JP2005002952A - Valve opening/closing timing controller - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To realize a valve opening/closing timing controller which prevents such defective operation that a wound coil part of a spring runs on a guide part during operation of the spring energizing a lock member. <P>SOLUTION: The valve opening/closing timing controller is equipped with a retraction groove part 34 formed on a rotating transmission member 3 and housing a lock plate 80 which is energized toward a rotating member 2 by a coil spring 81; a spring housing hole 35 communicating with the retraction groove part 34, housing the coil spring 81 and provided with the guide part 35a for guiding the coil spring 81 in an axial direction; and a receiving part 23 which is formed on the rotating member 2 and which a head part 80a of the lock plate 80 is set into when the relative position of the rotating member 2 and the rotating transmission member 3 corresponds to a predetermined position. Length A of the guide part 35a in the axial direction is set larger than a clearance B between wound coils adjacent to each other in an axial direction of the coil spring 81. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a valve opening / closing timing control device for controlling the opening / closing timing of intake and exhaust valves of an internal combustion engine.
[0002]
[Prior art]
As this kind of valve opening / closing timing control device, a rotating member integrally connected to a valve opening / closing camshaft, and a rotating member is assembled to the rotating member so as to be relatively rotatable within a predetermined range, and rotational power from a crankshaft is transmitted. The oil chamber formed in the rotation transmission member is divided into an advance oil chamber and a retard oil chamber by a vane attached to the rotation member, and the advance oil chamber and the retard angle. There are first and second hydraulic oil passages that supply and discharge hydraulic oil to and from the oil chamber, respectively, and rotate and rotate the rotation member and the rotation transmission member relative to each other by supplying and discharging hydraulic oil to and from each oil chamber. . The rotation transmitting member is formed with a retracting groove portion that accommodates the lock member biased toward the rotating member by the spring, and further includes a guide portion that communicates with the retracting groove portion and accommodates the spring and guides the spring in the axial direction. A provided spring accommodation hole is formed. The rotating member is formed with a receiving portion into which the head of the locking member is inserted when the relative position with respect to the rotation transmitting member is a predetermined position. Then, the rotation transmission member can be locked to the rotation member by fitting the lock member and the receiving portion.
[0003]
In such a valve opening / closing timing control device, the outer periphery of the winding portion and the spring accommodation hole are provided in the spring accommodation hole so that the spring winding portion does not bend when the spring expands and contracts as the lock member extends and retracts. An appropriate clearance is provided between the inner periphery and the guide portion for guiding the spring. On the other hand, while securing the seating surface of the both ends of a spring at the junction part of the radial direction both ends of the spring accommodation hole which the both ends of a spring seat, and the inner peripheral surface of a guide part, ie, the end part of a guide part, When the rotating member and the rotation transmitting member are locked, a concave corner R is formed so that stress generated when rotational power is applied in the rotation direction is not concentrated (see, for example, Patent Document 1).
[0004]
[Patent Document 1]
[Patent Document 1] Japanese Patent Laid-Open No. 2003-13713
[Problems to be solved by the invention]
However, in the conventional configuration described above, when the spring is assembled in the spring accommodating hole, or when the head of the lock member is immersed in the receiving portion and the spring is extended, the spring winding is connected to the end portion of the guide portion ( There is a possibility that the lock member is not accommodated in the retracting groove portion and malfunctions because the winding portion cannot be contracted by riding on the concave corner R).
[0006]
Therefore, an object of the present invention is to realize a valve opening / closing timing control device that does not cause a malfunction such that a winding portion rides on a guide portion while a spring for energizing a lock member is operating.
[0007]
[Means for Solving the Problems]
A first technical means made to solve the above technical problem includes a rotating member integrally connected to a valve opening / closing camshaft rotatably mounted on a cylinder head of an internal combustion engine, and the rotation A rotation transmission member that is assembled so as to be relatively rotatable within a predetermined range with respect to the member, and that transmits rotational power from a crankshaft; a vane provided on either the rotation member or the rotation transmission member; and the rotation member And an oil hydraulic chamber formed between the rotation transmission member and the advance oil chamber and the retard oil chamber by the vane, and the advance oil chamber and the retard oil chamber, respectively. First and second hydraulic oil passages for supplying and discharging oil, and a lock member formed in the rotation transmission member or the rotation member and biased toward the rotation member or the rotation transmission member by a spring And a retraction part, a spring accommodating hole that communicates with the retraction part, and has a guide part that guides the spring in the axial direction, and the rotation member or the rotation transmission member. A receiving portion into which the head of the lock member is retracted when the relative position of the member and the rotation transmitting member coincides with each other at a predetermined position, and a third hydraulic oil passage for supplying and discharging hydraulic oil to and from the receiving portion. In the valve opening / closing timing control device for controlling the opening / closing timing of the intake valve or the exhaust valve of the engine, the length of the guide portion in the axial direction is determined by a gap between lines provided between windings adjacent in the axial direction of the spring. This is a large setting.
[0008]
According to this means, when the length of the guide portion in the axial direction is set larger than the gap between the lines provided between the windings adjacent to each other in the axial direction of the spring, when assembling the spring in the spring accommodating hole, or When the head of the lock member is inserted into the receiving part and the spring is extended, the winding member runs over the end part (concave corner R) of the guide part, and the winding part cannot contract, so the lock member is retracted. It is possible to prevent malfunction due to being not accommodated in the part.
[0009]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments of the present invention will be described with reference to the drawings.
[0010]
A valve opening / closing timing control device 1 shown in FIGS. 1 to 4 includes a camshaft 10 that is rotatably supported by a cylinder head 100 of an internal combustion engine, and an internal rotor 20 that is integrally assembled to the tip of the camshaft 10. And a rotary member 2 for opening and closing the valve. Further, the valve timing control device 1 has a rotation transmission member 3 including an external rotor 30, a front plate 40, and a rear plate 50 that are assembled so as to be able to rotate relative to the internal rotor 20 within a predetermined range. ing. An integrally provided timing sprocket 31 is formed on the outer periphery of the outer rotor 30. Further, a torsion spring 60 assembled between the inner rotor 20 and the front plate 40, four vanes 70 assembled to the inner rotor 20, a lock plate 80 (FIG. 2) assembled to the outer rotor 30, and the like. Is provided.
[0011]
As is well known, rotational power is transmitted to the timing sprocket 31 from a crankshaft (not shown) via a crank sprocket and a timing chain in the clockwise direction shown as the camshaft rotation direction in FIG.
[0012]
The camshaft 10 has a known cam (not shown) that opens and closes an intake valve (not shown), and an advance angle passage (first hydraulic oil passage) extending in the axial direction of the camshaft 10 inside the camshaft 10. 11 and a retard passage (second hydraulic oil passage) 12 are provided. The advance passage 11 is connected to the first connection port 201 of the switching valve 200 through the radial passage 71 and the annular groove 14 provided in the camshaft 10 and the connection passage 16 provided in the cylinder head 100. Further, the retard passage 12 is connected to the second connection port 202 of the switching valve 200 through the radial passage 72 provided in the camshaft 10 and the connection groove 15 provided in the annular groove 13 and the cylinder head 100.
[0013]
The switching valve 200 is a known valve that energizes the solenoid 203 to move the spool 204 against a spring (not shown). When the power is not supplied, the supply port 206 connected to the oil pump 205 driven by the internal combustion engine communicates with the second connection port 202, and the first connection port 201 communicates with the discharge port 207. . When energized, the supply port 206 communicates with the first connection port 201 and the second connection port 202 communicates with the discharge port 207 as shown in FIG. Therefore, hydraulic oil (hydraulic pressure) is supplied to the retard passage 12 when the switching valve 200 is not energized, and hydraulic oil (hydraulic pressure) is supplied to the advance passage 11 when energized. The switching valve 200 is duty-controlled to change the ratio between energization and non-energization per unit time. For example, when the duty ratio is controlled at 50%, the first and second ports 201 and 202 and the supply and discharge ports 206 and 207 are not in communication with each other.
[0014]
The inner rotor 20 is integrally fixed to the camshaft 10 by mounting bolts 91. Further, as shown in FIG. 2, four vane grooves 21 and a receiving portion 22 are formed in the inner rotor 20. The inner rotor 20 has three first hydraulic oil passages 23 extending in the radial direction, one hydraulic oil groove 23a, four second hydraulic oil passages 24, and a bottom portion of the receiving portion 22 through an advance passage. A plurality of hydraulic oil passages including one third hydraulic oil passage 25 that communicates with the first hydraulic oil passage 11 are provided.
[0015]
As shown in FIG. 2, a vane 70 is inserted into each vane groove 21, and the vane 70 is movable in four working hydraulic pressure chambers R <b> 0 formed between an external rotor 30 and an internal rotor 20 described later, and The hydraulic operating chamber R0 is arranged so as to be divided into an advance oil chamber R1 and a retard oil chamber R2. A vane spring 73 (FIG. 1) is disposed between the bottom of the vane groove 21 and the bottom surface of the vane 70, and each of the four vanes 70 is pushed into the vane groove 21 in the radial direction. Mounted movably.
[0016]
The receiving portion 22 can move to the external rotor 30 in the state shown in FIG. 2, that is, when the relative positions of the camshaft 10 and the internal rotor 20 and the external rotor 30 coincide with each other at a predetermined position (most retarded position). A head 80a of a flat plate-like lock plate (lock member) 80 attached to the head is recessed by a predetermined amount so that the rotation of the outer rotor 30 and the inner rotor 20 can be locked.
[0017]
As shown in FIG. 2, hydraulic oil (hydraulic pressure) is supplied to and discharged from the four retard oil chambers R <b> 2 divided by the vanes 70 through the retard passage 12 and the second hydraulic oil passage 24. It becomes the composition which is done. In addition, hydraulic oil (hydraulic pressure) is supplied to and discharged from three of the four advance oil chambers R <b> 1 through the advance passage 11 and the first hydraulic passage 23. The other hydraulic oil chamber R1 is supplied with hydraulic oil (hydraulic pressure) from the third hydraulic oil passage 25 provided at the bottom of the receiving portion 22 with respect to the lock plate 80. When moved, it is configured to be able to supply and discharge via a hydraulic oil groove 23a that connects the third hydraulic oil passage 25 and the advance oil chamber R1. As described above, the first hydraulic oil passage 23 is not provided for the one advance oil chamber R1, and the third hydraulic oil passage 25 is also used, whereby the configuration of the hydraulic oil passage can be simplified and manufactured at low cost. It has a configuration.
[0018]
An annular front plate 40 and a rear plate 50 are joined to both sides of the outer rotor 30 in the axial direction, and are integrally assembled by four connecting bolts 92. The outer rotor 30 and the inner rotor 20 are rotatable relative to each other within an angle range defined by the vane 70 and the lock plate 80 that move in the working hydraulic chamber R0.
[0019]
A timing sprocket 31 is integrally formed on the outer periphery of the end portion in the axial direction where the rear plate 50 of the external rotor 30 is joined. In addition, five convex portions 33 are formed on the inner periphery of the outer rotor 30 so as to protrude radially inward. The inner peripheral surfaces of these convex portions 33 are in contact with each other so as to slide on the outer peripheral surface of the inner rotor 20, and the outer rotor 30 is rotatably supported by the inner rotor 20. Of the five protrusions 33, a retracting groove (retracting part) 34 that accommodates the lock plate 80 between the two protruding parts 33, and a lock plate 80 that communicates with the retracting groove 34 and is attached radially inward. A spring accommodating hole 35 for accommodating the energizing coil spring (spring) 81 is formed. Further, the four hydraulic hydraulic chambers R0 described above are formed between the five convex portions 33.
[0020]
As shown in FIG. 4, a coil spring 81 is disposed in the spring accommodation hole 35 so as to push the lock plate 80 toward the center in the radial direction of the external rotor 30. The coil spring 81 includes a winding portion 81a and both end portions in the axial direction. The winding part 81a is formed by winding a wire in a spiral shape, and is wound with an interval (space between wires: space between adjacent wires) B adjacent in the axial direction. Both end portions are formed in parallel to a plane perpendicular to the axial direction. In the spring accommodating hole 35, when the coil spring 81 expands and contracts as the lock plate 80 protrudes and retracts, the outer periphery of the winding part 81a and the inside of the spring accommodating hole 35 are prevented so that the winding part 81a of the coil spring 81 does not bend. An appropriate clearance is provided between the periphery and a guide portion 35 a for guiding the coil spring 81 is formed. In addition to securing seating surfaces at both ends of the coil spring 81 at the connecting portion between the both end surfaces in the radial direction of the spring accommodation hole 35 on which both ends of the coil spring 81 are seated and the inner peripheral surface of the guide portion 35a, rotation is ensured. When the member 2 and the rotation transmitting member 3 are locked, a concave corner R is formed so that stress generated when rotational power is applied in the rotation direction is not concentrated. In this configuration, the axial length A of the coil spring 81 of the guide portion 35 a is set to be larger than the inter-line gap B of the coil spring 81. Thereby, when the coil spring 81 is assembled to the spring accommodating hole 35, or when the head portion 80a of the lock plate 80 is fitted into the receiving portion 22 and the coil spring 81 is extended, the winding is connected to the end of the guide portion 35a. It is possible to prevent the winding portion 81a from contracting by climbing on the portion (concave corner R).
[0021]
The torsion spring 60 is attached with one end locked to the front plate 40 and the other end locked to the inner rotor 20. The inner rotor 20 is advanced with respect to the outer rotor 30, the front plate 40 and the rear plate 50. It is energized (clockwise in FIG. 2). Therefore, the operation response to the advance side of the internal rotor 20 is improved.
[0022]
The relative rotation of the inner rotor 20 and the outer rotor 30 to advance each other means that the vane 70 shown in FIG. 3 is advanced (clockwise) from the most retarded position shown in FIG. Is to move on. The most advanced angle is regulated at a position where the vane 70 comes into contact with one side surface in the circumferential direction of the convex portion 33, and the most retarded angle is regulated at a position where the head 80 a of the lock plate 80 enters the receiving portion 22. In this embodiment, one of the vanes 70 is in contact with the other side surface of the convex portion 33 at the most retarded position.
[0023]
The operation of the valve timing control apparatus 1 of the present embodiment configured as described above will be described. When the internal combustion engine is stopped, the oil pump 205 is stopped and the switching valve 200 is in a non-energized state, so that hydraulic oil (hydraulic pressure) is not supplied to the hydraulic pressure chamber R0. For this reason, as shown in FIG. 2, the internal rotor 20 and the external rotor 30 are in the most retarded position shown in FIG. 2 due to cam friction acting in the retarded direction. The head portion 80a of the lock plate 80 is immersed in the receiving portion 22 of the inner rotor 20, and relative rotation between the inner rotor 20 and the outer rotor 30 is restricted at the most retarded position. Even when the internal combustion engine is started and the oil pump is driven, the operation supplied from the oil pump is performed while the duty ratio for energizing the switching valve 200 is small (the ratio of the energization time to the non-energization time per unit time is small). Since the oil (hydraulic pressure) is substantially supplied to the retarding oil chamber R2 through the connecting passage 15, the retarding passage 12 and the passage 24, the valve opening / closing timing control device 1 is maintained in the locked state.
[0024]
If the valve opening / closing timing requires an advance angle depending on the operating conditions of the internal combustion engine, the duty ratio for energizing the switching valve 200 is increased, and the position of the spool 204 is switched. The hydraulic oil (hydraulic pressure) supplied from the oil pump is supplied to the receiving portion 22 through the connection passage 16, the advance passage 11 and the first hydraulic oil passage 23, or from the third hydraulic oil passage 25 to the hydraulic oil groove 23 a. And is supplied to the advance oil chamber R1.
[0025]
On the other hand, the hydraulic oil (hydraulic pressure) in the corner oil chamber R <b> 2 is discharged from the discharge port 207 of the switching valve 200 through the passage 24, the retard passage 12, and the connection passage 15. Therefore, the lock plate 80 moves against the spring 81, and its head 80a is retracted from the receiving portion 22 to unlock the inner rotor 20 and the outer rotor 30 and rotate integrally with the camshaft 10. The inner rotor 20 and the vanes 70 are rotated relative to the outer rotor 30, the front plate 40, and the rear plate 50 in the advance side (clockwise in FIG. 2). Due to this relative rotation, the state of FIG. 2 is shifted to the state of FIG. 3, and the cam timing is advanced. By controlling the duty ratio of the control valve 200, the relative rotational position can be stopped at an arbitrary position, for example, an intermediate position as shown in FIG.
[0026]
【The invention's effect】
As described above, according to the technical means taken in the invention of claim 1, the axial length of the guide portion is set to be larger than the gap between the lines provided between the adjacent windings in the axial direction of the spring. As a result, when the spring is assembled into the spring accommodating hole, or when the head of the lock member is fitted into the receiving portion and the spring is extended, the winding is at the end (concave corner R) of the guide portion. It is possible to prevent the lock member from being housed in the retracting portion and malfunctioning because the winding portion and the winding portion cannot contract.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a valve opening / closing timing control device according to an embodiment of the present invention, which is a section taken along a line AA shown in FIG.
FIG. 2 is a cross-sectional view taken along line B-B in FIG. 1 in the most retarded state of the valve timing control device according to the embodiment of the present invention.
FIG. 3 is a cross-sectional view taken along the line BB in FIG. 1 in an intermediate advance state of the valve timing control device according to the embodiment of the present invention.
4 is a longitudinal sectional view of the valve timing control apparatus according to the embodiment of the present invention, and is an enlarged view of a portion D in FIG.
[Explanation of symbols]
2 Rotating member 3 Rotation transmitting member 22 Receiving portion 23 First hydraulic oil passage 24 Second hydraulic oil passage 25 Third hydraulic oil passage 34 Retraction groove (retraction portion)
35 Spring accommodating hole 35a Guide portion 70 Vane 80 Lock plate (lock member)
80a Head 81 Coil spring (spring)
100 Cylinder head R0 Hydraulic oil chamber R1 Advance angle oil chamber R2 Delay angle oil chamber A Guide section axial length B Clearance between lines

Claims (1)

A rotating member integrally connected to a camshaft for opening and closing a valve that is rotatably assembled to a cylinder head of an internal combustion engine;
A rotation transmitting member that is assembled so as to be relatively rotatable with respect to the rotating member within a predetermined range, and that transmits rotational power from a crankshaft;
A vane provided on either the rotating member or the rotation transmitting member;
An operating hydraulic chamber formed between the rotating member and the rotation transmitting member and divided into an advance oil chamber and a retard oil chamber by the vane;
First and second hydraulic oil passages for supplying and discharging hydraulic oil to and from the advance oil chamber and the retard oil chamber,
A retraction portion that accommodates a lock member formed on the rotation transmission member or the rotation member and biased toward the rotation member or the rotation transmission member by a spring;
A spring accommodating hole that communicates with the retracting portion and accommodates the spring, and is provided with a guide portion that guides the spring in the axial direction;
A receiving portion that is formed on the rotation member or the rotation transmission member, and into which the head of the lock member is immersed when the relative position of the rotation member and the rotation transmission member coincides at a predetermined position;
In a valve opening / closing timing control device for controlling the opening / closing timing of an intake valve or an exhaust valve of an internal combustion engine comprising a third hydraulic oil passage for supplying and discharging hydraulic oil to and from the receiving portion,
The valve opening / closing timing control device characterized in that the length of the guide portion in the axial direction is set larger than a gap between lines provided between windings adjacent in the axial direction of the spring.

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