JP2012067752A - Engine valve control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To hold a phase angle to a decided angle without consuming electric power after the phase angle is decided.SOLUTION: An engine valve control device is arranged at an outer cylinder 10 to which a drive force of a crankshaft is transmitted so as to be relatively turnable with respect to the outer cylinder, an intermediate member 14 is movably arranged at the external periphery of an inner cylinder 12 connected to a camshaft, balls 46, 48 are moved in mutual reverse directions in response to axial displacement associated with the movement of the intermediate member 14 in a process in which the intermediate member 14 is moved in the axial direction associated with the energization of a solenoid 74 or a solenoid 76, a phase between the outer cylinder 10 and the camshaft 2 is variably adjusted, the movement of the balls 46, 48 is stopped with respect to a torque input from the outer cylinder 10 or the camshaft 2 after the intermediate member 14 is set at an advance position or a retardation position associated with the non-energization of the solenoids 74, 76, and the valve control device of the engine is brought into a self-locked state.

Description

  The present invention relates to an engine valve control device that controls the opening / closing timing of an intake valve or an exhaust valve by changing the rotational phase of a camshaft that opens and closes an intake valve or an exhaust valve of the engine.

  As an apparatus for controlling the opening / closing timing of an intake valve or an exhaust valve of an engine, for example, a sprocket to which driving force of an engine crankshaft is transmitted and a camshaft constituting a valve operating mechanism rotate integrally. The sprocket and the camshaft rotate in synchronization with each other. However, when a braking force is applied to the rotating drum by the electromagnetic brake means, the rotating drum has a rotation delay with respect to the sprocket, and this rotation drum has a rotation delay. In conjunction with this, there has been proposed a phase variable device that changes the phase of the camshaft relative to the sprocket (see Patent Document 1). In this phase variable device, an oil passage provided in the camshaft, an oil reservoir provided radially inside the clutch case, and an inner peripheral wall of the clutch case are disposed in a relative sliding portion between the friction material of the clutch case and the rotary drum. Since the structure in which engine oil is introduced through an oil introduction notch provided at the edge is adopted, the relative sliding surfaces of the friction material and the rotating drum can be cooled.

JP 2002-371814 A (see pages 4 to 6, see FIGS. 1 to 4)

  In the phase varying device described in Patent Document 1, when changing the phase of the camshaft with respect to the sprocket body, the electromagnetic clutch resists the elastic force of the torsion coil spring (return spring) except for the initial position of the phase angle. The braking force must be applied to the rotating drum by driving, and the electric power accompanying the driving of the electromagnetic clutch is always consumed even when the phase angle is variable and after the phase angle is made variable (after the phase angle is determined). . In addition, a helical spline is formed on the intermediate member in order to move the intermediate member along the axial direction of the camshaft in accordance with the braking force acting on the rotating drum, and the helical gear meshing with the helical spline of the intermediate member is formed on the sprocket body. A spline is formed, and a helical spline that meshes with the helical spline of the intermediate member is formed in the inner cylinder, and a phase angle conversion mechanism that converts the axial movement distance of the intermediate member into a phase angle is adopted. The angle conversion mechanism becomes complicated and the cost increases.

  The present invention has been made in view of the above-mentioned problems of the prior art, and its purpose is to hold the phase angle at the determined phase angle without consuming electric power after the phase angle is determined. is there.

  In order to solve the above-described problem, in the valve control apparatus for an engine according to claim 1, the outer cylinder part to which the driving force of the crankshaft of the engine is transmitted and the inner cylinder side of the outer cylinder part are disposed so as to be relatively rotatable. An inner cylinder portion coaxially connected to a camshaft that opens and closes an intake valve or an exhaust valve of the engine, and an intermediate portion that is movably disposed along the axial direction of the inner cylinder portion on the outer periphery of the inner cylinder portion A member, a position control mechanism for controlling the position of the intermediate member in the axial direction according to the operating state of the engine, and between the outer cylinder portion and the camshaft according to the position of the intermediate member in the axial direction. A phase adjusting mechanism that variably adjusts the phase, wherein the phase adjusting mechanism is formed on the inner periphery of the outer cylinder portion in a direction intersecting with the axis and formed in parallel with each other. group The outer cylinder has an outer periphery facing the first lead groove group, intersecting the axis thereof, formed in a direction opposite to the first lead groove group and parallel to each other. The two lead groove groups, the first lead groove group and the second lead groove group are used as sliding paths or rolling paths, and are slidably or slidably inserted into the sliding paths or rolling paths. A plurality of sliding bodies or rolling elements, and a piece of the intermediate member that is slidably or rotatably inserted into a guide groove formed on a surface facing the sliding path or rolling path, A plurality of sliding bodies or rolling elements are fixed to the intermediate member so as to be slidable or rollable, and the piece receives an elastic force and is biased in a direction away from the intermediate member. The piece is regulated by contact with the outer cylinder part or the inner cylinder part, and the piece The crossing angle with the guide groove is set to be greater than 0 degree and equal to or less than the friction angle, and prevents transmission of the torque with respect to torque input from the outer cylinder part or the camshaft, In response to the axial displacement from the member, the axial displacement is converted into a circumferential displacement, and the circumferential displacement is a displacement having a different size depending on the position of the intermediate member in the axial direction, It was set as the structure formed by giving to the said outer cylinder part and the said inner cylinder part as a displacement of a reverse direction.

  (Operation) The phase adjustment mechanism converts the axial displacement into a circumferential displacement in response to the axial displacement from the intermediate member only when the phase between the outer cylinder portion and the camshaft is variably adjusted. This circumferential displacement is a displacement having a different size depending on the position of the intermediate member in the axial direction, and is applied to the outer tube portion and the inner tube portion as displacements in opposite directions, and at other times, that is, the outer tube After the phase between the outer cylinder part and the camshaft is determined, this torque transmission is prevented in response to torque input from the outer cylinder part or the camshaft, so the phase between the outer cylinder part and the camshaft is determined. After that, even if torque is input from the outer cylinder part or camshaft, the phase between the outer cylinder part and the camshaft can be maintained at the specified phase without consuming electric power, thereby reducing power consumption. Can do.

  Further, when the axial displacement from the intermediate member acts on the phase adjustment mechanism, only the elastic force acts on the piece, so the piece slides along the guide groove, and the intermediate member follows the axial direction of the inner cylinder portion. With the movement of the intermediate member and the sliding body or rolling element, the outer cylinder part and the inner cylinder part are circumferential displacements having different sizes depending on the position of the intermediate member in the axial direction, Circumferential displacements in opposite directions are applied to each other, the outer cylinder part and the inner cylinder part rotate in opposite directions with respect to the sliding body or the rolling element, and the phase between the outer cylinder part and the camshaft is advanced or It is adjusted to the retard side. When the intermediate member is set at the advanced angle position or the retarded angle position and the phase angle between the outer cylinder part and the camshaft is determined, the torque input from the outer cylinder part or the camshaft is When torque acts between the inner cylinder portions and torque is applied in the advance angle or retard angle direction, the piece is locked in the guide groove of the intermediate member due to frictional force, and its movement is prevented. At this time, since the outer cylinder part and the inner cylinder part cannot move relative to the intermediate member, even if torque acts between the outer cylinder part and the inner cylinder part, the outer cylinder part and the inner cylinder part do not operate and are in a self-holding state (self-locking state). State), and the phase between the outer cylinder portion and the camshaft can be maintained at a specified phase.

  In the valve control apparatus for an engine according to claim 2, the outer cylinder part to which the driving force of the crankshaft of the engine is transmitted and the inner cylinder side of the outer cylinder part are disposed so as to be relatively rotatable, and the intake air of the engine An inner cylinder portion coaxially connected to a camshaft for opening and closing a valve or an exhaust valve; an intermediate member disposed on the outer periphery of the inner cylinder portion so as to be movable along the axial direction of the inner cylinder portion; and the engine A position control mechanism for controlling the position of the intermediate member in the axial direction according to the operation state of the intermediate member, and variably adjusting the phase between the outer tube portion and the camshaft according to the position of the intermediate member in the axial direction. A phase adjustment mechanism that includes a piece and a spring inserted in series between the outer cylinder part and the inner cylinder part, and the intermediate member and the outer cylinder part or the inner cylinder part. Tube Are engaged with each other by a helical spline. The movement according to the elastic force of the spring is restricted by contact with the outer cylinder part or the inner cylinder part, and the intersection angle between the piece and the guide groove exceeds 0 degree and is less than the friction angle And is configured to prevent transmission of the torque in response to torque input from the outer cylinder portion or the camshaft, and to rotate the axial displacement in response to the axial displacement from the intermediate member. The circumferential displacement is applied to the outer tube portion and the inner tube portion as displacements of different sizes depending on the position of the intermediate member in the axial direction and in opposite directions. Tena It was constructed.

  (Operation) When the axial displacement from the intermediate member acts on the phase adjustment mechanism, only the elastic force acts on the piece, so the piece slides along the guide groove, and the intermediate member is the outer cylinder portion or the inner cylinder portion. And move along the axial direction of the inner cylinder part, and with the movement of the intermediate member and the rolling element, the size of the outer cylinder part and the inner cylinder part depends on the position of the intermediate member in the axial direction. Different circumferential displacements are imparted in opposite circumferential directions, and the outer cylinder part and the inner cylinder part rotate in opposite directions with respect to the intermediate member, and the phase between the outer cylinder part and the camshaft Is adjusted to the advance side or retard side. When the intermediate member is set at the advanced angle position or the retarded angle position and the phase angle between the outer cylinder part and the camshaft is determined, the torque input from the outer cylinder part or the camshaft is When torque acts between the inner cylinder portions and torque is applied in the advance angle or retard angle direction, the piece is locked in the guide groove of the intermediate member due to frictional force, and its movement is prevented. At this time, since the outer cylinder part and the inner cylinder part cannot move relative to the intermediate member, even if torque acts between the outer cylinder part and the inner cylinder part, the outer cylinder part and the inner cylinder part do not operate and are in a self-holding state (self-locking state). State), and the phase between the outer cylinder portion and the camshaft can be maintained at a specified phase.

  The engine valve control device according to claim 3 is the engine valve control device according to claim 1 or 2, wherein the position control mechanism is disposed around the inner tube portion so as to be rotatable with the inner tube portion. Based on the plurality of rotating drums and the electromagnetic force, at the time of advance, a braking force is applied to one of the plurality of rotary drums to decelerate the rotation with the inner cylinder portion, and at the time of retard An electromagnetic clutch that applies a braking force to the other rotating drum among the plurality of rotating drums to decelerate the rotation with the inner cylinder portion, and the inner peripheral side of each rotating drum is along the circumferential direction thereof Each of the slide lamps is engaged with one of a pair of positioning lamps formed along the circumferential direction on the outer peripheral side of the intermediate member.

  (Operation) In advance control, when each rotating drum rotates with the intermediate member, the electromagnetic clutch is energized to generate an electromagnetic force from the electromagnetic clutch and apply a braking force to one rotating drum. When the rotation of one rotating drum is decelerated, the intermediate member rotates together with the other rotating drum. At this time, since the positioning ramp moves along the slide ramp of the rotary drum, the intermediate member moves, for example, toward the camshaft along the axial direction of the inner cylinder portion. Thereafter, when the electromagnetic clutch is deenergized, one of the rotating drums rotates again, the movement of the intermediate member is stopped, and the intermediate member is positioned at an arbitrary advance position. On the other hand, when the intermediate member is in the advanced position, the electromagnetic clutch is energized, electromagnetic force is generated from the electromagnetic clutch, braking force is applied to the other rotating drum, and the rotation of the other rotating drum is decelerated. The intermediate member rotates together with one of the rotating drums. At this time, since the positioning lamp moves along the slide lamp of the rotary drum, the intermediate member moves along the axial direction of the inner cylinder portion, for example, in a direction away from the camshaft. Thereafter, when the electromagnetic clutch is deenergized, the other rotating drum rotates again, the movement of the intermediate member is stopped, and the intermediate member is positioned at an arbitrary retarded position. That is, the electromagnetic clutch is energized only when the intermediate member is moved to an arbitrary advance or retard position, and the electromagnetic clutch is de-energized at other times so that the intermediate member can be arbitrarily advanced or retarded. It can be set at a corner position, and power consumption can be reduced.

  The engine valve control device according to claim 4 is the engine valve control device according to claim 1 or 2, wherein the position control mechanism is disposed around the inner tube portion so as to be rotatable with the inner tube portion. Based on the plurality of rotating drums and the electromagnetic force, at the time of advance, a braking force is applied to one of the plurality of rotary drums to decelerate the rotation with the inner cylinder portion, and at the time of retard An electromagnetic clutch that applies a braking force to the other rotating drum among the plurality of rotating drums to decelerate the rotation with the inner cylinder portion, and the flange portion of the intermediate member includes the one rotating drum and the other rotating drum. A positive lead for guiding the intermediate member along the axial direction of the inner tube portion on a surface of each of the rotary drums facing the flange portion of the intermediate member. Reverse lead A threaded portion of a positive lead or a reverse lead is formed on the flange portion of the intermediate member, and the threaded portions of the positive lead or the threaded portions of the reverse lead are kept in mesh with each other. It became the composition which becomes.

  (Operation) In advance control, when each rotating drum rotates with the intermediate member, the electromagnetic clutch is energized to generate an electromagnetic force from the electromagnetic clutch and apply a braking force to one rotating drum. When the rotation of one rotating drum is decelerated, the intermediate member rotates together with the other rotating drum. At this time, there is a speed difference between the threaded part of one rotating drum, for example, the threaded part of the positive lead and the threaded part of the positive lead of the flange, and both are in a state of being able to rotate relative to each other. Is in a decelerated state. As a result, the intermediate member is relatively engaged with the screw portion of the positive lead of one rotary drum and the screw portion of the positive lead of the flange portion along the axial direction of the inner cylinder portion, for example, in the camshaft direction. Move to. Thereafter, when the electromagnetic clutch is deenergized, one of the rotating drums rotates again, the movement of the intermediate member is stopped, and the intermediate member is positioned at an arbitrary advance position.

  On the other hand, when the intermediate member is in the advanced position, the electromagnetic clutch is energized, electromagnetic force is generated from the electromagnetic clutch, braking force is applied to the other rotating drum, and the rotation of the other rotating drum is decelerated. The intermediate member rotates together with one of the rotating drums. At this time, there is a speed difference between the screw portion of the other rotating drum, for example, the screw portion of the reverse lead and the screw portion of the reverse lead of the flange portion, and both are in a state of being able to rotate relative to each other. Is in a decelerated state. As a result, the intermediate member is relatively engaged with the screw portion of the reverse lead of the other rotating drum and the screw portion of the reverse lead of the flange portion along the axial direction of the inner cylinder portion, for example, from the camshaft. Move away. Thereafter, when the electromagnetic clutch is deenergized, the other rotating drum rotates again, the movement of the intermediate member is stopped, and the intermediate member is positioned at an arbitrary retarded position. That is, the electromagnetic clutch is energized only when the intermediate member is moved to an arbitrary advance or retard position, and the electromagnetic clutch is de-energized at other times so that the intermediate member can be arbitrarily advanced or retarded. It can be set at a corner position, and power consumption can be reduced.

  The engine valve control device according to claim 5 is the engine valve control device according to claim 1 or 2, wherein the position control mechanism is disposed around the inner tube portion so as to be rotatable with the inner tube portion. Based on the plurality of rotating drums and the electromagnetic force, at the time of advance, a braking force is applied to one of the plurality of rotary drums to decelerate the rotation with the inner cylinder portion, and at the time of retard An electromagnetic clutch that applies a braking force to the other rotating drum among the plurality of rotating drums to decelerate the rotation with the inner cylinder portion, and the flange portion of the intermediate member includes the one rotating drum and the other rotating drum. A positive lead for guiding the intermediate member along the axial direction of the inner tube portion on a surface of each of the rotary drums facing the flange portion of the intermediate member. Reverse lead And a sliding body or rolling element having the groove of the positive lead or the reverse lead as a sliding path or a rolling path is slidably or slidably fixed to the flange portion of the intermediate member. .

  (Operation) In advance control, when each rotating drum rotates with the intermediate member, the electromagnetic clutch is energized to generate an electromagnetic force from the electromagnetic clutch and apply a braking force to one rotating drum. When the rotation of one rotating drum is decelerated, the intermediate member rotates together with the other rotating drum. At this time, a speed difference is generated between the sliding body or the rolling element and the groove, for example, the groove of the positive lead, the two can rotate relative to each other, and the one rotating drum is decelerated. As a result, the intermediate member is moved along the axial direction of the inner cylinder portion, for example, in the camshaft direction, by sliding or rolling the sliding body or rolling body along the groove of the positive lead of one rotary drum. Move to. Thereafter, when the electromagnetic clutch is deenergized, one of the rotating drums rotates again, the movement of the intermediate member is stopped, and the intermediate member is positioned at an arbitrary advance position.

  On the other hand, when the intermediate member is in the advanced position, the electromagnetic clutch is energized, electromagnetic force is generated from the electromagnetic clutch, braking force is applied to the other rotating drum, and the rotation of the other rotating drum is decelerated. The intermediate member rotates together with one of the rotating drums. At this time, a speed difference is generated between the sliding body or rolling element and the groove of the reverse lead, the two are in a state of being able to rotate relative to each other, and the other rotating drum is in a decelerated state. As a result, the intermediate member is relatively moved along the axial direction of the inner cylinder portion by, for example, sliding or rolling the sliding body or rolling body along the groove of the reverse lead of the other rotating drum. , Move away from the camshaft. Thereafter, when the electromagnetic clutch is deenergized, the other rotating drum rotates again, the movement of the intermediate member is stopped, and the intermediate member is positioned at an arbitrary retarded position. That is, the electromagnetic clutch is energized only when the intermediate member is moved to an arbitrary advance or retard position, and the electromagnetic clutch is de-energized at other times so that the intermediate member can be arbitrarily advanced or retarded. It can be set at a corner position, and power consumption can be reduced.

  As is apparent from the above description, according to the engine valve control apparatus of the first aspect, after the phase between the outer cylinder portion and the camshaft is determined, torque is input from the outer cylinder portion or the camshaft. However, the phase between the outer cylinder portion and the camshaft can be held at a specified phase without consuming power, and power consumption can be reduced. Further, in response to torque input from the intermediate member, the phase between the outer cylinder part and the cam shaft is variably adjusted, and when the phase angle between the outer cylinder part and the cam shaft is determined, the outer cylinder part or the cam shaft In response to the torque input from, the self-holding state is established, and the phase between the outer cylinder portion and the camshaft can be held at a specified phase.

  According to the engine valve control device of the second aspect, in response to torque input from the intermediate member, the phase between the outer cylinder portion and the camshaft is variably adjusted, and the phase angle between the outer cylinder portion and the camshaft is adjusted. Is determined, it becomes a self-holding state with respect to torque input from the outer cylinder part or the camshaft, and the phase between the outer cylinder part and the camshaft can be held at a specified phase.

  According to the engine valve control apparatus of the third aspect, the electromagnetic clutch is energized only when the intermediate member is moved to an arbitrary advance or retard position, and otherwise the electromagnetic clutch is de-energized. Thus, the intermediate member can be set at an arbitrary advance angle or retard angle position, and power consumption can be reduced.

According to the engine valve control apparatus of the fourth aspect, the electromagnetic clutch is energized only when the intermediate member is moved to an arbitrary advance or retard position, and otherwise the electromagnetic clutch is de-energized. Thus, the intermediate member can be set at an arbitrary advance angle or retard angle position, and power consumption can be reduced.
According to the engine valve control device of the fifth aspect, the electromagnetic clutch is energized only when the intermediate member is moved to an arbitrary advance or retard position, and otherwise the electromagnetic clutch is de-energized. Thus, the intermediate member can be set at an arbitrary advance angle or retard angle position, and power consumption can be reduced.

1 is a longitudinal sectional view of an engine valve control apparatus showing a first embodiment of the present invention. 1 is a front view of an engine valve control apparatus according to a first embodiment of the present invention. It is a rear view of an outer cylinder part. It is sectional drawing of an outer cylinder part. It is an expanded view of an outer cylinder part inner peripheral side. It is a perspective view of an inner cylinder part. It is sectional drawing of an inner cylinder part. It is a rear view of an inner cylinder part. It is an expanded view of an inner cylinder part outer peripheral side. It is a perspective view of an intermediate member. It is sectional drawing of an intermediate member. It is an expanded view of the intermediate member outer peripheral side. It is a perspective view of a rotating drum. It is sectional drawing of a rotating drum. It is an expanded view of the rotating drum inner peripheral side. It is a perspective view of another rotating drum. It is sectional drawing of another rotating drum. FIG. 6 is a development view of the inner peripheral side of another rotating drum. It is an expanded view for demonstrating the relationship between an intermediate member and a pair of rotating drum. (A) is an expanded view for demonstrating the relationship between six balls and an inner cylinder part, (b) is an expanded view for demonstrating the relationship between six balls and an outer cylinder part. It is a principal part expanded sectional view for demonstrating the relationship between a piece and an intermediate member. It is a principal part enlarged front view for demonstrating the relationship between a piece and an intermediate member. It is a schematic diagram for demonstrating the relationship between a ball | bowl and a piece when advance angle or retard angle control is not performed. It is a schematic diagram for demonstrating the relationship between a ball | bowl and a piece when advance angle or retard angle control is performed. It is a principal part expanded view of the phase adjustment mechanism which shows 2nd Example of this invention. It is a principal part expanded view of the phase adjustment mechanism which shows 3rd Example of this invention. It is sectional drawing of the position control mechanism which shows 4th Example of this invention. It is sectional drawing of the position control mechanism which shows 5th Example of this invention. It is a longitudinal cross-sectional view of the valve control apparatus of the engine which shows 6th Example of this invention. It is a longitudinal cross-sectional view of the valve control apparatus of the engine which shows 7th Example of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view of an engine valve control apparatus according to a first embodiment of the present invention, FIG. 2 is a front view of the engine valve control apparatus according to the first embodiment of the present invention, and FIG. FIG. 4 is a cross-sectional view of the outer tube portion, FIG. 5 is a development view of the outer periphery of the outer tube portion, FIG. 6 is a perspective view of the inner tube portion, and FIG. 7 is a cross section of the inner tube portion. 8 is a rear view of the inner cylinder portion, FIG. 9 is a development view of the outer peripheral side of the inner cylinder portion, FIG. 10 is a perspective view of the intermediate member, FIG. 11 is a sectional view of the intermediate member, and FIG. FIG. 13 is a perspective view of the rotating drum, FIG. 14 is a sectional view of the rotating drum, FIG. 15 is a developed view of the inner peripheral side of the rotating drum, and FIG. 16 is a drawing of another rotating drum. FIG. 17 is a cross-sectional view of another rotating drum, FIG. 18 is a development view of the inner peripheral side of another rotating drum, and FIG. 19 is for explaining the relationship between the intermediate member and the pair of rotating drums. FIG. 20A is a development view for explaining the relationship between the six balls and the inner cylinder portion, and FIG. 20B is a diagram for explaining the relationship between the six balls and the outer cylinder portion. FIG. 21 is an enlarged view of a main part for explaining the relationship between the piece and the intermediate member, FIG. 22 is an enlarged rear view of the main part for explaining the relation between the piece and the intermediate member, and FIG. FIG. 24 is a schematic diagram for explaining the relationship between the ball and the piece when the advance or retard control is not executed, and FIG. 24 explains the relationship between the ball and the piece when the advance or retard control is executed. FIG. 25 is a development view of a main part of a phase adjustment mechanism showing a second embodiment of the present invention, and FIG. 26 is a development view of a main part of the phase adjustment mechanism showing a third embodiment of the invention. 27 is a sectional view of a position control mechanism showing a fourth embodiment of the present invention, and FIG. 28 is a diagram showing a fifth embodiment of the present invention. FIG. 29 is a longitudinal sectional view of an engine valve control apparatus showing a sixth embodiment of the present invention, and FIG. 30 is a longitudinal sectional view of an engine valve control apparatus showing a sixth embodiment of the present invention. FIG.

  In these drawings, the engine valve control device according to the present invention is used in an engine oil atmosphere in a form assembled to an automobile engine, for example, and the intake and exhaust valves open and close in synchronization with the rotation of the crankshaft. As shown in FIG. 1, the rotation of the crankshaft is transmitted to the camshaft, and the opening / closing timing of the intake valve or exhaust valve of the engine is changed according to the operating state such as the engine load and the rotational speed. As described above, the annular outer cylinder portion 10 to which the driving force of the crankshaft of the engine is transmitted is disposed on the inner peripheral side of the outer cylinder portion 10 so as to be coaxial with the outer cylinder portion 10 and relatively rotatable with respect to the outer cylinder portion 10. And an annular inner cylinder portion 12 coaxially connected to the camshaft 2 for opening and closing the intake valve or exhaust valve of the engine, and formed in an annular shape The intermediate member 14 that is movably disposed along the axial direction of the inner cylinder portion 12 on the outer periphery of the inner cylinder portion 12, and the position control that controls the position of the intermediate member 14 in the axial direction according to the operating state of the engine A mechanism 16 and a phase adjustment mechanism 18 that variably adjusts the phase between the outer cylinder portion 10 and the camshaft 2 in accordance with the position of the intermediate member 14 in the axial direction are provided. One end in the axial direction of the camshaft 2 is fitted to the inner peripheral side of the inner cylinder portion 12, and a cam bolt 19 is fastened to one end in the axial direction of the camshaft 2. The cam bolt 19 is fixed to one end of the inner cylinder portion 12 in the axial direction via a bearing 20 and a stopper 21. The bearing 20 and the stopper 21 are fixed to the outer peripheral surface on one end side in the axial direction of the inner cylinder portion 12, and the flange portion 22 formed integrally with the outer ring of the bearing 20 has a substantially disc shape as shown in FIG. The holder 23 formed in the above is rotatably arranged. The holder 23 is provided with three protrusions 23a arranged at a 120 degree pitch on the outer peripheral side thereof, and each protrusion 23a is inserted into a recess of a cover (not shown) fixed to the engine body. Is prevented from rotating in the circumferential direction.

  As shown in FIGS. 3 to 5, the outer cylinder portion 10 has a plurality of sprockets 24 arranged on the outer peripheral side as a cylinder on the drive shaft side, and the driving force of the crankshaft of the engine is chained to the sprocket 24. Is transmitted in synchronization with the crankshaft, and the driving force associated with this rotation is transmitted to the inner cylinder portion 12 via the phase adjustment mechanism 18. A semicircular lead groove (ball groove) 26 is formed as an element of the phase adjusting mechanism 18 on the inner peripheral side of the outer cylindrical portion 10 along the direction intersecting the axis. . In addition, the small diameter outer cylinder part 28 is arranged in parallel adjacent to the outer cylinder part 10, and the small diameter outer cylinder part 28 is arrange | positioned at the outer periphery of the inner cylinder part 12, and is fixed to the outer cylinder part 10 with the volt | bolt 30. Yes. The small diameter outer cylinder portion 28 has a sprocket 32 formed on the outer peripheral side thereof, and rotates in synchronization with the crankshaft when the driving force of the crankshaft of the engine is transmitted to the sprocket 32 via the chain. It is like that.

  As shown in FIGS. 6 to 9, the inner cylinder portion 12 is configured as a cylinder on the camshaft 2 side, and large diameter portions 34 and 36 are formed on the outer peripheral side of the inner cylinder portion 12. A cam bolt insertion hole 38 and a cam shaft fitting hole 40 are formed on the side. In the large-diameter portion 36, as one element of the phase adjusting mechanism 18, semicircular lead grooves (ball grooves) 42 and 44 that intersect with each other are formed over the entire circumference along the direction intersecting the axis. ing. The lead grooves 42 and 44 together with the lead groove 26 of the outer cylinder portion 10 constitute a rolling path or a sliding path for the balls 46 and 48, and between the lead grooves 42 and 44 and the lead groove 26. The three balls 46 are inserted on the clamp pulley CP side (the head side of the cam bolt 19), and the three balls 48 are inserted on the head H side (the camshaft 2 side) (see FIG. 1). . When the intermediate member 14 moves to the advance position or the retard position along the axial direction of the inner cylinder portion 12 as a sliding body or a rolling body that is an element of the phase adjustment mechanism 18, the balls 46 and 48 are In response to the axial displacement from the intermediate member 14 accompanying the movement, the lead grooves 42 and 44 and the lead groove 26 move in opposite directions.

  As shown in FIGS. 10 to 12, the intermediate member 14 is configured as a cylinder having a small diameter portion 50 and a large diameter portion 52, and the shaft of the inner cylinder portion 12 is disposed on the large diameter portions 34 and 36 of the inner cylinder portion 12. It is arranged to be movable along the direction. In the small diameter portion 50 of the intermediate member 14, three guide grooves (grooves for guiding the piece 82 holding the ball 48) 54 and three fixing holes (holes for fixing the ball 46) 56 are formed. In the large-diameter portion 52, lamps (positioning lamps) 58 and 60 having different phases in the circumferential direction are formed as convex portions over the entire circumference. Although all the guide grooves 54 are twisted in the same direction in FIG. 12, a part of the guide grooves 54 can be twisted in the reverse direction in order to cancel the reaction force in the rotation direction. For example, by twisting one of the guide grooves 54 in the opposite direction to the other two, the force (backlash) in the rotational direction generated by the piece 82 moving in the guide groove 54 can be canceled. The ramp 58 is formed in a shape in which the inclination gradually changes every 180 degrees, and the ramp 60 is similarly formed in a shape in which the inclination gradually changes every 180 degrees. However, in this configuration, the phases of the lamp 58 and the lamp 60 are shifted by 90 degrees.

  The position control mechanism 16 for controlling the position of the intermediate member 14 includes rotating drums 62 and 64 and electromagnetic clutches 66 and 68 formed in an annular shape. The electromagnetic clutches 66 and 68 include braking plates 70, 72, Solenoids 74 and 76 are provided, and each solenoid 74 and 76 is connected to a control circuit (not shown) that detects the operating state of the engine and outputs a control signal or the like (see FIGS. 1 and 2).

  As shown in FIGS. 13 to 18, the rotating drums 62 and 64 are formed in a cylindrical shape and arranged on the outer peripheral side of the inner cylinder portion 12, and when receiving no braking force from the braking plates 70 and 72, The movement is made freely, and the movement of the inner cylinder part 12 in the axial direction is blocked by the outer cylinder part 10 or the stopper 21. On the inner peripheral side of the rotating drum 62, as shown in FIGS. 13 to 15, two lamps (sliding lamps) 78 whose positions in the axial direction gradually change are formed as recesses at a pitch of 180 degrees. The ramp 78 is adapted to engage with the ramp 58 of the intermediate member 14. On the inner peripheral side of the rotating drum 64, as shown in FIGS. 16 to 18, two lamps (sliding lamps) 80 whose positions in the axial direction gradually change are formed as recesses at a pitch of 180 degrees. The lamp 80 is adapted to engage with the lamp 60 of the intermediate member 14.

  On the other hand, the brake plates 70 and 72 are rotatably arranged around the rotating drums 62 and 64 with the bolt 71 as a fulcrum (see FIG. 2), and when the solenoids 74 and 76 are energized, respectively. The bolt 71 is turned around a fulcrum to apply a braking force to the rotating drums 62 and 64 to decelerate the rotation of the rotating drums 62 and 64. In this case, the solenoid 74 is energized during the advance angle control, and the solenoid 76 is energized during the retard angle control. By energizing the solenoid 74 or the solenoid 76, the intermediate member 14 is moved to the advance position or the retard position. It can be moved to the corner position.

  Specifically, as shown in FIG. 19, when the solenoid 74 and the solenoid 76 are in a non-energized state, the rotating drums 62 and 64 rotate together with the intermediate member 14, for example, when controlling the opening / closing timing of the intake valve, During idling, the intermediate member 14 is at the most retarded position. Thereafter, in order to control the advance angle, only the solenoid 74 is energized when the rotary drums 62 and 64 are rotating together with the intermediate member 14, and a braking force is applied from the brake plate 70 to the rotary drum 62. When the rotation of 62 is decelerated, the intermediate member 14 rotates together with the rotating drum 64. At this time, the intermediate member 14 moves to the head H side (camshaft 2 side) along the axial direction of the inner cylinder portion 12 because the ramp 58 moves along the ramp 78 of the rotary drum 62. When the solenoid 74 is energized, the intermediate member 14 moves to the most advanced position. When the intermediate member 14 is moved from the most retarded position to the most advanced position, the solenoid 74 is deenergized at an arbitrary timing, so that the intermediate member 14 is positioned at an arbitrary advanced position.

  On the other hand, when the retard control is performed when the intermediate member 14 is at the most advanced angle position, only the solenoid 76 is energized and rotated from the brake plate 72 when the rotary drums 62 and 64 are rotating together with the intermediate member 14. When a braking force is applied to the drum 64 to decelerate the rotation of the rotary drum 64, the intermediate member 14 rotates together with the rotary drum 62. At this time, the intermediate member 14 moves to the crank pulley CP side (the head side of the cam bolt 19) along the axial direction of the inner cylinder portion 12 because the ramp 60 moves along the ramp 80 of the rotary drum 64. When the solenoid 76 is energized, the intermediate member 14 moves to the most retarded position. If the solenoid 76 is deenergized at an arbitrary timing in the process in which the intermediate member 14 moves from the most advanced position to the most retarded position, the intermediate member 14 is positioned at an arbitrary retarded position.

  When the intermediate member 14 is at an arbitrary advance angle position or retard angle position, the intermediate member 14 rotates together with the rotary drums 62 and 64. Thereafter, when the advance angle control is performed, the solenoid 74 is energized. The intermediate member 14 can be positioned at another advance position, and when the retard control is performed, the intermediate member 14 can be positioned at another retard position by energizing the solenoid 76.

  Here, for example, when the intermediate member 14 is at the most retarded position, as shown in FIGS. 20A and 20B, the three balls 46 are fixed in the fixing holes 56 of the intermediate member 14. Is located on the crank pulley CP side (the head side of the cam bolt 19), and the three balls 48 are located on the head H side (camshaft 2 side) while being held by the piece 82 shown in FIGS. is doing. The lead groove 26 is represented by six lead grooves 26a to 26f, the lead groove 42 is represented by three lead grooves 42a, 42c, and 42e, and the lead groove 44 is represented by three lead grooves 44b, 44d, and 44f. The lead grooves 42a, 42c, 42e correspond to the lead grooves 26a, 26c, 26e, and the lead grooves 44b, 44d, 44f correspond to the lead grooves 26b, 26d, 26f.

  Here, the axial directions of the inner cylinder portion 12 and the outer cylinder portion 10 are X, the inner cylinder portion 12 rotates in the arrow Y direction, and the outer cylinder portion 10 rotates in the arrow Z direction. As the advance angle control is performed, as the intermediate member 14 moves to the head H side, the three balls 46 also move from the crank pulley CP side to the head H side so that the lead grooves 26b and 44b, the lead grooves 26d and 44d, The lead moves along the lead grooves 26f and 44f up to a position indicated by a broken line. On the other hand, the three balls 48 held by the piece 82 are broken at maximum along the lead grooves 26a, 42a, the lead grooves 26c, 42c and the lead grooves 26e, 42e from the head H side to the crank pulley CP side. Move to the indicated position. At this time, in accordance with the movement of the intermediate member 14 and the balls 46 and 48, the outer cylinder portion 10 and the inner cylinder portion 12 are displaced in the circumferential direction opposite to each other, and the intermediate member 14 is moved to the position in the axial direction. Accordingly, circumferential displacements of different sizes are applied, and the outer cylinder portion 10 rotates counterclockwise as viewed from the crank pulley CP side with respect to the balls 46 and 48, and the inner cylinder portion 12 48, it rotates clockwise as viewed from the crank pulley CP side, and the phase between the outer cylinder portion 10 and the camshaft 2 is adjusted to the advance side.

  On the other hand, when the intermediate member 14 is at the advanced position indicated by the broken line, the three balls 46 fixed to the fixing hole 56 of the intermediate member 14 are more than when the intermediate member 14 is at the most retarded position. The three balls 48 positioned on the head H side (camshaft 2 side) and held by the piece 82 are closer to the crank pulley CP side (head of the cam bolt 19) than when the intermediate member 14 is at the most retarded position. Part side). When the retard control is performed from this state, as the intermediate member 14 moves from the head H side to the crank pulley CP side, the three balls 46 also move from the head H side to the crank pulley CP side. The three balls 48 held by the piece 82 move from the crank pulley CP side to the head H side. At this time, in accordance with the movement of the intermediate member 14 and the balls 46 and 48, the outer cylinder portion 10 and the inner cylinder portion 12 are displaced in the circumferential direction opposite to each other, and the intermediate member 14 is moved to the position in the axial direction. Accordingly, circumferential displacements having different sizes are applied, and the outer cylinder portion 10 rotates clockwise with respect to the balls 46 and 48 as viewed from the crank pulley CP side, and the inner cylinder portion 12 rotates with the balls 46 and 48. On the other hand, it rotates counterclockwise when viewed from the crank pulley CP side, and the phase between the outer cylinder portion 10 and the camshaft 2 is adjusted to the retard side.

  Here, since the three balls 46 are inserted into the holes 56 of the intermediate member 14 and are fixed to the intermediate member 14, the three balls 46 move together with the intermediate member 14. On the other hand, since the three balls 48 are inserted into the groove 84 of the piece 82 inserted into the guide groove 54 of the intermediate member 14, the three balls 48 move together with the piece 82. As shown in FIGS. 21 and 22, the guide groove 54 of the intermediate member 14 is inclined with respect to the axis of the intermediate member 14, and the straight portion 86 of the groove 84 of the piece 82 is the axis of the intermediate member 14. Inclined with respect to direction. The extension line of the guide groove 54 of the intermediate member 14 and the extension line of the straight portion 86 of the piece 82 intersect at an intersection angle θ, and the intersection angle θ is set to an angle that is less than the friction angle and greater than 0 degrees.

  For this reason, even when the intermediate member 14 is at an arbitrary advance position or retard position and the advance control or retard control is not performed, even when torque is input from the outer cylinder portion 10 or the camshaft 2. As shown in FIG. 23, this torque input is generated in a piece 82 inserted into a guide groove 54 inclined with respect to the axis L of the camshaft 2 (an axis parallel to the axis of the intermediate member 14) L. A force F perpendicular to the straight portion 86 of the piece 82 is generated on the ball 48. A force Fa parallel to the force F is generated as a reaction force of the piece 82 against the intermediate member 14. At this time, when the force F is decomposed into a component Fa parallel to the force F and a component Fb orthogonal to the guide groove 54, an angle (θ1) formed by the component Fa parallel to the force F and the component Fb orthogonal to the guide groove 54 is obtained. − (− Θ2)) is the same as the intersection angle θ between the extension line of the guide groove 54 and the extension line of the straight portion 86 of the piece 82 (θ = θ1 − (− θ2)). The frictional force Fc acting on the guide groove 54 is the same as the component Fd of the force F parallel to the guide groove 54, and the piece 82 cannot move. Accordingly, since the ball 48 cannot move, the ball 48 cannot move, and the intermediate member 14 is held at an arbitrary advance angle position or retard angle position.

  On the other hand, when the intermediate member 14 is at an arbitrary advance angle position or retard angle position, advance angle control or retard angle control is performed, and when the intermediate member 14 is displaced in the axial direction, this axial displacement is 24, it acts on the piece 82 as a force F that lowers the piece 82 downward. At this time, due to the movement of the piece 82 (movement in the direction of arrow B), the linear portion 86 of the piece 82 guides the ball 48 to move in the direction opposite to the movement of the intermediate member 14 (direction of arrow C). As a result, the intermediate member 14 is positioned at an arbitrary advance angle position or retard angle position by the advance angle control or the retard angle control.

  According to the present embodiment, in the process in which the intermediate member 14 moves to the advanced position or the retarded position as the solenoid 74 or the solenoid 76 is energized, in response to the axial displacement accompanying the movement of the intermediate member 14, The balls 46 and 48 move in opposite directions, and are circumferential displacements in opposite directions with respect to the outer cylinder portion 10 and the inner cylinder portion 12, and differ in size depending on the position of the intermediate member 14 in the axial direction. A circumferential displacement is applied, and the phase between the outer cylinder portion 10 and the camshaft 2 is variably adjusted.

  On the other hand, when the intermediate member 14 is set to the advanced position or the retarded position in accordance with the deenergization of the solenoid 74 and the solenoid 76 and the phase angle between the outer cylinder 10 and the camshaft 2 is determined, the outer cylinder 10 or the torque input from the camshaft 2, the movement of the balls 46 and 48 is stopped and the transmission of the torque input is prevented, so that the drive shaft side including the outer cylinder portion 10 and the inner cylinder portion 12 are included. The driven shaft side is irreversible in torque transmission and is in a self-holding state (self-locking state).

  That is, after the phase angle between the outer cylinder portion 10 and the camshaft 2 is determined, even if a reaction force is received from the camshaft 2, the power shaft side including the outer cylinder portion 10 and the inner side are not consumed even if a reaction force is received. The driven shaft side including the cylindrical portion 12 is in a self-holding state (self-locking state), the phase angle can be held at the determined phase angle, and power consumption can be reduced.

  Further, it is not necessary to move the intermediate member 14 against the elastic force of the return spring, and the intermediate member 14 can be moved only by energizing the solenoid 74 or the solenoid 76, so that the return spring is used. As a result, power consumption can be reduced.

  Furthermore, since the lamps 58 and 60 are formed on the intermediate member 14 so that the phases in the circumferential direction are different from each other, the axis of the intermediate member 14 as a whole is larger than the case where the phases in the circumferential direction are the same. The length in the direction can be shortened, and the length in the axial direction of the entire apparatus can be shortened.

  Next, a second embodiment of the present invention will be described with reference to FIG. In the present embodiment, the lead groove serving as the ball sliding path or rolling path has a parallel groove structure, and other configurations are the same as those of the first embodiment. Specifically, the phase adjustment mechanism 18A is a non-reciprocal torque transmission mechanism, and is formed by twisting the inner periphery of the outer cylinder portion 10 in a direction intersecting the axis thereof, and formed in parallel to each other. A group (ball groove group) 90 and a region of the outer periphery of the inner cylindrical portion 12 facing the first lead groove group, intersecting the axis thereof, twisted in the opposite direction to the first lead groove group 90, and The second lead groove group (ball groove group) 92 formed in parallel to each other, the first lead groove group 90, and the second lead groove group 92 as the slide paths or rolling paths are used as the slide paths or rolling paths. The six balls 46, which are slidably or slidably inserted in the movement path, and the guide groove 54 formed on the surface of the intermediate member 14 facing the sliding path or the rolling path slide or roll. It is configured to include a piece 94 inserted freely.

  The first lead groove group 90 is composed of six lead grooves 90a to 90f parallel to each other, and the second lead groove group 92 is parallel to each other and twisted in the opposite direction to the lead grooves 90a to 90f. The two lead grooves 92a to 92f are formed as parallel grooves.

  Each ball 46 is slidably or slidably fixed in the fixing hole 56 of the intermediate member 14 as a slidable or rolling element. Each piece 94 is formed in a substantially rectangular shape and is slidably inserted into the guide groove 54, and is urged in a direction away from the intermediate member 14 by receiving an elastic force from a spring 96 mounted in the guide groove 54. The movement due to the elastic force of the spring 96 is restricted by contact with the outer cylinder part 10 or the inner cylinder part 12. The intersection angle θ between the piece 94 and the guide groove 54 (the angle θ formed between the straight line along the guide groove 54 and the axis of the intermediate member 14) is set to be greater than 0 degree and equal to or less than the friction angle.

  The phase adjustment mechanism 18A is a non-reciprocal torque transmission mechanism that twists in opposite directions when torque acts between the outer cylinder part 10 and the inner cylinder part 12, but the intermediate member 14 and the outer cylinder part 10 or the inner cylinder part. The intermediate member 14 tends to move along its axial direction, whereas the outer cylinder portion 10 and the inner cylinder portion 12 try to move in the rotational direction. At this time, the intermediate member 14 tries to co-rotate with the outer cylinder part 10 or the inner cylinder part 12 due to friction between the piece 94 and the outer cylinder part 10 or the inner cylinder part 12, The member 14 tends to be moved in the axial direction opposite to the direction in which the torque is applied (the direction in which the torque acts).

  For example, when the solenoid 74 and the solenoid 76 are in a non-energized state, the intermediate member 14 is set to the advanced angle position or the retarded angle position, and the phase angle between the outer cylinder portion 10 and the camshaft 2 is determined. In addition, when torque is applied between the outer cylinder portion 10 and the inner cylinder portion 12 as torque input from the outer cylinder portion 10 or the camshaft 2 and torque is applied in the advance direction (the intermediate member 14 moves toward the head H side). When traveling, the piece 94 is locked in the guide groove 54 of the intermediate member 14 due to the frictional force, and the intermediate member 14 cannot advance to the head H side. At this time, since the outer cylinder part 10 and the inner cylinder part 12 cannot move relative to the intermediate member 14, even if torque acts between the outer cylinder part 10 and the inner cylinder part 12, the outer cylinder part 10 and the inner cylinder part 12 do not operate. The holding state (self-locking state) is established.

  On the other hand, when the axial displacement of the intermediate member 14 acts on the phase adjusting mechanism 18A, only the elastic force by the spring 96 acts on the piece 94, so the piece 94 slides along the guide groove 54, The intermediate member 14 can move along the axial direction of the inner cylinder portion 12.

  Here, for example, when advance control is performed by energization of the solenoid 74 when the intermediate member 14 is in the retard position, the intermediate member 14 is fixed to the intermediate member 14 as the intermediate member 14 moves to the head H side. The ball 46 also moves to the head H side together with the intermediate member 14. At this time, in accordance with the movement of the intermediate member 14 and the ball 46, the outer cylinder portion 10 and the inner cylinder portion 12 are circumferentially displaced in opposite directions, and according to the position of the intermediate member 14 in the axial direction. Circumferential displacements of different sizes are applied, the outer cylinder portion 10 rotates counterclockwise with respect to the ball 46 as viewed from the crank pulley CP side, and the inner cylinder portion 12 cranks against the ball 46. It rotates clockwise as viewed from the pulley CP side, and the phase between the outer cylinder portion 10 and the camshaft 2 is adjusted to the advance side.

  On the other hand, when the intermediate member 14 is in the advanced position, if the retard control is performed by energizing the solenoid 76, the intermediate member 14 moves to the crank pulley CP side as the intermediate member 14 moves from the head H side to the crank pulley CP side. The fixed ball 46 also moves from the head H side to the crank pulley CP side. At this time, in accordance with the movement of the intermediate member 14 and the ball 46, the outer cylinder portion 10 and the inner cylinder portion 12 are circumferentially displaced in opposite directions, and according to the position of the intermediate member 14 in the axial direction. Circumferential displacements of different sizes are applied, the outer cylinder portion 10 rotates clockwise with respect to the ball 46 as viewed from the crank pulley CP side, and the inner cylinder portion 12 rotates with respect to the ball 46 as a crank pulley. It rotates counterclockwise as viewed from the CP side, and the phase between the outer cylinder portion 10 and the camshaft 2 is adjusted to the retard side.

  According to the present embodiment, in the process in which the intermediate member 14 moves to the advanced position or the retarded position as the solenoid 74 or the solenoid 76 is energized, in response to the axial displacement accompanying the movement of the intermediate member 14, The ball 46 moves along the lead groove groups 90 and 92, and the circumferential displacement is opposite to the outer cylinder portion 10 and the inner cylinder portion 12, depending on the position of the intermediate member 14 in the axial direction. Circumferential displacements having different sizes are applied, and the phase between the outer cylinder portion 10 and the camshaft 2 is variably adjusted.

  On the other hand, when the intermediate member 14 is set to the advanced position or the retarded position in accordance with the deenergization of the solenoid 74 and the solenoid 76 and the phase angle between the outer cylinder 10 and the camshaft 2 is determined, the outer cylinder 10 or the torque input from the camshaft 2, the movement of the ball 46 is stopped and torque transmission is prevented, so that the drive shaft side including the outer cylinder portion 10 and the driven shaft side including the inner cylinder portion 12 Torque transmission is irreversible and a self-holding state (self-locking state) is established.

  That is, after the phase angle between the outer cylinder portion 10 and the camshaft 2 is determined, even if a reaction force is received from the camshaft 2, the power shaft side including the outer cylinder portion 10 and the inner side are not consumed even if a reaction force is received. The driven shaft side including the cylindrical portion 12 is in a self-holding state (self-locking state), the phase angle can be held at the determined phase angle, and power consumption can be reduced.

  Next, a third embodiment of the present invention will be described with reference to FIG. In this embodiment, a helical spline is used without using a ball, and other configurations are the same as those in the first embodiment or the second embodiment. The phase adjustment mechanism 18B in the present embodiment is a nonreciprocal torque transmission mechanism in which a piece 94 and a spring 96 are inserted in series between the outer cylinder portion 10 and the inner cylinder portion 12, and the outer peripheral surface of the intermediate member 14 A helical spline 98 is formed on the surface. The helical spline 98 of the intermediate member 14 is formed so as to be able to mesh with a helical spline (not shown) formed in the outer cylinder portion 10.

  In addition, the position of the outer cylinder part 10 and the inner cylinder part 12 can be made reverse, and the helical spline which can mesh | engage with the helical spline 98 of the intermediate member 14 can also be formed in the inner cylinder part 12. FIG.

  The piece 94 is formed in a substantially rectangular shape, is slidably inserted into the guide groove 54, is urged in a direction away from the intermediate member 14 by receiving an elastic force from a spring 96 mounted in the guide groove 54, The movement due to the elastic force of the spring 96 is restricted by contact with the outer cylinder portion 10. The intersection angle θ between the piece 94 and the guide groove 54 (the angle θ formed between the straight line along the guide groove 54 and the axis of the intermediate member 14) is set to be greater than 0 degree and equal to or less than the friction angle.

  The phase adjustment mechanism 18B is an irreversible torque transmission mechanism, and when the torque acts between the outer cylinder part 10 and the inner cylinder part 12, the phase adjustment mechanism 18B twists in opposite directions, but the intermediate member 14 and the outer cylinder part 10 or the inner cylinder part. The intermediate member 14 tends to move along its axial direction, whereas the outer cylinder portion 10 and the inner cylinder portion 12 try to move in the rotational direction. At this time, the intermediate member 14 tries to co-rotate with the outer cylinder part 10 or the inner cylinder part 12 due to friction between the piece 94 and the outer cylinder part 10 or the inner cylinder part 12, The member 14 tends to be moved in the axial direction opposite to the direction in which the torque is applied (the direction in which the torque acts).

  For example, when the solenoid 74 and the solenoid 76 are in a non-energized state, the intermediate member 14 is set to the advanced angle position or the retarded angle position, and the phase angle between the outer cylinder portion 10 and the camshaft 2 is determined. In addition, when torque is applied between the outer cylinder portion 10 and the inner cylinder portion 12 as torque input from the outer cylinder portion 10 or the camshaft 2 and torque is applied in the advance direction (the intermediate member 14 moves toward the head H side). When traveling, the piece 94 is locked in the guide groove 54 of the intermediate member 14 due to the frictional force, and the intermediate member 14 cannot advance to the head H side. At this time, since the outer cylinder part 10 and the inner cylinder part 12 cannot move relative to the intermediate member 14, even if torque acts between the outer cylinder part 10 and the inner cylinder part 12, the outer cylinder part 10 and the inner cylinder part 12 do not operate. The holding state (self-locking state) is established.

  On the other hand, when the axial displacement of the intermediate member 14 acts on the phase adjusting mechanism 18B, only the elastic force by the spring 96 acts on the piece 94, so the piece 94 slides along the guide groove 54, The intermediate member 14 can move along the axial direction of the inner cylindrical portion 12 while the helical spline 98 is engaged with the helical spline of the outer cylindrical portion 10.

  Here, for example, when advance control is performed by energization of the solenoid 74 when the intermediate member 14 is in the retard position, the intermediate member 14 moves the head while the helical spline 98 is engaged with the helical spline of the outer cylinder portion 10. Move to H side. At this time, with the movement of the intermediate member 14, the outer cylinder portion 10 and the inner cylinder portion 12 are circumferentially displaced in directions opposite to each other, and have a magnitude corresponding to the position of the intermediate member 14 in the axial direction. Different circumferential displacements are applied, the outer cylinder portion 10 rotates counterclockwise with respect to the intermediate member 14 as viewed from the crank pulley CP side, and the inner cylinder portion 12 rotates with respect to the intermediate member 14 as a crank pulley. It rotates clockwise as viewed from the CP side, and the phase between the outer cylinder portion 10 and the camshaft 2 is adjusted to the advance side.

  On the other hand, when the intermediate member 14 is in the advanced position and the retard control is performed by energization of the solenoid 76, the intermediate member 14 is moved from the head H side while the helical spline 98 is engaged with the helical spline of the outer cylinder portion 10. Move to the crank pulley CP side. At this time, with the movement of the intermediate member 14, the outer cylinder portion 10 and the inner cylinder portion 12 are circumferentially displaced in directions opposite to each other, and have a magnitude corresponding to the position of the intermediate member 14 in the axial direction. Different circumferential displacements are applied, the outer cylinder portion 10 rotates clockwise with respect to the intermediate member 14 as viewed from the crank pulley CP side, and the inner cylinder portion 12 rotates with respect to the intermediate member 14 as a crank pulley CP. Rotating counterclockwise when viewed from the side, the phase between the outer cylinder portion 10 and the camshaft 2 is adjusted to the retard side.

  According to the present embodiment, in the process in which the intermediate member 14 moves to the advanced position or the retarded position as the solenoid 74 or the solenoid 76 is energized, in response to the axial displacement accompanying the movement of the intermediate member 14, The intermediate member 14 moves along the axial direction of the inner cylinder part 12 while the helical spline 98 meshes with the helical spline of the outer cylinder part 10, and the circumferential directions in the opposite directions with respect to the outer cylinder part 10 and the inner cylinder part 12 A displacement, which is a displacement in the circumferential direction with a different size depending on the position of the intermediate member 14 in the axial direction, is applied, and the phase between the outer cylinder portion 10 and the camshaft 2 is variably adjusted.

  On the other hand, when the intermediate member 14 is set to the advanced position or the retarded position in accordance with the deenergization of the solenoid 74 and the solenoid 76 and the phase angle between the outer cylinder 10 and the camshaft 2 is determined, the outer cylinder 10 or the torque input from the camshaft 2, the movement of the intermediate member 14 is stopped and torque transmission is prevented, so that the drive shaft side including the outer cylinder portion 10 and the driven shaft including the inner cylinder portion 12 On the side, torque transmission is irreversible and a self-holding state (self-locking state) is established.

  That is, after the phase angle between the outer cylinder portion 10 and the camshaft 2 is determined, even if a reaction force is received from the camshaft 2, the power shaft side including the outer cylinder portion 10 and the inner side are not consumed even if a reaction force is received. The driven shaft side including the cylindrical portion 12 is in a self-holding state (self-locking state), the phase angle can be held at the determined phase angle, and power consumption can be reduced.

  Next, a fourth embodiment of the present invention will be described with reference to FIG. In this embodiment, the position control mechanism 16A is configured by using screws of a normal lead and a reverse lead, and other configurations are the same as any one of the first to third embodiments. . In this embodiment, the position control mechanism 16A energizes the plurality of rotating drums 100 and 102 disposed around the inner cylinder portion 12 so as to be rotatable with the inner cylinder portion 12 and the solenoid 74 at the time of advance, thereby braking the brake plate. By rotating 70, a braking force is applied to the rotating drum 100 to decelerate the rotation of the rotating drum 100, and at a retarded angle, the solenoid 76 is energized and the braking plate 72 is rotated to rotate the rotating drum 102. And the electromagnetic clutches 66 and 68 for decelerating the rotation of the rotating drum 102, and the flange portion 104 of the intermediate member 14A is inserted between the rotating drum 100 and the rotating drum 102 (intermediate). The member 14A corresponds to a member in which the flange portion 104 is formed on one end side in the axial direction of the intermediate member 14. On the surface of each rotary drum 100, 102 facing the intermediate member 14 </ b> A, there is a positive lead screw portion 106 or a reverse lead screw portion 108 for guiding the intermediate member 14 </ b> A along the axial direction of the inner cylinder portion 12. Is formed. The positive lead screw portion 106 meshes with the positive lead screw portion 112 of the intermediate member 14A, and the reverse lead screw portion 108 meshes with the reverse lead screw portion 110 of the intermediate member 14A.

  Here, when the solenoid 74 and the solenoid 76 are not energized, the rotating drums 100 and 102 rotate together with the intermediate member 14A. For example, when controlling the opening / closing timing of the intake valve, the intermediate member 14A is the latest when idling. In the corner position. Thereafter, in order to control the advance angle, only the solenoid 74 is energized when the rotating drums 100 and 102 are rotating together with the intermediate member 14A, and a braking force is applied from the braking plate 70 to the rotating drum 100 to rotate the rotating drum. When the rotation of 100 is decelerated, the intermediate member 14 </ b> A rotates with the rotating drum 102. At this time, a speed difference is generated between the screw portion 106 and the screw portion 112, the two are in a state of being able to rotate relative to each other, and the rotary drum 100 is in a decelerated state. As a result, the intermediate member 14 </ b> A relatively moves to the head H side due to the engagement of the screw portion 106 and the screw portion 112. By energization of the solenoid 74, the intermediate member 14A moves to the most advanced position. In the process in which the intermediate member 14A moves from the most retarded position to the most advanced position, if the solenoid 74 is turned off at an arbitrary timing, the intermediate member 14A is positioned at an arbitrary advanced position.

  On the other hand, when the intermediate member 14A is at the most advanced position, when the retard control is performed, only the solenoid 76 is energized and rotated from the brake plate 72 when the rotary drums 100 and 102 are rotating together with the intermediate member 14A. When a braking force is applied to the drum 102 to decelerate the rotation of the rotating drum 102, the intermediate member 14 </ b> A rotates with the rotating drum 100. At this time, a speed difference is generated between the screw portion 108 and the screw portion 110, the two are in a state where they can be rotated relative to each other, and the rotary drum 102 is in a decelerated state. As a result, the intermediate member 14 </ b> A relatively moves to the crank pulley CP side (the head side of the cam bolt 19) along the axial direction of the inner cylinder portion 12 due to the meshing of the screw portion 108 and the screw portion 110. The energization of the solenoid 76 moves the intermediate member 14A to the most retarded position. In the process in which the intermediate member 14A moves from the most advanced position to the most retarded position, if the solenoid 76 is deenergized at an arbitrary timing, the intermediate member 14A is positioned at an arbitrary retarded position.

  When the intermediate member 14A is at an arbitrary advance angle position or retard angle position, the intermediate member 14A rotates together with the rotary drums 100 and 102. Thereafter, when the advance angle control is performed, the solenoid 74 is energized. The intermediate member 14A can be positioned at another advance angle position, and when the retard angle control is performed, the intermediate member 14A can be positioned at another retard angle position by energizing the solenoid 76.

  According to the present embodiment, the intermediate member 14A can be accurately positioned at the advanced or retarded position by meshing the screw portions 106, 112 of the positive lead and the screw portions 108, 110 of the reverse lead.

  Next, a fifth embodiment of the present invention will be described with reference to FIG. In this embodiment, the position control mechanism 16B is configured by using a groove of a ball and a reverse lead, and other configurations are the same as those of any one of the first to fourth embodiments. is there. In the present embodiment, the position control mechanism 16B energizes the plurality of rotating drums 114 and 116 disposed around the inner cylinder portion 12 so as to be rotatable with the inner cylinder portion 12 and the solenoid 74 at the time of advance, thereby braking the brake plate. By rotating 70, a braking force is applied to the rotating drum 114 to decelerate the rotation with the inner cylinder portion 12, and at a retarded angle, the solenoid 76 is energized, and the rotating plate 116 is rotated by rotating the braking plate 72. Electromagnetic clutches 66 and 68 that apply braking force to decelerate rotation with the inner cylinder portion 12 are provided, and the flange portion 118 of the intermediate member 14B is inserted between the rotary drum 114 and the rotary drum 1116. (The intermediate member 14B corresponds to a member in which the flange portion 118 is formed on one axial end side of the intermediate member 14). Of the rotating drums 114 and 116, on the surface facing the intermediate member 14B, a positive lead ball groove (right screw) 122 for guiding the intermediate member 14B along the axial direction of the inner cylinder portion 12 and a reverse lead A ball groove (left-hand thread) 120 is formed. The ball grooves 120 and 122 are configured as rolling paths or sliding paths for the balls 124 that are slidably or slidably inserted into the holes of the flange portion 118 of the intermediate member 14B.

  Here, when the solenoid 74 and the solenoid 76 are in a non-energized state, the rotating drums 114 and 116 rotate together with the intermediate member 14B. For example, when controlling the opening / closing timing of the intake valve, the intermediate member 14B is the latest when idling. In the corner position. Thereafter, in order to control the advance angle, only the solenoid 74 is energized when the rotating drums 114 and 116 are rotating together with the intermediate member 14B, and a braking force is applied from the braking plate 70 to the rotating drum 114. When the rotation of 114 is decelerated, the intermediate member 14B rotates together with the rotating drum 114. At this time, a speed difference is generated between the ball 124 and the ball groove 120, the two can rotate relative to each other, and the rotating drum 114 is decelerated. As a result, the intermediate member 14 </ b> B moves to the head H side when the ball 124 rolls or slides along the ball groove 122. When the solenoid 74 is energized, the intermediate member 14B moves to the most advanced position. When the intermediate member 14B is moved from the most retarded position to the most advanced position, the solenoid 74 is deenergized at an arbitrary timing, so that the intermediate member 14B is positioned at an arbitrary advanced position.

  On the other hand, when the retard control is performed when the intermediate member 14B is at the most advanced angle position, only the solenoid 76 is energized and rotated from the brake plate 72 when the rotary drums 114 and 116 are rotating together with the intermediate member 14B. When a braking force is applied to the drum 116 to decelerate the rotation of the rotating drum 116, the intermediate member 14 </ b> B rotates together with the rotating drum 114. At this time, a speed difference is generated between the ball 124 and the ball groove 122, the two can rotate relative to each other, and the rotating drum 116 is decelerated. As a result, relative to the intermediate member 14B, the ball 124 rolls or slides along the ball groove 120, so that the intermediate member 14B moves along the axial direction of the inner cylinder portion 12 to the crank pulley CP side (the head of the cam bolt 19). To the side). By energizing the solenoid 76, the intermediate member 14B moves to the most retarded position. If the solenoid 76 is deenergized at an arbitrary timing in the process of moving the intermediate member 14B from the most advanced position to the most retarded position, the intermediate member 14B is positioned at an arbitrary retarded position.

  When the intermediate member 14B is in an arbitrary advance angle position or retard angle position, the intermediate member 14B rotates together with the rotary drums 114 and 116. After that, when the advance angle control is performed, the solenoid 74 is energized. The intermediate member 14B can be positioned at another advance angle position, and when the retard angle control is performed, the intermediate member 14B can be positioned at another retard angle position by energizing the solenoid 76.

  According to this embodiment, the ball 124 moves along the ball groove 122 of the positive lead or the ball groove 120 of the reverse lead, so that the intermediate member 14B can be accurately positioned at the advanced or retarded position. .

  Next, a sixth embodiment of the present invention will be described with reference to FIG. In this embodiment, instead of the flange portion 22 of the bearing 20, a flange portion 22A having a structure in which an attachment portion 22a is formed at an axial end portion of the flange portion 22 is used, and between the outer periphery of the intermediate member 14 and the attachment portion 22a. A bearing 20 is disposed on the outer periphery of the intermediate member 14, and a holder 23 is mounted on the outer periphery of the intermediate member 14 via a bearing 20 and a flange portion 22A. Other configurations are the same as those of the first embodiment. The structure in the present embodiment can also be applied to those in the second to fifth embodiments.

  According to the present embodiment, since the holder 23 is mounted on the outer periphery of the intermediate member 14 via the bearing 20 and the flange portion 22A, the length in the axial direction of the inner cylinder portion 12 is made longer than that of the first embodiment. Can be shortened.

  Next, a seventh embodiment of the present invention will be described with reference to FIG. In this embodiment, instead of the flange portion 22 of the bearing 20, a flange portion 22 </ b> B having a structure in which an attachment portion 22 b is formed at the axial end portion of the flange portion 22 is used, and the flange portion 10 a and the attachment portion of the outer cylinder portion 10 are used. The bearing 20 is arranged between the outer cylinder portion 10 and the holder 23 is mounted on the outer periphery of the flange portion 10a of the outer cylinder portion 10 via the bearing 20 and the flange portion 22B. Other configurations are the same as those of the first embodiment. It is the same. The structure in the present embodiment can also be applied to those in the second to fifth embodiments.

  According to the present embodiment, since the holder 23 is mounted on the outer periphery of the flange portion 10a of the outer cylinder portion 10 via the bearing 20 and the flange portion 22B, the shaft of the inner cylinder portion 12 is more than that of the first embodiment. The length in the direction can be shortened.

  According to each of the above-described embodiments, since the general-purpose solenoids 74 and 76 can be used as the electromagnetic clutches 66 and 68, the cost can be reduced.

  Further, according to each of the above embodiments, the entire apparatus has an integral structure, and handling is easier than a conventional structure in which an electromagnetic clutch is attached to the cover side.

DESCRIPTION OF SYMBOLS 10 Outer cylinder part 12 Inner cylinder part 14, 14A, 14B Intermediate member 16, 16A, 16B Position control mechanism 18, 18A, 18B Phase adjustment mechanism 26 Lead groove 28 Small diameter outer cylinder part 34, 36 Large diameter part 42, 44 Lead groove 46, 48 Ball 50 Small diameter portion 52 Large diameter portion 54 Guide groove 56 Fixing hole 58, 60 Lamp 62, 64, 100, 102, 114, 116 Rotary drum 66, 68 Electromagnetic clutch 70, 72 Brake plate 74, 76 Solenoid 78, 80 lamp 82, 94 pieces 84 groove 86 straight section

Claims (5)

An outer cylinder portion that transmits the driving force of the crankshaft of the engine and a camshaft that is rotatably arranged on the inner peripheral side of the outer cylinder portion and that opens and closes the intake valve or the exhaust valve of the engine is coaxial. The connected inner cylinder part, the intermediate member arrange | positioned along the axial direction of the said inner cylinder part at the outer periphery of the said inner cylinder part, and the said axial direction of the said intermediate member according to the driving | running state of the said engine A position control mechanism that controls the position of the intermediate member, and a phase adjustment mechanism that variably adjusts the phase between the outer tube portion and the camshaft according to the position of the intermediate member in the axial direction,
The phase adjustment mechanism is
A first lead groove group formed in a direction intersecting the axis of the inner periphery of the outer cylinder part and formed in parallel to each other, and the first lead groove group of the outer periphery of the inner cylinder part. A second lead groove group which intersects the axis of the region facing the first region and is formed in a direction opposite to the first lead groove group and parallel to each other; the first lead groove group and the first lead groove group; A plurality of sliding bodies or rolling elements that are slidably or slidably inserted into the sliding path or rolling path, and the sliding member among the intermediate members. A piece inserted into a guide groove formed on a surface facing the movement path or the rolling path so as to be slidable or rollable, and the plurality of sliding bodies or rolling bodies slide or roll on the intermediate member. The piece is movably fixed, and the piece receives an elastic force and urges away from the intermediate member. The movement due to the elastic force is restricted by contact with the outer cylinder part or the inner cylinder part, and the intersection angle between the piece and the guide groove is set to be more than 0 degree and less than the friction angle. In response to torque input from the outer cylinder or the camshaft, the transmission of the torque is prevented, and the axial displacement is displaced in the circumferential direction in response to the axial displacement from the intermediate member. The circumferential displacement is a displacement having a different size depending on the position of the intermediate member in the axial direction, and is applied to the outer tube portion and the inner tube portion as displacements in opposite directions to each other. Engine valve control device. An outer cylinder portion that transmits the driving force of the crankshaft of the engine and a camshaft that is rotatably arranged on the inner peripheral side of the outer cylinder portion and that opens and closes the intake valve or the exhaust valve of the engine is coaxial. The connected inner cylinder part, the intermediate member arrange | positioned along the axial direction of the said inner cylinder part at the outer periphery of the said inner cylinder part, and the said axial direction of the said intermediate member according to the driving | running state of the said engine A position control mechanism that controls the position of the intermediate member, and a phase adjustment mechanism that variably adjusts the phase between the outer tube portion and the camshaft according to the position of the intermediate member in the axial direction,
The phase adjustment mechanism is
A piece and a spring inserted in series between the outer cylinder part and the inner cylinder part are provided, and the intermediate member and the outer cylinder part or the inner cylinder part are meshed with each other by a helical spline. It is slidably inserted into a guide groove formed in the intermediate member, receives an elastic force from a spring mounted in the guide groove and is urged away from the intermediate member, and accompanies the elastic force of the spring. The movement is restricted by contact with the outer cylinder part or the inner cylinder part, and the intersection angle between the piece and the guide groove is set to be greater than 0 degree and less than the friction angle, and the outer cylinder part or In response to torque input from the camshaft, transmission of the torque is blocked, and in response to axial displacement from the intermediate member, the axial displacement is converted into circumferential displacement, and the circumferential displacement is Intermediate member A position different displacement sizes depending on the serial direction, the valve control apparatus for an engine comprising imparted to the outside of the inner cylinder portion and the cylinder portion as a reverse direction of displacement from each other.   The position control mechanism includes a plurality of rotating drums arranged around the inner cylinder portion so as to be rotatable with the inner cylinder portion, and rotation of one of the plurality of rotating drums during advance based on electromagnetic force. A braking force is applied to the drum to decelerate rotation with the inner cylinder portion, and at a retarded angle, a braking force is applied to the other rotating drum of the plurality of rotating drums to decelerate rotation with the inner cylinder portion. And an electromagnetic clutch to be formed, and a slide lamp is formed along the circumferential direction on the inner peripheral side of each rotary drum, and each slide lamp is formed along the circumferential direction on the outer peripheral side of the intermediate member. The valve control device for an engine according to claim 1 or 2, wherein the valve control device is engaged with one of a pair of positioning lamps.   The position control mechanism includes a plurality of rotating drums arranged around the inner cylinder portion so as to be rotatable with the inner cylinder portion, and rotation of one of the plurality of rotating drums during advance based on electromagnetic force. A braking force is applied to the drum to decelerate rotation with the inner cylinder portion, and at a retarded angle, a braking force is applied to the other rotating drum of the plurality of rotating drums to decelerate rotation with the inner cylinder portion. An electromagnetic clutch to be inserted, and a flange portion of the intermediate member is inserted between the one rotating drum and the other rotating drum, and a surface of each rotating drum facing the flange portion of the intermediate member A forward lead or reverse lead thread portion for guiding the intermediate member along the axial direction of the inner cylinder portion is formed, and a forward lead or reverse lead thread portion is formed on the flange portion of the intermediate member. , The screw part of the positive lead Valve control device for an engine according to claim 1 or 2, threaded portions of or the reverse lead is characterized by comprising maintaining a meshed state with each other.   The position control mechanism includes a plurality of rotating drums arranged around the inner cylinder portion so as to be rotatable with the inner cylinder portion, and rotation of one of the plurality of rotating drums during advance based on electromagnetic force. A braking force is applied to the drum to decelerate rotation with the inner cylinder portion, and at a retarded angle, a braking force is applied to the other rotating drum of the plurality of rotating drums to decelerate rotation with the inner cylinder portion. An electromagnetic clutch to be inserted, and a flange portion of the intermediate member is inserted between the one rotating drum and the other rotating drum, and a surface of each rotating drum facing the flange portion of the intermediate member A groove for a forward lead or a reverse lead for guiding the intermediate member along the axial direction of the inner cylinder portion is formed, and a groove for the forward lead or the reverse lead is formed on the flange portion of the intermediate member as a sliding path. Or a sliding body as a rolling path or Rolling elements valve control apparatus for an engine according to claim 1 or 2, characterized in that fixed slidably or rolling.

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