than the displacement force to the retard side based on the cam fluctuation torque on the advance side of the intermediate lock phase, the relative rotation phase is on the advance side of the intermediate lock phase as it is. It stops and is not restrained by the lock mechanism 6.

  When the displacement force to the retard side based on the cam fluctuation torque is larger than the biasing force of the torsion spring 26 on the advance side from the intermediate lock phase, the relative rotation phase is delayed until the cam is completely stopped. Displace to the corner side. When the projection 53 comes into contact with the displacement regulating member 51, the projection 53 is pressed against the side surface 51 a of the displacement regulating member 51 by a displacement force based on the cam fluctuation torque. The relative rotation phase is positioned at the intermediate lock phase, the lock member enters the lock groove 62, and the relative rotation phase is constrained to the intermediate lock phase. That is, the valve opening / closing timing control device 1 stops in the state shown in FIG.

  As described above, when the engine is completely stopped, as shown in FIG. 7, the relative rotation phase is constrained to the intermediate lock phase and the displacement restricting member 51 is projected, or the relative rotation phase is set to the intermediate lock as shown in FIG. The valve opening / closing timing control device 1 stops in any state where the displacement regulating member 51 protrudes while being on the advance side of the phase. In any case, the displacement regulating member 51 protrudes.

  The operation when the engine is restarted will be described. As shown in FIG. 7, when the engine is restarted in a state where the relative rotation phase is constrained to the intermediate lock phase and the displacement restricting member 51 protrudes, the engine can be appropriately started in the intermediate lock phase.

  Thereafter, retardation control is performed, and the displacement regulating member 51 is retreated as shown in FIG. After a while, the rotation speed of the camshaft 101 increases, and the displacement regulating member 51 is held in a retreated state by centrifugal force. Further, advance angle control is performed, and as shown in FIG. 10, the lock member 63 is retracted from the lock groove 62, and the restriction on the relative rotation phase is released. Thereafter, advance angle control, retard angle control, and control for maintaining the phase are performed according to the operating state of the engine, and the relative rotational phase is displaced to a phase according to the operating state of the engine.

  As shown in FIG. 8, when the engine is restarted in a state in which the displacement restricting member 51 protrudes while the relative rotational phase is on the advance side with respect to the intermediate lock phase, the displacement force based on the cam fluctuation torque causes relative displacement. The rotational phase is displaced to the retarded angle side, and the protrusion 53 contacts the side surface 51 a of the displacement regulating member 51. The relative rotation phase is not displaced to the retard side from the intermediate lock phase. At this time, although there is some flutter, the relative rotation phase stops at the intermediate lock phase at the moment when the projection 53 collides with the side surface 51a of the displacement regulating member 51. The lock mechanism 6 is more easily constrained than when the phase is fluttered toward the retard side and the advance side with respect to the phase. Therefore, as shown in FIG. 7, the lock member 63 enters the lock groove 62, and the relative rotation phase is constrained to the intermediate lock phase. Furthermore, even if the lock mechanism 6 is not restrained, at least the relative rotational phase is on the advance side with respect to the intermediate lock phase, so there is no problem in starting the engine itself. Subsequent operations are the same as the above-described operations, and thus description thereof is omitted.

  In the present embodiment, the spring 64 and the spring 59 are set so that the urging force of the spring 64 of the lock mechanism 6 is larger than the urging force of the spring 59 of the phase displacement regulating mechanism 5. For example, when the engine is started in a state where the hydraulic oil is high temperature and its viscosity is low, it is difficult to ensure the hydraulic pressure for releasing the phase displacement regulating mechanism 5 and the lock mechanism 6. Therefore, the displacement regulating member 51 and the lock 63 may be retreated due to the centrifugal force caused by the rotation of the camshaft 101. In this case, according to this configuration, the phase displacement restriction mechanism 5 is released before the lock mechanism 6 is released. Therefore, if the lock member 63 is retracted, the phase displacement regulation mechanism 5 is not regulated, so that the relative rotation phase can be displaced to the retard side from the intermediate lock phase. As a result, for example, it is possible to quickly suppress exhaust gas emission and improve fuel efficiency during engine idling.

  In the above embodiment, the recess 52 is formed separately from the fluid pressure chamber 4 to configure the phase displacement restricting mechanism 5, but the present invention is not limited to this. For example, although not shown, the phase displacement regulating mechanism 5 may be configured with the fluid pressure chamber 4 as a recess 52 and the vane 32 as a projection 53. In this case, a space for forming the accommodating portion 54 is secured by decreasing the radial height H1 of the fluid pressure chamber 4 or expanding the external rotor 21 radially outward. Or you may change and arrange | position the arrangement | positioning of the phase displacement control mechanism 5, the protrusion direction of the displacement control member 51, etc.

  In the present embodiment, the restriction oil passage 55 is branched from the retard oil passage 44, but may be an oil passage independent of the advance oil passage 43 and the retard oil passage 44. If the oil passage is different from at least the oil passage communicating with the lock mechanism 6, the valve opening / closing timing control device 1 can be appropriately operated.

  Although only one pump 71 is provided in the present embodiment, a second pump that is driven by power different from that of the internal combustion engine and supplies the working fluid to the phase conversion mechanism may be provided. When the second pump is provided, when the hydraulic oil supply amount from the pump 71 is insufficient, the shortage can be compensated.

(Another embodiment)
In the above-described embodiment, the leak path is formed on the outer peripheral surface 53c of the protrusion 53. However, the present invention is not limited to this. For example, as shown in FIG. 11, the leak path may be formed on the outer peripheral surface 52 c of the recess 52. In this case, the groove 52d as a leak path is formed over the entire circumferential direction of the outer peripheral surface 52c.

  Also, as shown in FIG. 12, the protruding corner of the outer peripheral surface 53c of the protrusion 53 may be chamfered to form a chamfered portion 53e as a leak path. Although not shown, the protruding corner of the outer peripheral surface 52c of the recess 52 may be chamfered. In these cases, if the position of the restriction release groove 56 is changed to the vicinity of the protruding corner of the external rotor 21 according to the position of the leak path, the processing is easy.

  In the above-described embodiment, an example in which the valve opening / closing timing control device 1 is applied to an intake valve has been described. However, the valve opening / closing timing control device 1 for an exhaust valve may be used. However, in this case, since the valve opening / closing timing required for the intake valve and the exhaust valve is different, it is necessary to change the control of the hydraulic pressure and the configuration of the oil passage.

  The present invention is a valve that can reliably restrain the relative rotational phase to a predetermined phase suitable for starting an internal combustion engine when the internal combustion engine is stopped or started, and controls the opening and closing timings of an intake valve and an exhaust valve of an engine such as an automobile. The present invention can be applied to an opening / closing timing control device.

1 Valve opening / closing timing control device 2 Housing (drive side rotating body)
3 Internal rotor (driven rotor)
4 Fluid pressure chamber 5 Phase displacement regulating mechanism 6 Lock mechanism 7 Working fluid supply / discharge mechanism 21a Inner peripheral surface 26 Torsion spring (biasing mechanism)
32 Vane (partition)
41 Advance chamber 42 Delay chamber 51 Displacement restricting member 52 Recessed portion (first portion)
52c Outer peripheral surface 53 Protrusion (second part)
53c Outer peripheral surface 53d Groove (leakage path)
57 1st space 58 2nd space 101 Camshaft t Thickness H1 Height H2 Height

Claims (10)

A drive side rotating body that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating body that is coaxially disposed with respect to the driving-side rotating body and that rotates synchronously with a camshaft that opens and closes either the intake valve or the exhaust valve of the internal combustion engine;
A fluid pressure chamber formed by the driving side rotating body and the driven side rotating body;
A partition provided in any one of the driving side rotating body and the driven side rotating body to partition the fluid pressure chamber into an advance chamber and a retard chamber;
A working fluid supply and discharge mechanism for supplying and discharging a working fluid to and from the fluid pressure chamber;
A lock mechanism capable of constraining a relative rotation phase between the driving side rotating body and the driven side rotating body to a predetermined phase suitable for starting the internal combustion engine between a most advanced angle phase and a most retarded angle phase;
Independently of the lock mechanism, it is provided on at least one of the drive side rotating body and the driven side rotating body, and advances from the predetermined phase toward the predetermined phase from either the advance side or the retard side. with the to either the other side of the corner side or the retarding side is possible restrict the displacement of the relative rotational phase phase displacement restriction mechanism, a city,
The phase displacement restricting mechanism protrudes and retracts between a first part on the driving side rotating body side and a second part on the driven side rotating body side, and protrudes to protrude from the first part and the second part. And a displacement regulating member having a thickness such that the relative rotational phase becomes the predetermined phase when sandwiched between the valve opening and closing timing control device.   2. The valve opening / closing timing according to claim 1, wherein the phase displacement restriction mechanism performs at least one of restriction and release thereof by at least one of supply and discharge of the working fluid to and from the phase displacement restriction mechanism by the working fluid supply / discharge mechanism. Control device. The valve opening / closing timing control device according to claim 1 or 2 , wherein the displacement regulating member moves in and out in a radial direction of the camshaft. The valve opening / closing timing control device according to claim 3 , wherein the displacement regulating member is disposed on the driving-side rotating body while being urged so as to protrude radially inward of the camshaft. Provided with a biasing mechanism for biasing the relative rotational phase to the advanced angle side, the displacement regulating member according to any one of 4 claims 1 to regulate the displacement of the retard side of the relative rotational phase Valve timing control device. 6. The valve opening / closing timing control device according to claim 5 , wherein an urging force by the urging mechanism is larger than a displacement force toward the retard side based on a cam fluctuation torque during rotation of the camshaft. Forming a concave portion having a circumference corresponding to a range from the most advanced angle phase to the most retarded angle phase along the inner circumferential surface of the drive side rotating body;
The valve opening / closing timing control device according to any one of claims 1 to 6 , wherein the second portion is configured to slide along the recess. The recess is formed between the adjacent fluid pressure chambers,
The valve opening / closing timing control device according to claim 7 , wherein the height of the concave portion in the radial direction of the camshaft is set to be lower than the height of the fluid pressure chamber in the radial direction of the camshaft. 9. The valve opening / closing timing control device according to claim 7, further comprising a leak path that communicates the first space on the advance side of the concave portion and the second space on the retard side separated by the second portion. 9. The valve opening / closing according to claim 9 , wherein the leak path is provided on at least one of an outer peripheral surface of the concave portion in the radial direction of the camshaft and an outer peripheral surface of the second portion in the radial direction of the camshaft. Timing control device.

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