JP2006083785A - Valve timing control device of internal combustion engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing control device of an internal combustion engine, avoiding sliding of a holder member, a sprocket and a plate to restrain the occurrence of contamination, and improved in operational responsiveness and durability. <P>SOLUTION: This valve timing control device includes: a coiled spring disposed in a retard oil chamber and/or an advance oil chamber for applying the energizing force to a vane and a shoe to separate from each other; and a holder member formed to hold the coiled spring and having a sliding part provided on the circumferential side of the vane to slide at least in the direction of a rotating shaft, both side ends of which are formed of a curved surface. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a valve timing control device for an internal combustion engine, and more particularly to a holder member that holds a coil spring provided in a retard / advance oil chamber separated by a housing and a vane rotor.

Conventionally, in the valve timing control device, when the engine is stopped, the valve timing is set to a phase capable of restarting the engine. Therefore, the radial direction is defined by the housing and the vane rotor, and the axial direction is defined by the sprocket and the plate. Some coil springs are provided to bias the vane rotor to a position suitable for engine restart. Further, in this technique, in order to ensure the ease of assembly of the spring, a holder member for holding the spring is provided at both ends of the spring, and a spring unit in which the holder member and the spring are integrated is arranged in the working chamber from the axial direction. It is inserted into the axial groove (for example, see Patent Document 1).
WO01-055662 publication

  However, in the above prior art, the holder member also moves as the spring expands and contracts, so that the holder member moves in the axial direction along the axial groove in the working chamber. For this reason, there is a problem that the sprocket and plate provided at the end of the housing in the axial direction slide with the holder member, causing contamination (abrasion powder) and lowering of the operation response and durability.

  The present invention has been made paying attention to the above-mentioned problems, and an object of the present invention is to provide a valve timing control device for an internal combustion engine that suppresses the occurrence of contamination and improves the operation response and durability. There is.

  In order to achieve the above-described object, in the present invention, a rotation transmission member that transmits rotation from a crankshaft of an internal combustion engine, and one of the rotation transmission member and the camshaft are fixed, and at least one end in the axial direction has an opening. A working chamber is defined by a housing formed by a housing body and at least one plate that seals the opening of the housing body, and formed so as to protrude toward the inner peripheral side of the housing body. A shoe, a vane rotor fixed to the other of the rotation transmission member or the camshaft and having a vane protruding in the radial direction and disposed in the housing, and the working chamber are separated by the vane rotor. A retard oil chamber, an advance oil chamber, and a fluid supply / discharger that supplies and discharges oil to and from the retard oil chamber and the advance oil chamber. And a coil spring that is disposed in the retard oil chamber and / or the advance oil chamber and that exerts an urging force in a direction in which the vane and the shoe are separated from each other, and is configured to be able to hold the coil spring, A holder member provided on the circumferential side surface of the vane so as to be slidable at least in the rotational axis direction, and having both end portions in the rotational axis direction having sliding portions formed of curved surfaces.

  Therefore, it is possible to provide a valve timing control device for an internal combustion engine in which the occurrence of contamination is suppressed and the operation responsiveness and durability are improved by avoiding sliding between the holder member, the sprocket and the plate.

  Hereinafter, the best mode for realizing a valve timing control apparatus for an internal combustion engine of the present invention will be described based on Example 1 shown in the drawings.

[Outline of valve timing control device]
The first embodiment will be described with reference to FIGS. FIG. 1 is a cross-sectional view in the axial direction and a control configuration of a valve timing control device 1 (hereinafter referred to as VTC 1) at the time of engine start. The x axis in FIG. 1 is parallel to the camshaft 2. The VTC 1 is provided at the end of the camshaft 2 connected to the engine in the negative x-axis direction, and rotation is transmitted from the crankshaft through the chain.

  The VTC 1 has a housing 10 and a vane rotor 20. The vane rotor 20 is integrally fixed to the camshaft 2 by the cam bolt 3, is provided in the housing 10, and is accommodated so as to be rotatable relative to the rotation shaft of the housing 10. A sprocket 30 is provided adjacent to the positive side of the housing 10 in the x-axis direction, and the rotation of the crankshaft is transmitted by a wound chain.

  A plurality of oil chambers are defined between the vane rotor 20 and the housing 10, and are made fluid-tight by a seal 40. The seal 40 is urged in the outer diameter direction by the seal spring 41 from the inner diameter direction to ensure liquid tightness. As a result, the hydraulic oil supplied from the oil pump 4 is introduced into the oil chamber that is liquid-tight, and rotation is transmitted between the vane rotor 20 and the housing 10 via the hydraulic oil.

  At that time, the vane rotor 20 and the housing 10 are provided so as to be relatively rotatable by adjusting the supply and discharge of the hydraulic oil to change the oil chamber volume. That is, the rotational phase of the camshaft 2 is changed with respect to the rotation of the crankshaft by transmitting the rotational force between the two while the housing 10 is rotated relative to the vane rotor 20.

  Further, a lock pin 21 is provided in the vane rotor 20 in order to set the valve timing to a phase where the engine can be restarted when the engine is stopped. When the engine is stopped, the lock pin 21 is fitted into the sleeve 11 of the housing 10 to restrict the relative rotation between the vane rotor 20 and the housing 10 and to set the valve timing to a phase suitable for engine restart.

  The lock pin 21 is urged in the x-axis positive direction by a spring 23 held by a retainer 22 and is configured to be disengaged against the spring force by the action of supplied hydraulic oil. . Since the vane rotor 20 is urged in the circumferential direction by other springs, the vane rotor 20 moves in the radial direction according to the urging force when the engine is stopped and the hydraulic pressure is released, and the lock pin is locked by the relative rotation of the housing 10 and the vane rotor 20. When 21 reaches a position corresponding to the sleeve 11, the sleeve 21 is fitted.

  Thus, by providing the sleeve 11 at a position optimal for engine restart, the lock pin 21 is fitted into the sleeve 11 when the engine is stopped, and the phase of the valve timing is set to a phase suitable for engine restart. Further, even when no hydraulic pressure is generated, the housing 10 and the vane rotor 20 are held, and the vane rotor 20 flutters due to the alternating torque generated by the action of the valve springs and cams provided on the intake and exhaust valves. To prevent.

  A hydraulic control actuator 5 is provided between the oil pump 4 and the VTC 1 to control the hydraulic pressure supplied to and discharged from the oil chamber defined between the vane rotor 20 and the housing 10. The hydraulic control actuator 5 inputs the engine operating state, that is, the engine temperature detected by the water temperature sensor, the crank angle sensor, and the throttle opening sensor, the engine speed, the engine load, etc., to the controller 6 and calculates the command signal. The hydraulic oil is supplied and discharged through a hydraulic pressure supply block 7 provided in the vane rotor 20. The hydraulic control actuator 5 is driven based on a command signal from the controller 6, and hydraulic oil is selectively supplied to and discharged from the plurality of oil chambers.

  In the present embodiment, the VTC 1 is not particularly limited as long as it is provided on either or both of the intake cam shaft and the exhaust cam shaft. Alternatively, the rotation of the crankshaft may be directly transmitted to both camshafts by the chain, or the rotation may be transmitted to the other camshaft by a separate rotation transmission member after being transmitted to one camshaft. Well, not particularly limited.

[Configuration of valve timing control device]
FIG. 2 is an exploded perspective view of the VTC 1. As described above, the VTC 1 includes the housing 10, the vane rotor 20, and the sprocket 30. The vane rotor 20 includes first and second vanes 210 and 220 provided at substantially equal intervals on the outer peripheral portion, and three first vanes 210 and one second vane 220 are provided. The second vane 220 has a larger circumferential width than the first vane 210, and the second vane 220 is provided with an x-axis direction through-hole so that the lock pin 21 is slidable in the axial direction. . Further, seals 40 are provided on the outer diameter surfaces of the first and second vanes 210 and 220 so as to be in fluid-tight sliding contact with the inner peripheral surface of the housing 10.

  The housing 10 has a shoe 110 protruding radially inward on the inner peripheral surface, and a seal 50 is provided on the inner surface of the shoe 110 so as to be in fluid-tight contact with the rotor portion 230 of the vane rotor 20. As a result, a plurality (four) of oil chambers are liquid-tightly defined by the shoe 110 and the first and second vanes 210 and 220.

  In addition, if the counterclockwise rotation is positive with the x axis as the rotation axis in the figure, the positive rotation direction of the oil chamber defined by the first and second vanes 210 and 220 and the shoe 110 is the shoe 110. Spring units 300 are provided in the four oil chambers defined by the first or second vanes 210 and 220 in the negative rotation direction. In this embodiment, the oil chamber in which the spring unit 300 is provided is defined as an advance oil chamber. The spring unit 300 may be provided in the retarded oil chamber without any particular limitation.

  The spring unit 300 is formed by two first and second coil springs 310 and 320 and holder members 330 provided at both axial ends of the coil springs. The first and second coil springs 310 and 320 are identically attached. It is provided in the power. Also, grooves 112, 212, and 222, which are recesses penetrating in the x-axis direction, are provided on the side surfaces 111, 211, and 221 of the advance oil chamber side of the shoe 110 and the first and second vanes 210, 220, respectively, and the holder member The movement of 330 in the radial direction is restricted.

  At the time of assembly, the spring unit 300 is inserted into the advance oil chamber from the negative direction of the x-axis, and the holder member 330 is engaged with each of the grooves 112, 212, and 222 for assembly. That is, two first and second coil springs 310 and 320 are provided in one advance oil chamber, and the first and second coil springs 310 and 320 are parallel to the rotation direction of the VTC 1 and in the x-axis. It is provided symmetrically. Therefore, the urging force of the spring unit 300 acts in the rotation direction of the VTC 1. In the present embodiment, there are two coil springs provided in one spring unit 300, but there may be three or more, and there is no particular limitation.

  In addition, as described above, the second vane 220 is provided with the x-axis direction through hole 223, and the lock pin 21 is slidable in the x-axis direction. The lock pin 21 is fitted with a spring 23 and a retainer 22 and is urged in the positive x-axis direction. Further, the sprocket 30 is provided with a sleeve locking portion 31 that restricts the sleeve 11 in the positive x-axis direction, and the sleeve 11 is locked in contact with the sprocket 30 at the sleeve locking portion 31.

  When assembling, the vane rotor 20 is first inserted into the housing 10, the lock pin 21 is inserted into the x-axis direction through hole 223, and the spring 23 and the retainer 22 are inserted into the lock pin 21. Next, the spring units 300 are respectively engaged with the four advance oil chambers, and the sprocket 30 is brought into contact with the housing 10 from the positive x-axis direction.

  At that time, the sleeve 11 and the sleeve locking portion 31 are brought into contact with the x-axis direction through hole 223 so as to be coaxial. Then, the front plate 60 is brought into contact with the housing 10 from the negative x-axis direction and fastened with bolts 61 so that the members are integrated. By forming the spring unit 300 from the two first and second coil springs 310 and 320 and the two holder members 330 provided at both axial end portions of each coil spring, the spring unit 300 is unitized and assembled easily. I am trying.

[VTC radial cross section]
FIG. 3 is a radial cross-sectional view at the most advanced angle position in the VTC 1, and FIG. 4 is a radial cross-sectional view at the most retarded angle position. As described above, each advance oil chamber 500 is provided with the spring unit 300 and biases the vane rotor 20 toward the negative direction rotation side.

  In FIG. 3, VTC 1 is in the most advanced state, and no hydraulic pressure is acting on the advance and retard oil chambers 500, 600, or the sum of the operating oil pressure of the advance oil chamber 500 and the urging force of the spring unit 300 is The operating oil pressure of the retarded oil chamber 600 is greater than that. In this advanced angle state, the housing 10 is urged in the positive rotation direction and the vane rotor 20 is urged in the negative rotation direction, so that the volume of the advance oil chamber 500 is maximized and the volume of the retard oil chamber 600 is minimized. Thus, VTC1 is in the most advanced state.

  In FIG. 4, VTC 1 is the most retarded state, and the operating oil pressure of the retarding oil chamber 600 is greater than the sum of the operating oil pressure of the advanced oil chamber 500 and the urging force of the spring unit 300. In this retarded state, the housing 10 is biased in the negative rotation direction and the vane rotor 20 is biased in the positive rotation direction, so that the volume of the retard oil chamber 600 is maximized and the volume of the advance oil chamber 500 is minimal. Thus, VTC1 is in the most retarded state.

[Details of spring unit]
FIG. 5 is a perspective view of the spring unit 300. As described above, the spring unit 300 includes the first and second coil springs 310 and 320 and the holder member 330. The first and second coil springs 310 and 320 are fitted and held with the holder member 330 at both ends. Yes. In the first embodiment of the present application, the first and second coil springs 310 and 320 have the same diameter and the same length and are provided so that the winding directions are opposite to each other. do not do. Further, three or more coil springs may be provided without any particular limitation.

  The holder member 330 is a rectangular member formed by processing a metal thin plate, and the short side is bent inward by bending. The processing method is press processing from the viewpoint of weight reduction and cost reduction, and is formed of a material harder than the sprocket 30 and the front plate 60. In addition, two protrusions 331 that are cylindrical and protrude perpendicularly in the same direction are provided, and the protrusions 331 are provided with a diameter that allows the first and second coil springs 310 and 320 to be fitted.

  At the time of assembly, the first and second coil springs 310 and 320 are vertically fitted to the holder member 330 by fitting the protruding portion 331 to both ends of the first and second coil springs 310 and 320, respectively. In this configuration, the coil springs are prevented from contacting each other as much as possible when compressed, and the durability is improved. Note that the holder member 330 may be molded by a mold, and may be formed of a resin without any particular limitation.

[Details of holder member]
6 is a perspective view of the holder member 330 according to the first embodiment, FIG. 7 is a cross-sectional view, and FIG. 8 is a front view. As described above, the holder member 330 is formed by pressing a metal plate that is harder than the sprocket 30 and the front plate 60, and is provided with two projecting portions 331 that are hollow cylindrical and project vertically in the same direction. By making the protruding portion 331 hollow, the protruding portion 331 is easily protruded to ensure ease of processing. The protrusion 331 is provided with a diameter that allows the first and second coil springs 310 and 320 to be fitted.

  Further, the short side of the holder member 330 extends in a predetermined width in the axial direction, and forms a sliding portion 332 as an extending portion bent inward (spring side). The sliding portion 332 has elasticity, and an R is formed between the bottom surface 333 and the sliding portion 332 in accordance with press working. By pressing, the angle θ between the bottom surface portion 333 and the sliding portion 332 is set to 90 ° or less. In Example 1, the value of θ is a right angle of 90 °, but it is not particularly limited as long as it is 90 ° or less.

  In addition, in Example 1, although R was provided between the bottom face 333 and the sliding part 332, a taper surface may be provided and it does not specifically limit. Further, in the first embodiment, the supply / discharge hole 337 for supplying and discharging the hydraulic oil is provided on the bottom surface 333. However, the supply / discharge hole 337 is not particularly limited.

[Assembly of holder member to vane rotor]
FIG. 9 is a perspective view of the vane rotor 20 to which the holder member 330 is assembled. When assembling, the long side of the holder member 330 is engaged with the grooves 212 and 222 for assembling. Even when the holder member 330 moves to the outer peripheral side of the vane rotor 20 by the urging force of the springs 310 and 320, the holder member 330 is configured to avoid sliding with the housing 10 by engaging with the grooves 212 and 222 of the vane rotor 20. ing.

  Further, since the sliding portion 332 is assembled perpendicularly to the x-axis in FIG. 3, that is, the rotation axis of the VTC 1, the holder member 330 is engaged with at least the grooves 212 and 222 on the side surfaces 211 and 221 of the advanced oil chamber of the vane rotor 20. The sliding portion 332 provided at the end in the x-axis direction is slidable in the x-axis direction, and the first and second coil springs with respect to the sprocket 30 and the front plate 60 serving as sliding surfaces. The end portions 335 are bent at a predetermined width on the 310, 320 side. R is formed between the end portion 335 and the sliding portion 332 by performing bending by pressing. In the first embodiment, R is used, but the taper may be formed by other processing means.

[Contamination retention by sliding part]
10 is a cross-sectional view taken along line AA in FIG. When the VTC 1 operates, the holder member 330 also rotates relative to the housing 10 as the vane rotor 20 rotates, and the holder member 330 is axially moved along the grooves 212 and 222 by the urging forces of the first and second coil springs 310 and 320. Moving. Along with this, the sliding portion 332 slides in contact with the sprocket 30 and the front plate 60 provided at the axial end of the housing 10, and contamination is caused by sliding between the sliding portion 332, the sprocket 30 and the front plate 60. (Wear powder) occurs.

  At this time, the contamination is held by R formed between the bottom surface 333 of the holder member 330 and the sliding portion 332, and the oil pump 4 and the hydraulic actuator which are the hydraulic oil and fluid supply / discharge means supplied into the VTC 1 It is provided so that the diffusion of contamination to 5 etc. is suppressed. Further, by providing R, the surface pressure during sliding is reduced, and the volume for holding the contamination is enlarged to ensure the slidability and the contamination collecting property.

  Here, since the sliding portion 332 has elasticity, when the contamination staying in the taper portion 334 increases, the sliding portion 332 elastically deforms, and the volume for holding the contamination increases to increase the holding amount and elastic deformation during sliding. By doing so, the sliding load of each member on the sliding surface is reduced.

  Further, since the holder member 330 is formed of a metal plate that is harder than the sprocket 30 and the front plate 60 that are sliding surfaces, the holder member 330 wears when sliding by the urging force from the springs 310 and 320. Reduced to ensure durability.

  Further, the sliding portion 332 is bent toward the inner side of the holder member 330. When sliding, the sliding portion 332 contacts the sprocket 30 and the front plate 60 at the sliding portion 332, and the sprocket 30 and the front plate at the end portion 335. 60 does not abut. Therefore, even if the holder member 330 abuts and slides on the sprocket 30 and the front plate 60, the burden on each member on the sliding surface is reduced, and wear of each member is reduced by achieving smooth sliding. It has a configuration.

[Contrast of the effects of the conventional example and the embodiment of the present application]
Conventionally, in the valve timing control device, when the engine is stopped, the vane rotor is biased by providing a coil spring in the working chamber in order to set the valve timing to a phase where the engine can be restarted. At that time, in order to ensure the ease of assembly of the spring, a holder member for holding the spring is provided at both ends of the spring, and a spring unit in which the holder member and the spring are integrated is inserted from the axial direction into the axial groove in the working chamber. ing.

  However, in the above prior art, the holder member also moves as the spring expands and contracts, so that the holder member moves in the axial direction along the axial groove in the working chamber. Therefore, there is a problem that the sprocket and plate provided at the axial end of the housing and the holder member slide to cause contamination and reduce the operation response and durability.

  On the other hand, in the first embodiment of the present invention, the first and second vanes 210 and 220 and the shoe are disposed in the advance and / or retard oil chambers 300 and 400 formed by being separated by the housing 10 and the vane rotor 20. A plurality of spring units 300 provided in each one of the advance and / or retard oil chambers 300 and 400 so that the urging force acts in a direction in which the 110 separates from each other, The holder member 330 is configured to hold the first and second coil springs 310 and 320. The holder member 330 is provided in the x-axis direction grooves 212 and 222 on the advance oil chamber side surfaces 211 and 221 of the first and second vanes 210 and 220 so as to be slidable at least in the x-axis direction. Both side end portions in FIG. 3 have sliding portions 332 bent toward the first and second coil springs 310 and 302 side.

  Thereby, the sliding surface of the holder member 330, the sprocket 30, and the front plate 60 is the curved surface portion 336, so that the burden on each member on the sliding surface is reduced and smooth sliding can be achieved. Therefore, it is possible to provide a valve timing control device for an internal combustion engine that suppresses the occurrence of contamination and improves the operation responsiveness and durability (corresponding to claim 1).

  Further, the short side of the holder member 330 has an extending portion extending a predetermined width in the axial direction, and this extending portion is bent inward (spring side) to form a sliding portion 332. R is provided between the sliding portion 332 and the bottom surface 333, and the angle θ of the sliding portion 332 with respect to the bottom surface 333 of the holder member 330 is formed to be 90 ° or less.

  As a result, even if a slight amount of contamination occurs, it is possible to hold the contamination by the taper portion 334, and to the hydraulic oil supplied to the VTC 1 and the oil pump 4 and the hydraulic actuator 5 as fluid supply / discharge means. Diffusion of contamination can be suppressed (corresponding to claim 2).

  A second embodiment will be described with reference to FIGS. Since the basic configuration is the same as that of the first embodiment, only different points will be described. In the first embodiment, the short side of the holder member 330 is bent inward by pressing to form a sliding portion 332 having a curved surface portion 336, and radial movement is restricted by the grooves 212 and 222 provided in the axial direction. .

  On the other hand, in Example 2, the short side sliding part 332a that bends toward the first and second springs 310 and 320 by bending the short side and the long side of the holder member 330a by the press, and the long side sliding The second embodiment is different from the first embodiment in that a portion 338a is formed and is slidably contacted with the housing 10 at the long side sliding portion 338a on the radially outer side to restrict radial movement.

  11 is a perspective view of a holder member 330a according to the second embodiment, FIG. 12 is a side view, and FIG. 13 is a front view and a BB cross-sectional view. As described above, the holder member 330a according to the second embodiment is subjected to bending by pressing on both the short side and the long side, thereby forming the short side sliding portion 332a and the long side sliding portion 338a. As in the first embodiment, the holder member 330a is provided with a protrusion 331a to hold the first and second coil springs 310 and 320. The bottom surface 333a is provided with a hydraulic oil supply / discharge hole 337a, but is not particularly limited.

  The short side sliding portion 332a is bent by a press with a predetermined width in the same manner as in the first embodiment, and an R is formed between the bottom surface 333a and an angle φ with respect to the bottom surface 333a is set to 90 ° or less. A short side taper portion 336a is formed. Further, due to the urging force of the first and second coil springs 310 and 320 in the spring unit 300, the short side sliding portion 332a slides in contact with the sprocket 30 and the front plate 60. At the time of sliding contact, sliding contact is made at the shortest side end 334a.

  On the other hand, the long side sliding portion 338a is also bent by a press with a predetermined width, and an R is formed between the bottom surface 333a and an angle φ with respect to the bottom surface 333a is set to 90 ° or less so that the long side taper is formed. A portion 339a is formed. When the holder member 330a is about to move radially outward by the urging force of the first and second coil springs 310 and 320, the inner periphery of the housing 10 at the longest side end 335a of the long side sliding portion 338a. The surface and the holder member 330a are in sliding contact, and the holder member 330a is restricted from moving radially outward.

[Contamination retention in Example 2]
FIG. 14 is a perspective view of the vane rotor 20a assembled with the holder member 330a according to the second embodiment. In the first embodiment, the radially outer side of the holder member 330 is locked by the groove portions 212 and 222 provided in the vane rotor 20, but the groove portion is not provided in the vane rotor 20a of the second embodiment, and the holder member 330a. The long-side sliding portion 338a is brought into contact with the inner peripheral surface of the housing 10 to lock the radial movement of the holder member 330a.

  During the operation of the VTC 1, the holder member 330a moves in the axial direction and the radial direction by the urging force of the first and second coil springs 310 and 320. Accordingly, the short-side sliding portion 332a slides in contact with the sprocket 30 and the front plate 60 provided at the axial end of the housing 10 as in the first embodiment. The long side sliding portion 338a slides with the inner peripheral surface of the housing 10, and contamination occurs near the short side and the long side sliding portions 332a and 338a.

  At that time, contamination is retained by R formed between the bottom surface 333 of the holder member 330 and the short side and long side sliding portions 332a and 338a, and the hydraulic oil and fluid supply / discharge in the VTC 1 are retained. It is provided so that the diffusion of contamination to the oil pump 4 and the hydraulic actuator 5 which are means is suppressed. Further, by providing the short side and long side taper portions 336a and 339a, the short side sliding portion 332a and the sprocket 30 or the front plate 60, and the long side sliding portion 338a and the housing 10 are provided. A region where contamination is held is formed between the periphery and the diffusion is suppressed.

  In addition, the long side sliding portion 338a bent toward the springs 310 and 320 also has an angle ψ with respect to the bottom surface 333a of 90 ° or less, and is applied by the urging force of the first and second coil springs 310 and 320. When the holder member 330a moves in the radial direction, the inner peripheral surface of the housing 10 and the holder member 330a are in sliding contact with each other at the longest side end 335a of the long side sliding portion 338a, thereby achieving smooth sliding. ing.

[Effects of Example 2]
In the second embodiment, both the short side and the long side of the holder member 330a are bent by pressing to provide a short side sliding portion 332a and a long side sliding portion 338a. R is formed between the long side sliding portions 332a and 338a and the bottom surface 333a. Further, the short side sliding part 332a and the long side sliding part 338a are provided with angles φ and ψ with respect to the bottom surface 333a of 90 ° or less, respectively, and are bent by a press with a predetermined width, and the short side side and long side The side taper surfaces 336a and 339a are formed.

  Further, when the holder member 330a attempts to move outward in the radial direction by the urging force of the first and second coil springs 310, 320 in the spring unit 300, the longest side end 335a of the long side sliding portion 338a. , The inner peripheral surface of the housing 10 and the holder member 330a are in sliding contact, and the holder member 330a is restricted from moving radially outward.

  As a result, the contamination generated in the vicinity of the holder member 330a can be held in the R formed between the bottom surface 333 of the holder member 330 and the short side and long side sliding portions 332a and 338a. It is possible to suppress the diffusion of contamination into the hydraulic oil supplied to the inside and the oil pump 4 and the hydraulic actuator 5 which are fluid supply / discharge means. Further, by providing the short side and long side taper surfaces 336a and 339a, the short side sliding portion 332a and the sprocket 30 or the front plate 60, and the long side sliding portion 338a and the housing 10 are provided. Contamination can also be held in a region formed between the periphery.

  Further, when the holder member 330a is moved in the radial direction by the urging force of the first and second coil springs 310 and 320, the inner peripheral surface of the housing 10 at the longest side end 335a of the long side sliding portion 338a. The holder member 330a can be brought into sliding contact, and smooth sliding can be performed.

  A third embodiment will be described with reference to FIGS. Since the basic configuration is the same as that of the first embodiment, only different points will be described. In the first embodiment, the holder member 330 is locked in the axial grooves 112, 212, and 222 provided in the shoe 110 and the vane rotor 20 to restrict the radial movement.

  On the other hand, in Example 3, the short side of the holder member 330b is bent in the direction opposite to the protruding portion 331b to provide a claw portion 332b, and the claw portion 332b is formed in the grooves of the first and second vanes 210b and 220b of the vane rotor 20. The axial direction locking portions 213b and 223b provided at 212b and 222b are locked to restrict the axial movement of the holder member 330b, and the holder member 330b, the sprocket 30 and the front plate 60 are maintained in a non-contact state. This is different from the first embodiment.

  15 is a perspective view of the holder member 330 according to the third embodiment, FIG. 16 is a longitudinal sectional view, and FIG. 17 is a front view. As described above, the short side of the holder member 330b is bent in the direction opposite to the protruding portion 331b, and the claw portion 332b (fixed portion) is provided. Similar to the first embodiment, the holder member 330b of the third embodiment is also formed by pressing.

  18 is a perspective view when the holder member 330b of Example 3 is assembled to the vane rotor 20b, FIG. 19 is a partial cross-sectional view taken along the line DD of FIG. 18, and FIG. 20 is an axial front view. The holder member 330b is engaged with the first and second vanes 210b and 220b in the claw portion 332b. As shown in FIG. 19, the first and second vanes 210b and 220b are provided with axial locking portions 213b and 223b, and the first and second vanes 210b and 220b are holders in the axial locking portions 213b and 223b. Engage with the claw portion 332b of the member 330b to lock the axial movement. As shown in FIG. 20, the holder member 330b is also restricted from moving in the radial direction by the grooves 212b and 222b.

[Operational effects in Example 3]
In the third embodiment, the claw portion 332b is provided by bending the short side of the holder member 330b in the direction opposite to the protruding portion 331b, and the claw portion 332b is a groove of the first and second vanes 210b and 220b of the vane rotor 20. It was decided to be locked to the axial direction locking portions 213b and 223b provided at 212b and 222b. The holder member 330b is also restricted from moving in the radial direction by the grooves 212b and 222b.

  As a result, the holder member 330b, the sprocket 30 and the front plate 60 can be maintained in a non-contact state, and the occurrence of contamination is suppressed by avoiding sliding between the members, and the operation response and durability are also achieved. It is possible to provide a valve timing control device for an internal combustion engine that improves the above (corresponding to claim 3).

  Further, by locking the holder member 330b with the axial locking portions 213b and 223b provided in the grooves 212b and 222b, it is possible to simultaneously lock in the radial direction in addition to the axial direction. It is possible to stabilize the position and further improve the operation responsiveness of the VTC 1 and the durability of the holder member 330b.

[Other embodiments]
The best mode for carrying out the present invention has been described based on the first to third embodiments. However, the specific configuration of the present invention is not limited to each embodiment, and the gist of the invention is described. Any design change within a range that does not deviate from the above is included in the present invention.

  In the first embodiment, the short side of the holder member 330 is bent inward by a press bending process to form a sliding portion 332, and the holder member 330, the sprocket 30 and the front plate 60 are slid to each member on the sliding surface. In the case where the contamination occurs, the contamination is maintained in R provided between the sliding portion 332 and the bottom surface 333. It may be a thing.

  For example, as shown in FIGS. 21 to 23, the holder member 330c may be formed by molding, and a tapered surface 334c may be provided on the short side. The convex portion 336c formed between the tapered surfaces 334c is slidably brought into sliding contact with the sprocket 30 and the front plate 60, and the contamination is retained on the tapered surface 334c. An effect can be obtained.

  Further, technical ideas other than the claims that can be grasped from the above embodiments will be described below together with the effects thereof.

(A) A rotation transmission member that transmits rotation from a crankshaft of an internal combustion engine, a housing body that is fixed to one of the rotation transmission member or the camshaft and that has an opening at least on one end side in the axial direction, and an opening of the housing body A housing constituted by at least one plate for sealing
A shoe in which a working chamber is defined by projecting to the inner peripheral side of the housing body;
A vane rotor fixed to the other of the rotation transmission member or the camshaft and having a vane protruding in a radial direction and disposed in the housing;
A retard oil chamber and an advance oil chamber formed by separating the working chamber by the vane rotor;
Fluid supply / discharge means for supplying and discharging oil to and from the retard oil chamber and the advance oil chamber;
A coil spring that is disposed in the retard oil chamber and / or the advance oil chamber and that exerts a biasing force in a direction in which the vane and the shoe are separated from each other;
A holder member provided to hold the coil spring;
In a valve timing control device for an internal combustion engine having
The holder member is provided on the circumferential side surface of the vane so as to be slidable at least in the rotation axis direction, and both end portions in the rotation axis direction have tapered portions having an angle of 90 ° or less with respect to the sliding surface. A valve timing control device for an internal combustion engine, comprising:

(B) In the valve timing control device for an internal combustion engine according to claim 1 and (A),
The valve timing control device for an internal combustion engine, wherein the holder member has an extending portion having a predetermined width extending in a circumferential direction from the sliding portion.

  Even if a slight contamination occurs when the sliding portion slides, the contamination stays in the extending portion, so that the contamination does not flow into the working chamber or the fluid supply / discharge means, thereby causing no trouble.

(C) In the internal combustion engine valve timing control device according to claim 2,
The valve timing control device for an internal combustion engine, wherein the holder member plastically deforms a plate material to form a holder member and a sliding portion.

  Since the holder member is also formed by plastic deformation of the plate member, weight reduction and cost reduction can be achieved.

(D) In the valve timing control device for an internal combustion engine according to claim 2 and (b) above,
The valve timing control device for an internal combustion engine, wherein the sliding portion has elasticity.

  When the amount of contamination staying in the sliding portion increases, the sliding portion elastically deforms, so that more contamination can be retained.

(E) In the valve timing control device for an internal combustion engine according to (c),
The valve timing device for an internal combustion engine, wherein the holder member of the holder member is formed in a hollow cylindrical shape inside.

  By making the inside hollow, the holder member can be projected easily and reliably.

(F) In the valve timing control apparatus for an internal combustion engine according to any one of claims 1 and 2, or the above (a) to (e), the holder member is formed on a circumferential side surface of the vane. A valve timing device for an internal combustion engine, wherein the valve timing device is disposed in a recess penetrating in the direction of the rotation axis.

  By avoiding the holder member from moving to the outer peripheral side by the biasing force of the spring, sliding between the longitudinal side surface of the holder member and the housing can be prevented.

(G) In the valve timing control apparatus for an internal combustion engine according to claim 1,
The valve timing device for an internal combustion engine, wherein the holder member is disposed on the outermost peripheral side of the side surface in the circumferential direction of the vane, and a sliding portion having a curved surface is formed in the longitudinal direction.

  Even if the holder member moves to the outer peripheral side by the urging force of the spring, the sliding portion made of a curved surface slides, so that the sliding between the housing and the holder member can be performed smoothly.

(H) In the valve timing control device for an internal combustion engine according to (b) above,
The holder member is disposed on the outermost peripheral side of the side surface in the circumferential direction of the vane, and a sliding portion including a tapered portion having an angle of 90 ° or less with respect to the sliding surface is formed in the longitudinal direction. A valve timing control device for an internal combustion engine.

(I) In the valve timing control device for an internal combustion engine according to claim 2,
The holder member is disposed on the outermost peripheral side of the circumferential side surface of the vane, and a sliding portion having a predetermined width is formed in the longitudinal direction and is bent toward the spring side with respect to the sliding surface. A valve timing control device for an internal combustion engine.

(Nu) In the valve timing control apparatus for an internal combustion engine according to any one of claims 1 to 3 or (a) to (h) above,
The valve timing device for an internal combustion engine, wherein the holder member is also provided between a circumferential side surface of the shoe and the spring.

  The holder member and the spring can be attached in a united state, and the ease of assembly is improved.

(L) In the valve timing control apparatus for an internal combustion engine according to claim 1 or (i) to (nu),
The valve timing control device for an internal combustion engine, wherein the holder member is made of a material harder than the vane or the housing.

  When receiving a load from the spring, the wear of the holder member can be reduced to improve the durability.

(V) In the valve timing control device for an internal combustion engine according to claim 3,
The valve timing control device for an internal combustion engine, wherein the fixing portion is a claw portion extending in a direction opposite to a protruding portion that holds the spring.

  The fixing portion can be easily formed and the axial movement of the holder member can be reliably regulated.

It is a figure showing the structure of the valve timing control apparatus containing the side sectional drawing at the time of engine starting in the valve timing control apparatus of Example 1. FIG. 1 is an exploded perspective view of a valve timing control device in Embodiment 1. FIG. FIG. 3 is a radial cross-sectional view at the most advanced angle position of the valve timing control device according to the first embodiment. FIG. 3 is a radial cross-sectional view at the most retarded position of the valve timing control device according to the first embodiment. 3 is a perspective view of a spring unit in Embodiment 1. FIG. 3 is a perspective view of a holder member in Embodiment 1. FIG. 2 is a cross-sectional view of a holder member in Embodiment 1. FIG. 6 is a front view of a holder member in Embodiment 1. FIG. It is a perspective view of the vane rotor which assembled | attached the holder member in Example 1. FIG. It is AA sectional drawing in FIG. It is a perspective view of the holder member in Example 2. FIG. It is a side view of the holder member in Example 2. It is the front view and BB sectional drawing of the holder member in Example 2. FIG. It is a perspective view of the vane rotor which assembled | attached the holder member in Example 2. FIG. 10 is a perspective view of a holder member in Embodiment 3. FIG. 6 is a longitudinal sectional view of a holder member in Embodiment 3. FIG. 10 is a front view of a holder member in Embodiment 3. FIG. It is a perspective view at the time of attaching the holder member of Example 3 to a vane rotor. It is a fragmentary sectional view in the DD cross section of FIG. It is a front view at the time of assembling the holder member of Example 3 to a vane rotor. It is a figure which shows the other Example of the valve timing control apparatus of this application internal combustion engine. It is a figure which shows the other Example of the valve timing control apparatus of this application internal combustion engine. It is a figure which shows the other Example of the valve timing control apparatus of this application internal combustion engine.

Explanation of symbols

1 Valve Timing Control Device 2 Camshaft 3 Cam Bolt 4 Oil Pump 5 Hydraulic Control Actuator 6 Controller 7 Hydraulic Supply Block 10 Housing 11 Sleeve 20 Vane Rotor 21 Lock Pin 22 Retainer 23 Spring 30 Sprocket 31 Sleeve Locking Portion 40 Seal 41 Seal Spring 50 Seal 60 Front plate 61 Bolt 110 Shoe 111 Advance side oil chamber side surface 112, 212, 222 Groove 120 Coil spring 210 First vane 220 Second vane 223 Axial through hole 230 Rotor unit 300 Spring unit 310 First coil spring 320 Second Coil spring 330 Holder member 331 Protruding portion 332 Sliding portion 333 Bottom surface 335 End portion 337 Supply / exhaust hole 500 Advance oil chamber 600 Delay oil chamber

Claims (3)

A rotation transmission member for transmitting rotation from a crankshaft of the internal combustion engine;
A housing constituted by a housing body fixed to one of the rotation transmission member or the camshaft and having an opening on at least one axial end, and at least one plate for sealing the opening of the housing body;
A shoe in which a working chamber is defined by projecting to the inner peripheral side of the housing body;
A vane rotor fixed to the other of the rotation transmission member or the camshaft and having a vane protruding in a radial direction and disposed in the housing;
A retard oil chamber and an advance oil chamber formed by separating the working chamber by the vane rotor;
Fluid supply / discharge means for supplying and discharging oil to and from the retard oil chamber and the advance oil chamber;
A coil spring that is disposed in the retard oil chamber and / or the advance oil chamber and that exerts a biasing force in a direction in which the vane and the shoe are separated from each other;
A holder member configured to be able to hold the coil spring, and provided on the circumferential side surface of the vane so as to be slidable at least in the rotational axis direction, and having both end portions in the rotational axis direction having sliding portions formed of curved surfaces; ,
A valve timing control device for an internal combustion engine, comprising: A rotation transmission member for transmitting rotation from a crankshaft of the internal combustion engine;
A housing constituted by a housing body fixed to one of the rotation transmission member or the camshaft and having an opening on at least one axial end, and at least one plate for sealing the opening of the housing body;
A shoe in which a working chamber is defined by projecting to the inner peripheral side of the housing body;
A vane rotor fixed to the other of the rotation transmission member or the camshaft and having a vane protruding in a radial direction and disposed in the housing;
A retard oil chamber and an advance oil chamber formed by separating the working chamber by the vane rotor;
Fluid supply / discharge means for supplying and discharging oil to and from the retard oil chamber and the advance oil chamber;
A coil spring that is disposed in the retard oil chamber and / or the advance oil chamber and that exerts a biasing force in a direction in which the vane and the shoe are separated from each other;
The coil spring is configured to be able to hold, and is provided on the side surface in the circumferential direction of the vane so as to be slidable at least in the rotational axis direction, and both end portions in the rotational axis direction are bent toward the spring side with respect to the sliding surface. A valve timing control device for an internal combustion engine having a holder member having a sliding portion of a predetermined width,
The valve timing device for an internal combustion engine, wherein the sliding portion of the holder member is bent at an angle of 90 ° or less with respect to the sliding surface. A rotation transmission member for transmitting rotation from a crankshaft of the internal combustion engine;
A housing constituted by a housing body fixed to one of the rotation transmission member or the camshaft and having an opening on at least one axial end, and at least one plate for sealing the opening of the housing body;
A shoe in which a working chamber is defined by projecting to the inner peripheral side of the housing body;
A vane rotor fixed to the other of the rotation transmission member or the camshaft and having a vane protruding in a radial direction and disposed in the housing;
A retard oil chamber and an advance oil chamber formed by separating the working chamber by the vane rotor;
Fluid supply / discharge means for supplying and discharging oil to and from the retard oil chamber and the advance oil chamber;
A coil spring that is disposed in the retard oil chamber and / or the advance oil chamber and that exerts a biasing force in a direction in which the vane and the shoe are separated from each other;
A holder member that is configured to be able to hold the coil spring and is provided so as to be insertable on a circumferential side surface of the vane, and having a fixing portion in which both end portions in the rotation axis direction maintain a non-contact state with the housing;
A valve timing apparatus for an internal combustion engine, comprising:

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