JP5954056B2 - Valve timing control device - Google Patents

Description

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

  In recent years, a valve opening / closing timing control device that can change the opening / closing timings of an intake valve and an exhaust valve in accordance with an operating state of an internal combustion engine (hereinafter also referred to as an engine) has been put into practical use. This valve opening / closing timing control device is, for example, an intake / exhaust valve that opens and closes as the driven side rotating member rotates by changing the relative rotation phase of the driven side rotating member with respect to the rotation of the driven side rotating member caused by the operation of the engine. It has a mechanism to change the opening and closing timing of.

  In general, the optimum opening / closing timing of the intake / exhaust valves varies depending on the operating conditions of the engine such as when the engine is started and when the vehicle is running. Therefore, when the engine is started, the relative rotational phase of the driven side rotational member with respect to the rotation of the driving side rotational member is constrained to a predetermined phase between the most retarded angle phase and the most advanced angle phase, which is optimal for engine startup. The opening and closing timing of the intake and exhaust valves is realized. Further, it is desirable to change the phase to the most retarded phase at which it is easy to restart the engine in a high temperature state at the time of idling stop in which the engine is temporarily stopped when the brake pedal is depressed during normal operation.

  In Patent Document 1, it is possible to constrain the relative rotational phase between the driving side rotating member and the driven side rotating member by selecting the phase that provides the optimum valve opening / closing timing at the start according to the state of the internal combustion engine. A valve opening / closing timing control device is disclosed. In this valve opening / closing timing control device, an external rotor that rotates synchronously with a crankshaft of an internal combustion engine, an internal rotor that is arranged coaxially with the external rotor and that rotates synchronously with a camshaft, and a relative rotational phase between the external rotor and the internal rotor A lock mechanism capable of restraining the displacement of the actuator at a predetermined lock phase, and the displacement of the relative rotation phase that is operable independently of the lock mechanism and exceeds a set phase displacement allowable range including the lock phase is regulated. And a possible phase displacement regulating mechanism.

  The phase displacement restricting mechanism includes a protruding member (corresponding to a restricting member of the present invention) that can be moved back and forth from the outer rotor side to the inner rotor side, and a restricting recess that is provided on the inner rotor and can be fitted into the protruding member. . The protruding member is slidably provided along a sliding groove provided in the external rotor, and is urged radially inward by an urging spring. The restriction recess is formed in the inner rotor and communicates with a restriction passage that is a passage for supplying and discharging hydraulic oil. Switching of the supply and discharge of hydraulic oil to and from the restriction passage is performed by a second control valve (corresponding to the release control valve of the present invention). When the energization of the second control valve is interrupted and hydraulic oil flows through this restriction passage and is supplied to the restriction recess, the hydraulic oil release pressure acts on the pressure receiving surface of the protrusion member, and the protrusion member becomes the restriction recess. Retired from the control status is released. That is, when the hydraulic oil is supplied and filled in the restriction recess, and the hydraulic oil acts on the pressure receiving surface to urge the protruding member radially outward, the protruding member becomes larger than the urging force of the urging spring. Retract from the restricting recess and enter the released state.

  FIG. 12 shows changes in the operation of the second control valve, the pressure of hydraulic oil (regulation release hydraulic pressure) acting on the end surface of the protruding member until the state of release from the restricted state in the most retarded phase, and the operation of the protruding member. A time chart is shown. As shown in FIG. 12, when the energization of the second control valve is interrupted and the hydraulic oil flows through the restriction passage, and the hydraulic oil reaches the pressure receiving surface of the protruding member, the restriction release hydraulic pressure starts to rise. When the regulation release hydraulic pressure reaches the release hydraulic pressure, the protruding member starts to be separated from the bottom surface of the regulation recess. When the projecting member moves away from the bottom surface of the restricting recess and the hydraulic oil flows into the restricting recess, the regulation release hydraulic pressure acting on the pressure receiving surface of the projecting member is reduced due to the spreading of the working oil into the restricting recess. Then, as the hydraulic oil is filled into the regulating recess, the regulation release hydraulic pressure that acts on the pressure receiving surface of the projecting member returns again, and the retraction of the projecting member from the regulating recess is completed.

JP 2006-348926 A

  In the valve opening / closing timing control device disclosed in Patent Document 1, as shown in FIG. 12, the time T from when the second control valve is de-energized until the protruding member is retracted operates the volume of the regulating recess. Since the retraction of the projecting member is not completed until it is filled with oil, it takes a long time and there is a problem that it is difficult to quickly change the relative rotational phase. If the control to change the relative rotational phase is started before the retraction of the projecting member is completed, the projecting member remains in the restricting recess, so that a circumferential force, that is, a shearing force acts on the projecting member, and the relative rotational phase. There is a problem in that it cannot be changed and a defect occurs.

  In view of the above problems, an object of the present invention is to provide a valve opening / closing timing control device capable of quickly retracting a regulating member from a regulating recess.

  In order to solve the above problems, the characteristic configuration of the valve timing control apparatus according to the present invention is arranged on a drive side rotation member that rotates synchronously with a crankshaft of an internal combustion engine, and on the same axis as the drive side rotation member, A driven side rotating member that rotates synchronously with a camshaft for opening and closing the valve of the internal combustion engine, a fluid pressure chamber formed by the driving side rotating member and the driven side rotating member, the driving side rotating member, and the driven side Advancing angle control and retarding chamber formed by partitioning the fluid pressure chamber with a partition provided on at least one of the rotating members, and an advance angle control that is a passage for the working fluid supplied to and discharged from the advanced angle chamber A passage, a retard control passage that is a passage of working fluid supplied to and discharged from the retard chamber, a regulating member provided in one of the drive side rotation member and the driven side rotation member, and the drive side rotation Member and said driven side rotating part A regulating recess provided on the other and a pressure member having a portion placed on the regulation recess, and the regulation member protrudes to fit into the regulation recess and abut against the pressure member The relative rotational phase of the driven side rotational member with respect to the driving side rotational member is changed from one of the most advanced angle phase and the most retarded angle phase to a predetermined phase between the most advanced angle phase and the most retarded angle phase. A restriction mechanism that can be switched between a state restricted to a range and a state in which the restriction is released when the restriction member is retreated from the restriction recess by pressurization by the pressure member, and the working fluid is connected to the restriction recess A passage through which the advance chamber, the retard chamber, the advance control passage, and a restriction release passage that does not communicate with any of the retard control passages are supplied from the restriction release passage. Working fluid The pressure, the pressure member is in point pressurizing the regulating member is displaced in a direction away from the bottom surface of the restricting recess.

  With such a characteristic configuration, it is not necessary to fill the regulating recess with the working fluid in order to retract the regulating member. When hydraulic pressure acts on the pressure member, the pressure member is displaced, and the regulating member is retracted. Accordingly, there is no time delay that the retraction of the restricting member is not completed until the working fluid is filled in the restricting recess, and the retraction of the restricting member can be completed in a short time and the restriction can be released. As a result, the relative rotational phase can be quickly changed.

  In the valve opening / closing timing control device according to the present invention, the pressurizing member includes a pressurizing part in the restricting recess and a sliding part inserted in the restricting release passage, and the pressurizing part includes the pressurizing part. It is preferable that the area of the pressing surface in contact with the regulating member is larger than the cross-sectional area in the direction perpendicular to the flow direction of the working fluid in the sliding portion.

  With such a configuration, the force acting on the end surface of the sliding portion due to the hydraulic pressure of the working fluid increases in accordance with the area ratio between the end surface and the pressure surface, and a large force can be generated on the pressure surface. Therefore, even if the hydraulic pressure applied to the end surface is small, the increased force is applied to the pressure receiving surface of the restricting member, so that the retraction of the restricting member can be completed in a short time. As a result, even when a small hydraulic pump having a low discharge capacity is used, a rapid change in relative rotational phase can be realized.

  In the valve opening / closing timing control device according to the present invention, when the pressurizing portion and the bottom surface of the restricting recess are in contact with each other when viewed along the flow direction of the working fluid, the pressurizing portion and the restricting recess When the pressure member is displaced until the pressure surface reaches the boundary between the drive side rotation member and the driven side rotation member, the pressure surface becomes the drive side rotation member and It is preferable that either one of the driven-side rotating members is flush with the other boundary surface.

  With such a configuration, regardless of which relative rotation phase the regulation member retreats from the regulation recess, when the relative rotation phase is changed, the regulation member is either the drive side rotation member or the driven side rotation member. The pressurizing member is not caught by either the moving side rotating member or the driven side rotating member, and the relative rotational phase can be changed smoothly.

  In the valve opening / closing timing control device according to the present invention, the cross-sectional shape in the direction perpendicular to the flow direction of the working fluid in the sliding portion and the restriction release passage is the other of the driving side rotating member and the driven side rotating member. It is preferable that the shape extends over the entire pressure portion along the circumferential direction.

  With such a configuration, even if the regulating member protrudes from the circumferential end of the pressure member, the pressure member is inclined because the sliding portion receives the force applied from the regulating member. It can slide without.

It is a longitudinal section showing the composition of the valve timing control device concerning a 1st embodiment. FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 1 and shows a locked state at an intermediate lock phase. It is sectional drawing showing the state of the most retarded angle phase of a valve timing control apparatus. It is sectional drawing showing the state of the most advance angle phase of a valve timing control apparatus. It is sectional drawing showing the lock release state in the intermediate | middle lock phase of a valve opening / closing timing control apparatus. It is a perspective view showing the structure of a 1st control mechanism. It is a time chart of control of a valve timing control device. It is a perspective view showing the shape of the piston used with the valve timing control apparatus which concerns on the modification of 1st Embodiment. It is a perspective view showing the shape of the piston used with the valve timing control apparatus which concerns on 2nd Embodiment. It is a partial expanded sectional view showing the structure of the 2nd control mechanism of the valve timing control apparatus which concerns on 3rd Embodiment. It is a perspective view showing the shape of the piston used with the valve timing control apparatus which concerns on 3rd Embodiment. It is a time chart of control of the conventional valve timing control apparatus.

1. First embodiment [basic configuration]
Hereinafter, a first embodiment of the present invention will be described in detail with reference to the drawings. FIG. 1 is a longitudinal sectional view showing a configuration of a valve opening / closing timing control device 10 according to the present embodiment, and FIG. 2 is a sectional view taken along line II-II in FIG. 1 and showing a locked state at an intermediate lock phase P1. The figure is shown. As shown in FIGS. 1 and 2, a valve opening / closing timing control device 10 that sets an opening / closing timing of an intake valve (not shown) of an engine E as an internal combustion engine, and an engine control unit (ECU) 40 that controls the engine E. An internal combustion engine control system including the above is configured.

  An engine E shown in FIG. 1 is provided in a vehicle such as a passenger car, and includes a starter motor M that transmits driving rotational force to the crankshaft 1, and a fuel control device 5 that controls fuel injection into an intake port or a combustion chamber. , An ignition control device 6 that controls ignition by a spark plug (not shown), and a shaft sensor 1S that detects a rotation angle and a rotation speed of the crankshaft 1 are provided. The valve timing control device 10 is provided with a phase detection sensor 46 that detects the relative rotational phase between the external rotor 11 and the internal rotor 12. The phase detection sensor 46 is not limited to one that directly detects the relative rotation phase, but includes one that can indirectly calculate the relative rotation phase, such as a cam angle sensor.

  The ECU 40 includes an engine control unit 41 and a phase control unit 42. The engine control unit 41 automatically starts and stops the engine E, and the phase control unit 42 controls the relative rotation phase of the valve opening / closing timing control device 10 and the lock mechanism. A control configuration and control mode related to the ECU 40 will be described later.

[Valve opening / closing timing control device]
As shown in FIG. 1, the valve opening / closing timing control device 10 opens and closes an external rotor 11 as a drive side rotating member that rotates synchronously with the crankshaft 1 of the engine E, and an intake valve (not shown) in the combustion chamber of the engine E. And an internal rotor 12 as a driven side rotating member connected to the camshaft 3 to be connected by a connecting bolt 13. The internal rotor 12 is disposed coaxially with the axis X of the camshaft 3, and the internal rotor 12 and the external rotor 11 are configured to be relatively rotatable about the axis X.

  The outer rotor 11 and the inner rotor 12 are disposed on the same axis as the axis X, and the outer rotor 11 is fastened by fastening bolts 16 while being sandwiched between the front plate 14 and the rear plate 15. A timing sprocket 15 </ b> S is formed on the outer periphery of the rear plate 15. The central portion of the inner rotor 12 is disposed so as to pass through an opening formed in the central portion of the rear plate 15, and the intake-side camshaft 3 is connected to the end portion of the inner rotor 12 on the rear plate 15 side.

  As shown in FIG. 2, the outer rotor 11 has a plurality of (three in the present embodiment) first projecting portions 11 </ b> T projecting in the direction of the axis X (inner radial direction) integrally and in the circumferential direction. And formed with a gap. The first protrusion 11 </ b> T is close to the outer peripheral surface of the internal rotor 12. As a result, a space surrounded by the outer rotor 11 and the inner rotor 12 is partitioned by the first protrusion 11T, and a plurality of fluid pressure chambers C are formed. On the outer peripheral surface of the inner rotor 12 forming the fluid pressure chamber C, a plurality of (three in this embodiment) second projecting portions 12T projecting radially outwardly form a gap in the circumferential direction. Formed. The 2nd protrusion part 12T is an example of a partition part. The second protrusion 12 </ b> T is close to the inner peripheral surface of the external rotor 11. Thereby, each fluid pressure chamber C is partitioned by the second projecting portion 12T, and is divided into an advance chamber Ca and a retard chamber Cb in the rotation direction. Further, a seal member 17 is disposed at a tip portion of the first projecting portion 11T facing the internal rotor 12 so as to contact the inner rotor 12, and a tip of the second projecting portion 12T facing the external rotor 11 is disposed. A seal member 17 is disposed at the portion so as to abut against the external rotor 11. In the present embodiment, there are three fluid pressure chambers C, but the number is not limited to three. Needless to say, the number may be more or less than three.

  As shown in FIG. 1, the relative rotational phase between the external rotor 11 and the internal rotor 12 (hereinafter referred to as the relative rotational phase) extends from the state of the most retarded angle phase P2 across the internal rotor 12 and the front plate 14. A torsion spring 18 is provided for applying a biasing force until the rotational phase reaches the intermediate lock phase P1. The range in which the urging force of the torsion spring 18 acts may exceed the intermediate lock phase P1, or may not reach the intermediate lock phase P1.

  This valve opening / closing timing control device 10 winds the timing chain 8 across the output sprocket 7 provided on the crankshaft 1 of the engine E and the timing sprocket 15S of the external rotor 11, so that the external rotor 11 is connected to the crankshaft. 1 and rotate synchronously. Although not shown in the drawings, the front end of the camshaft 3 on the exhaust side is provided with a device having the same configuration as the valve opening / closing timing control device 10, and the rotational force is transmitted from the timing chain 8 to this device as well. Is done.

  As shown in FIG. 2, in the valve opening / closing timing control device 10, the external rotor 11 rotates in the driving rotation direction S by the driving force from the crankshaft 1. A direction in which the internal rotor 12 rotates in the same direction as the drive rotation direction S with respect to the external rotor 11 is referred to as an advance angle direction Sa, and a rotation direction in the opposite direction is referred to as a retard angle direction Sb. In this valve opening / closing timing control device 10, when the relative rotational phase is displaced in the advance angle direction Sa, the intake compression ratio is increased as the displacement amount is increased, and when the relative rotational phase is displaced in the retard direction Sb, the displacement amount is increased. The relationship between the crankshaft 1 and the camshaft 3 is set so as to reduce the intake compression ratio as it increases.

  The advance chamber Ca is supplied with the working oil as the working fluid, and thereby the relative rotation phase is displaced in the advance direction Sa. On the contrary, the retard chamber Cb is supplied with the working oil so that the relative rotation phase is retarded. It is displaced in the direction Sb. The relative rotational phase in a state where the second protrusion 12T has reached the moving end in the advance direction Sa (the rocking end centered on the axis X) is referred to as the most advanced angle phase P3, and the second protrusion 12T is delayed. The relative rotational phase in a state where it reaches the moving end on the corner side (the swing end about the axis X) is referred to as the most retarded phase P2. The most advanced phase P3 is a concept including not only the moving end of the second projecting portion 12T in the advance direction Sa but also the vicinity thereof. Similarly, the most retarded phase P2 is a concept including not only the moving end of the second projecting portion 12T in the retarded direction Sb but also the vicinity thereof.

  As shown in FIGS. 1 and 2, hydraulic oil is supplied to and discharged from the internal rotor 12 to an advance angle control oil passage 21 communicating with the advance angle chamber Ca and a first restriction mechanism L1 which is two restriction mechanisms described later. A first restriction release oil passage 23 and a second restriction release oil passage 24 for supplying and discharging hydraulic oil to and from the second restriction mechanism L2 are formed. The rear plate 15 is formed with a retard control oil passage 22 communicating with the retard chamber Cb. In this valve opening / closing timing control device 10, the lubricating oil stored in the oil pan 1A of the engine E is used as the working oil, and this working oil is supplied to the advance chamber Ca or the retard chamber Cb.

[Valve opening / closing timing control device: Regulatory mechanism]
The valve opening / closing timing control device 10 includes a restriction mechanism including a first restriction mechanism L1 and a second restriction mechanism L2. FIG. 3 is a sectional view showing the state of the most retarded phase P2 of the valve opening / closing timing control device 10. FIG. 4 is a cross-sectional view showing the state of the most advanced angle phase P3 of the valve opening / closing timing control device 10. FIG. 5 is a cross-sectional view illustrating the unlocked state of the valve opening / closing timing control device 10 at the intermediate lock phase P1. FIG. 6 is a perspective view showing the structure of the first regulating mechanism L1. The first restricting mechanism L1 has a function of restricting the relative rotation phase between the outer rotor 11 and the inner rotor 12 between the intermediate lock phase P1 and the most advanced angle phase P3, and a function of releasing the restriction. The second restriction mechanism L2 has a function of restricting the relative rotation phase between the intermediate lock phase P1 and the most retarded phase P2, and a function of releasing the restriction.

  The intermediate lock phase P1 is set to a predetermined phase between the most advanced angle phase P3 whose relative rotational phase is the operating end in the advance direction Sa and the most retarded phase P2 which is the operating end in the retard direction Sb. This is a relative rotation phase that can satisfactorily start the engine E in a state. The most retarded phase P2 is a relative rotational phase for cranking the engine E that has stopped in a high temperature state (the engine E in a state where time has not elapsed since the stop) with low torque.

  As shown in FIGS. 2-4, the 1st control mechanism L1 is comprised by the combination of the 1st control member 31 and the 1st control recessed part 35, and the 2nd control mechanism L2 is the 2nd control member 32 and the 2nd control. It is comprised by the combination of the recessed part 36. FIG.

  As shown in FIG. 6, the first restricting member 31 is configured by a plate-like member and is accommodated in a groove formed in the external rotor 11. The first restricting member 31 is supported so as to be movable in and out of the external rotor 11 so that it can approach and separate in the direction of the axis X in a posture parallel to the axis X. The first restricting member 31 protrudes in the direction of the internal rotor 12 by the urging force of the first spring 31S.

  As shown in FIGS. 2-6, the 1st control recessed part 35 is a groove shape along the outer periphery of the internal rotor 12, and the whole axial direction of an axis X, and is provided with two side surfaces 35a and 35a, and the bottom face 35b. Has been. The side surfaces 35a and 35a are formed such that planes extending inward in the radial direction intersect at the axis X. Therefore, the distance between the side surfaces 35a and 35a becomes longer toward the outer side in the radial direction. The groove width (circumferential length) of the first restriction recess 35 is sufficiently larger than the thickness of the first restriction member 31. The first restricting member 31 fitted in the first restricting recess 35 restricts the relative rotational phase between the intermediate lock phase P1 and the most advanced angle phase P3. In the intermediate lock phase P1, as shown in FIG. 35a abuts on the side surface 35a in the advance angle direction Sa and approaches the side surface 35a in the retard angle direction Sb in the most advanced angle phase P3 as shown in FIG. The first deregulation oil passage 23 is connected to the first restriction recess 35 at the center of the bottom surface 35b.

  A piston 37, which is an example of a pressure member, is attached to the first restriction recess 35 and the first restriction release oil passage 23. The piston 37 includes a pressurizing portion 37 a in the first restriction recess 35 and a sliding portion 37 c inserted into the first restriction release oil passage 23. The thickness of the pressurizing portion 37 a is about half of the depth of the first restricting recess 35. As shown in FIG. 6, when viewed along the radial direction of the inner rotor 12 in a state where the pressure portion 37 a is in contact with the bottom surface 35 b, the pressure surface 37 b of the pressure portion 37 a is the entire first restriction recess 35. As long as the first restricting member 31 faces or fits into the first restricting recess 35, the first restricting member 31 always contacts the pressure surface 37b. Of the surfaces of the first restricting member 31, the surface that contacts the pressure surface 37b is referred to as a pressure receiving surface 31a. There are gaps between the pressure portion 37 a and the first restriction recess 35 and between the sliding portion 37 c and the first restriction release oil passage 23. As shown in FIG. 6, when viewed along the radial direction of the internal rotor 12, the area of the pressure portion 37a is considerably larger than the area of the sliding portion 37c.

  As shown in FIG. 2, the piston 37 is moved from a state in which the pressurizing portion 37a is in contact with the bottom surface 35b (hereinafter, this state is referred to as “the piston 37 is retracted”), as shown in FIG. The inside of the first regulating recess 35 is slid in the radial direction until the pressure surface 37b reaches the outer peripheral surface of the internal rotor 12 (hereinafter, this state is referred to as “the state where the piston 37 protrudes”). In a state where the piston 37 protrudes, the pressurizing surface 37 b is flush with the outer peripheral surface of the inner rotor 12. The pressurization surface 37b is flush with the outer peripheral surface of the internal rotor 12. The pressurization surface 37b has the same curvature as that of the outer peripheral surface of the internal rotor 12, and the outer peripheral surface of the internal rotor 12 and the pressurization surface 37b are It is a state that forms a smoothly continuous curved surface. Hereinafter, the movement of the piston 37 toward the radially outer side of the internal rotor 12 is referred to as “the piston 37 is raised”, and the movement of the piston 37 toward the radially inner side is referred to as “the piston 37 is lowered”. Even if the pressure surface 37 b is flush with the outer peripheral surface of the internal rotor 12, the sliding portion 37 c has a length that does not come off from the first deregulation oil passage 23.

  As shown in FIG. 1, the second restricting member 32 has a pin shape in which two types of cylinders having different outer diameters are stacked concentrically. The second restricting member 32 is inserted into a sleeve 33 that is a two-stage stepped through hole that is opened in the inner rotor 12 in parallel to the axis X, and is supported so as to be freely retractable. Of the second restricting member 32, a cylinder having a large outer diameter is provided with a concentric and bottomed hole, and a second spring 32S is inserted into the hole. The second restricting member 32 protrudes toward the rear plate 15 by the urging force of the second spring 32S. The second deregulation oil passage 24 is connected to the sleeve 33 in the vicinity of the step formed on the side surface of the sleeve 33.

  As shown in FIGS. 2 to 4, the second restricting recess 36 is an ellipse that is slightly curved so that its center line forms an arc centered on the axis X on the inner rotor 12 side surface of the rear plate 15. It is the groove | channel formed in the shape. The depth of the second restriction recess 36 is about half that of the first restriction recess 35. The second restricting member 32 fitted in the second restricting recess 36 restricts the relative rotational phase between the intermediate lock phase P1 and the most retarded angle phase P2. In the intermediate lock phase P1, as shown in FIG. 2, it contacts the end of the side surface of the second restricting recess 36 in the advance direction Sa, and in the most retarded phase P2, as shown in FIG. 3, the retard direction Sb Abuts against the end of

  As shown in FIG. 2, in the intermediate lock phase P1, the first restricting member 31 fitted in the first restricting recess 35 abuts on the side surface 35a in the advance direction Sa and the pressure surface 37b and fits in the second restricting recess 36. The second restricting member 32 is in contact with the end of the side surface of the second restricting recess 36 in the advance direction Sa. That is, the first restricting mechanism L1 restricts displacement in the retarding direction Sb, and the second restricting mechanism L2 restricts displacement in the advance angle direction Sa. As described above, when both the first restriction mechanism L1 and the second restriction mechanism L2 are in the restricted state, the relative rotational phase can be changed from the intermediate lock phase P1 to the advance angle direction Sa and the retard angle direction Sb. It becomes a locked state that can not be. In the locked state, the piston 37 is in a retreated state.

  As shown in FIG. 3, in the most retarded angle phase P <b> 2, the first restricting member 31 is retracted from the first restricting recess 35, and the second restricting member 32 fitted into the second restricting recess 36 is the second restricting recess 36. It contacts the end of the side surface in the retarding direction Sb. At this time, the piston 37 is in a protruding state. As shown in FIG. 4, in the most advanced angle phase P3, the first restricting member 31 fitted in the first restricting recess 35 abuts on the pressure surface 37b while approaching the side surface 35a on the retarding direction Sb side, and the second The restricting member 32 is retracted from the second restricting recess 36. At this time, the piston 37 is in a retreated state, but when the engine E rotates at a high speed and the centrifugal force acting on the piston 37 exceeds the urging force of the first spring 31S, the piston 37 is in a protruding state. Even if the piston 37 protrudes, there is no problem because the relative rotational phase is fixed at the most advanced angle phase P3. In the most retarded angle phase P2 and the most advanced angle phase P3, the relative rotational phase is not locked by the first regulating mechanism L1 or the second regulating mechanism L2. The relative rotation phase is fixed by pressing the second protrusion 12T against the first protrusion 11T by the pressure of the hydraulic oil supplied to the retard chamber Cb or the advance chamber Ca.

[Valve opening / closing timing control device: Fluid control mechanism]
As shown in FIG. 1, the engine E includes a hydraulic pump 20 that sucks the lubricating oil in the oil pan 1 </ b> A with the driving force of the engine E and sends it out as hydraulic oil. In the internal combustion engine control system according to the present embodiment, an electromagnetically operated type that supplies hydraulic oil discharged from the hydraulic pump 20 by selectively selecting one of the advance chamber Ca and the retard chamber Cb of the valve timing control device 10. The phase control valve 25, the electromagnetically operated first release control valve 26 for supplying the hydraulic oil discharged from the hydraulic pump 20 to the first restriction release oil passage 23, and the hydraulic oil discharged from the hydraulic pump 20 to the second And an electromagnetically operated second release control valve 27 that is supplied to the restriction release oil passage 24. In particular, the valve opening / closing timing control device 10 includes the hydraulic pump 20, the phase control valve 25, the first release control valve 26, the second release control valve 27, and the respective oil passages through which hydraulic oil is supplied and discharged. The fluid control mechanism is configured.

  The phase control valve 25 is configured as an electromagnetic valve that can be switched between an advance position, a retard position, and a neutral position by a control signal. That is, at the advance angle position, the hydraulic oil discharged from the hydraulic pump 20 flows through the advance angle control oil passage 21 and is supplied to the advance angle chamber Ca, and the hydraulic oil in the retard angle chamber Cb is retarded. 22 is discharged. In the retard position, the hydraulic oil discharged from the hydraulic pump 20 flows through the retard control oil passage 22 and is supplied to the retard chamber Cb, and the hydraulic oil in the advance chamber Ca passes from the advance control oil passage 21. Discharged. In the neutral position, no hydraulic oil is supplied or discharged in either the advance chamber Ca or the retard chamber Cb. When the phase control valve 25 is energized with 100% duty, the phase control valve 25 is in the advanced position, and when the energization is cut off, it is in the retarded position.

  The first release control valve 26 and the second release control valve 27 are configured as electromagnetic valves that can be switched between an unlock position and a lock position by a control signal from the ECU 40. In the unlock position, the first release control valve 26 causes the hydraulic oil discharged from the hydraulic pump 20 to flow through the first restriction release oil passage 23 to apply hydraulic pressure to the end surface 37 d of the sliding portion 37 c of the piston 37. As a result, the piston 37 rises away from the bottom surface 35b of the first restriction recess 35 and enters a protruding state. In the locked position, the hydraulic oil is discharged from the first restriction release oil passage 23, respectively. As a result, the piston 37 descends and stops and enters a retreated state. The first release control valve 26 is in the locked position when the first release control valve 26 is energized, and is in the unlock position when the energization is cut off.

  In the unlock position, the second release control valve 27 is supplied with hydraulic oil discharged from the hydraulic pump 20 through the second restriction release oil passage 24 and supplied to the second restriction recess 36. At the locked position, as shown in FIG. 1, the hydraulic oil is discharged from the second restriction recess 36 through the second restriction release oil passage 24. When the second release control valve 27 is energized, the second release control valve 27 is in the locked position, and when the energization is cut off, the second release control valve 27 is in the unlock position.

  In the present embodiment, the first release control valve 26 is used for the restriction control of the first restriction mechanism L1, and the second release control valve 27 is used for the restriction control of the second restriction mechanism L2. Not limited. If each of the first restriction mechanism L1 and the second restriction mechanism L2 can be controlled independently, a single solenoid valve may be used, and two oil passages may be connected to the valve.

[Control configuration]
As shown in FIG. 1, signals from the shaft sensor 1 </ b> S, the ignition switch 43, the accelerator pedal sensor 44, the brake pedal sensor 45, and the phase detection sensor 46 are input to the ECU 40. The ECU 40 outputs signals for controlling the starter motor M, the fuel control device 5 and the ignition control device 6, and controls the phase control valve 25, the first release control valve 26 and the second release control valve 27. Output a signal.

  The ignition switch 43 is configured as a switch for starting the internal combustion engine control system, and starts the engine E by an ON operation and stops the engine E by an OFF operation. Further, when the ON operation is performed, the engine E can be automatically stopped and automatically started by the idling stop control.

  The accelerator pedal sensor 44 detects the amount of depression of an accelerator pedal (not shown), and the brake pedal sensor 45 detects depression of a brake pedal (not shown).

  The engine control unit 41 realizes start and stop of the engine E based on the operation of the ignition switch 43 and realizes idling stop control that temporarily stops the engine E when the engine E stops in an idling state. .

  The phase control unit 42 performs the intake valve timing control by the valve opening / closing timing control device 10 during operation of the engine E, and sets the relative rotation phase of the valve opening / closing timing control device 10 based on the situation when the engine E stops. The transition to the intermediate lock phase P1 by the first restriction mechanism L1 and the second restriction mechanism L2 is realized. Further, during the operation of the engine E, the relative rotation phase is changed to the advance direction Sa or the retard direction Sb based on the depression amount and depression amount of the accelerator pedal.

[Control mode: From intermediate lock phase to the most retarded phase]
Next, control when changing the relative rotational phase from the intermediate lock phase P1 to the most retarded phase P2 in the control mode of the internal combustion engine control system according to the present embodiment will be described with reference to the drawings. FIG. 7 shows a change in the operation of the first release control valve 26, the pressure of hydraulic oil (regulation release hydraulic pressure) acting on the end surface 37d of the sliding portion 37c from the restriction state to the restriction release state in the intermediate lock phase P1. 3 is a time chart showing the operation of the first regulating member 31.

  As shown in FIG. 2, at the intermediate lock phase P1, both the first release control valve 26 and the second release control valve 27 are in the locked position, and the first restriction member 31 is moved into the first restriction recess 35 and the second restriction The members 32 are fitted in the second restriction recesses 36, respectively. When the phase control unit 42 performs the retard control to change the relative rotation phase to the most retarded phase P2 from the locked state at the intermediate lock phase P1, the phase control unit 42 first unlocks the first release control valve 26. Control to switch to the lock position, that is, control to cut off the power supply to the first release control valve 26 is performed. After the first release control valve 26 is switched to the unlock position, the energization of the phase control valve 25 is cut off, and the phase control valve 25 is controlled to switch to the retard position. When the phase control valve 25 is switched to the retard position, the working oil is supplied to the retard chamber Cb through the retard control oil passage 22 and filled. However, even if the retarding chamber Cb is filled with the hydraulic oil, the relative rotation phase does not change because the first restricting member 31 remains fitted in the first restricting recess 35.

  When the first release control valve 26 is switched to the unlock position, the hydraulic oil flows through the first restriction release oil passage 23 and applies hydraulic pressure to the end surface 37d of the piston 37 in the retracted state. A force is transmitted to the pressure surface 37 b by the hydraulic pressure applied to the end surface 37 d, and the pressure surface 37 b applies a force to the pressure receiving surface 31 a of the first regulating member 31. When the oil pressure acting on the end surface 37d rises and the force that the pressure surface 37b acts on the pressure receiving surface 31a exceeds the urging force of the first spring 31S, the piston 37 starts to rise and the first regulating member 31 begins to retract. Then, as shown in FIG. 5, the pressure surface 37b rises until it is flush with the outer peripheral surface of the inner rotor 12, and the piston 37 protrudes, that is, the first restricting member 31 is completely retracted and the restriction is released. Then, the relative rotational phase is displaced in the retarding direction Sb by the retarding control already performed, and is fixed at the most retarded phase P2 as shown in FIG. As for the second restriction mechanism L2, as shown in FIGS. 2 and 3, the second restriction member 32 can be displaced in the retarding direction Sb while being fitted in the second restriction recess 36. Accordingly, the second release control valve 27 maintains the lock position.

  As shown in FIG. 7, as compared with the time chart of FIG. 12, the time T from when the first release control valve 26 is switched to the unlock position until the first restricting member 31 is retracted is shortened. Thus, if it is the structure which retracts the 1st control member 31 using the piston 37, in order to retract the 1st control member 31, it is not necessary to fill the 1st control recessed part 35 with hydraulic fluid. Accordingly, there is no time delay that the retraction of the first restriction member 31 is not completed until the hydraulic oil as shown in FIG. 12 is filled in the first restriction recess 35, and the retraction of the first restriction member 31 is completed in a short time. And the restriction can be released. Thereby, a rapid change of the relative rotational phase can be realized.

  As shown in FIG. 6, when viewed along the radial direction of the internal rotor 12, the area of the pressing surface 37b is considerably larger than the area of the end surface 37d of the sliding portion 37c. Therefore, the force acting on the end surface 37d by the hydraulic pressure increases in accordance with the area ratio between the end surface 37d and the pressing surface 37b, and a large force can be generated on the pressing surface 37b. Therefore, even if the hydraulic pressure applied to the end surface 37d is small, an increased force is applied to the pressure receiving surface 31a of the first regulating member 31, so that the retraction of the first regulating member 31 can be completed in a short time. it can. As a result, even if a small hydraulic pump 20 having a low discharge capacity is used, a rapid change in the relative rotational phase can be realized.

  In the present embodiment, the first restricting member 31 has a plate shape and the second restricting member 32 has a pin shape. However, the present invention is not limited to this. Both the first restricting member 31 and the second restricting member 32 may be plate-shaped, or both may be pin-shaped. Moreover, although the piston 37 was provided only in the 1st control mechanism L1, it is not restricted to this. You may provide only in the 2nd control mechanism L2, and may provide in both the 1st control mechanism L1 and the 2nd control mechanism L2 (refer 3rd Embodiment). The combination of the shape of the first restricting member 31 and the second restricting member 32 and the piston 37 can be selected as freely as possible.

2. Modification of First Embodiment Hereinafter, a modification of the first embodiment of the present invention will be described in detail with reference to the drawings. In the description of the following embodiment, the same reference numerals are given to the same components as those in the first embodiment, and the description of the same components will be omitted. In the present embodiment, the shapes of the piston 37 and the first restriction release oil passage 23 are different from those of the first embodiment, and the other structures are the same. FIG. 8 is a perspective view showing the shapes of the piston 37 and the first restriction release oil passage 23.

  As shown in FIG. 8, in the present embodiment, the sliding portion 37 c of the piston 37 has a rectangular parallelepiped shape that extends over the entire pressure portion 37 a along the axial direction of the internal rotor 12. Yes. For this reason, the portion of the first deregulation oil passage 23 where the sliding portion 37c is inserted has a larger cross-sectional area perpendicular to the flow direction of the hydraulic oil than the other portions, and the shape of the sliding portion 37c. It is a rectangular parallelepiped shape to match.

  Even in such a configuration, when the hydraulic oil flows through the first restriction release oil passage 23 and spreads over the entire end surface 37d of the piston 37 in the retracted state, and the hydraulic pressure is applied to the end surface 37d, the hydraulic pressure causes the pressurizing surface 37b. The pressure is applied to the pressure receiving surface 31 a of the first regulating member 31. When the oil pressure acting on the end surface 37d rises and the force that the pressure surface 37b acts on the pressure receiving surface 31a exceeds the urging force of the first spring 31S, the piston 37 starts to rise and the first regulating member 31 begins to retract. Then, the pressure surface 37b rises until it is flush with the outer peripheral surface of the internal rotor 12, and the piston 37 is in a protruding state.

  As described above, even if the hydraulic pressure applied to the end surface 37d is small, an increased force is applied to the pressure receiving surface 31a of the first regulating member 31, so that the retraction of the first regulating member 31 is completed in a short time. be able to. As a result, even if a small hydraulic pump 20 having a low discharge capacity is used, a rapid change in the relative rotational phase can be realized. Further, in this modified example, when viewed along the radial direction of the inner rotor 12, the area occupied by the sliding portion 37c with respect to the pressing portion 37a is larger than that of the first embodiment, so that the piston 37 is stabilized. And can be slid.

3. Second Embodiment Hereinafter, a second embodiment of the present invention will be described in detail with reference to the drawings. In the present embodiment, the shapes of the piston 37 and the first restriction release oil passage 23 are different from those of the first embodiment, and the other structures are the same. FIG. 9 is a perspective view showing the shapes of the piston 37 and the first restriction release oil passage 23.

  As shown in FIG. 9, in the present embodiment, the sliding portion 37 c of the piston 37 has an oblong column shape extending over the entire pressure portion 37 a along the circumferential direction of the internal rotor 12. . Corresponding to the sliding portion 37c, the portion into which the sliding portion 37c is inserted in the shape of the first deregulation oil passage 23 has an elongated cylindrical shape that matches the shape of the sliding portion 37c. . As described above, the distance between the side surfaces 35a, 35a of the first restricting recess 35 becomes longer toward the radially outer side of the inner rotor 12. Therefore, as shown in FIG. 5, the gap between the pressurizing portion 37a and the side surfaces 35a, 35a when the piston 37 is in the protruding state is compared with that when the piston 37 is in the retracted state as shown in FIG. growing. At this time, if a force is applied to the circumferential end of the piston 37, the piston 37 may tilt.

  However, as shown in FIG. 9, the sliding portion 37 c of the piston 37 has a long cylindrical shape extending over the entire pressure portion 37 a along the circumferential direction of the inner rotor 12. Even when the restricting member 31 protrudes to the end of the piston 37 such as near the intermediate lock phase P1 or near the most advanced angle phase P3, the sliding portion 37c receives the force applied from the first restricting member 31. Therefore, the piston 37 can slide without tilting.

4). Third Embodiment Hereinafter, a third embodiment of the present invention will be described in detail with reference to the drawings. In this embodiment, the point which applied piston 37 to the 2nd control mechanism L2 differs from 1st Embodiment, and the other structure is the same. FIG. 10 is a partially enlarged cross-sectional view showing the structure of the second restriction mechanism L2 of the valve opening / closing timing control device 10 according to the present embodiment. FIG. 11 is a perspective view showing the shapes of the piston 37 and the second restriction release oil passage 24.

  As shown in FIGS. 10 and 11, in the present embodiment, the second restriction release oil passage 24 is formed in the rear plate 15 and is connected to the bottom surface of the second restriction recess 36. For this reason, the thickness of the rear plate 15 in the axial center X direction is thicker than that of the other embodiments. The depth of the second restricting recess 36 is twice that of the second restricting recess 36 in the first embodiment. The second restricting member 32 has a columnar shape without a step, and is inserted into a sleeve 33 which is a bottomed opening formed from the side of the inner rotor 12 facing the rear plate 15. Between the bottom surface of the sleeve 33 and the side of the second restricting member 32 that does not face the rear plate 15, a second spring 32 </ b> S that applies an urging force to the second restricting member 32 is inserted.

  As shown in FIG. 11, a piston 37 is attached to the second restriction recess 36 and the second restriction release oil passage 24. There are gaps between the pressure portion 37 a of the piston 37 and the second restriction recess 36 and between the sliding portion 37 c and the second restriction release oil passage 24. The pressing surface 37b is not curved and is flat.

  When the relative rotational phase is displaced from the state of the intermediate lock phase P1 shown in FIG. 2 to the most advanced angle phase P3 shown in FIG. 4, it is necessary to complete the retraction of the second restricting member 32 in a short time. This is because the displacement of the relative rotational phase in the advance direction Sa occurs at the time of acceleration when the accelerator pedal is depressed, so that the actual acceleration is performed after the accelerator is depressed (the second release control valve 27 is switched to the unlock position). This is because the shorter the time to start (the relative rotation phase begins to change), the driver can experience the good response. Therefore, even if the second restricting mechanism L2 has a structure that moves in and out in the direction of the axis X, the piston 37 according to the present embodiment can be used to retract the second restricting member 32 in a short time. Can be completed, and a rapid change of the relative rotational phase can be realized.

  The valve opening / closing timing control device 10 according to the present invention may be applied to the exhaust-side valve opening / closing timing control device 10.

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

DESCRIPTION OF SYMBOLS 1 Crankshaft 3 Camshaft 10 Valve opening / closing timing control apparatus 11 External rotor (drive side rotating member)
12 Internal rotor (driven side rotating member)
12T Second protrusion (partition)
21 Lead angle control oil path 22 Delay angle control oil path 23 First restriction release oil path 24 Second restriction release oil path 31 First restriction member 32 Second restriction member 35 First restriction recess 36 Second restriction recess 37 Piston Pressure member)
37a Pressurizing portion 37b Pressurizing surface 37c Sliding portion E Engine (internal combustion engine)
C Fluid pressure chamber Ca Advance angle chamber Cb Delay angle chamber L1 First restriction mechanism L2 Second restriction mechanism P1 Intermediate lock phase P2 Most retarded phase P3 Most advanced angle phase

Claims (4)

A drive-side rotating member that rotates synchronously with the crankshaft of the internal combustion engine;
A driven-side rotating member that is arranged on the same axis as the driving-side rotating member and that rotates synchronously with a camshaft for opening and closing the valve of the internal combustion engine;
A fluid pressure chamber formed by the driving side rotating member and the driven side rotating member;
An advance chamber and a retard chamber formed by partitioning the fluid pressure chamber with a partition provided in at least one of the driving side rotating member and the driven side rotating member;
An advance angle control passage which is a passage of a working fluid supplied to and discharged from the advance angle chamber;
A retardation control passage which is a passage of the working fluid supplied to and discharged from the retardation chamber;
The regulating member provided on one of the driving side rotating member and the driven side rotating member, and the regulating recess provided on the other side of the driving side rotating member and the driven side rotating member, and placed on the regulating recess A pressure member having a formed portion, and the regulation member protrudes, fits into the regulation recess, and abuts against the pressure member, thereby changing a relative rotation phase of the driven side rotation member with respect to the drive side rotation member. The state in which the regulating member is regulated to a range from one of the most advanced angle phase and the most retarded angle phase to a predetermined phase between the most advanced angle phase and the most retarded angle phase, and the pressure applied by the pressure member And a regulation mechanism that can be switched to a state in which regulation is released by retreating from the regulation recess,
A restriction release passage that is connected to the restriction recess and through which the working fluid flows, and that is not in communication with any of the advance chamber, the retard chamber, the advance control passage, and the retard control passage; Prepared,
A valve opening / closing timing control device that pressurizes the restricting member by displacing the pressurizing member in a direction away from the bottom surface of the restricting recess by the pressure of the working fluid supplied from the restriction releasing passage.   The pressure member includes a pressure portion in the restriction recess and a sliding portion inserted in the restriction release passage, and an area of a pressure surface in contact with the restriction member in the pressure portion is The valve opening / closing timing control device according to claim 1, wherein the valve opening / closing timing control device is larger than a cross-sectional area perpendicular to a flow direction of the working fluid in the sliding portion.   When viewed along the flow direction of the working fluid in a state where the pressurizing portion and the bottom surface of the restricting recess are in contact with each other, there is a gap between the pressurizing portion and the restricting recess, When the pressure member is displaced until the pressure surface reaches the boundary between the driving side rotating member and the driven side rotating member, the pressure surface is the boundary on the other side of the driving side rotating member and the driven side rotating member. The valve opening / closing timing control device according to claim 2, which is flush with the surface.   The cross-sectional shape perpendicular to the flow direction of the working fluid in the sliding portion and the restriction release passage is the whole of the pressurizing portion along the other circumferential direction of the driving side rotating member and the driven side rotating member. The valve opening / closing timing control device according to claim 2 or 3, wherein the valve opening / closing timing control device has a shape extending over the entire area.

Images