JP2009108705A - Valve timing adjusting device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a valve timing adjusting device, capable of improving productivity, and restricting deterioration of durability and generation of abnormal noise. <P>SOLUTION: A first rotator includes a first facing part and a second facing part that face each other in a rotational axis direction, and a second rotator includes a projected part projected in the rotational diameter direction. Between the first facing part and the second facing part, the projected part of the second rotator, a link mechanism part, and a planetary gear mechanism part are held in this order. The first facing part is disposed to face a first end part in the rotational axis direction on the counter-link mechanism part side in the projected part. The second facing part is disposed to face a second end part in the rotational axis direction on the counter-link mechanism part side in the planetary gear mechanism part. On either of the first facing part and the second facing part, a gap adjusting member is provided to project in the rotational axis direction toward the end part corresponding to the facing part. The gap adjusting member provides a gap between the facing part and the end part without getting in touch with the facing part or the end part, so that the gap is adjustable from the external. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a valve timing adjusting device that adjusts the valve timing of at least one of an intake valve and an exhaust valve whose camshaft opens and closes by torque transmission from a crankshaft in an internal combustion engine.

  2. Description of the Related Art Conventionally, there has been known a valve timing adjusting device that includes a first rotating body and a second rotating body that rotate in conjunction with a crankshaft and a camshaft of an internal combustion engine, respectively, and that adjusts valve timing based on the relative phase between the rotating bodies. Yes.

  As such a valve timing adjusting device, a guide rotating body having a guide groove, a link mechanism portion having a first link and a second link sharing a movable shaft guided in the guide groove, and the link mechanism portion A planetary gear mechanism having an electric motor for generating a control torque for actuating the link pair of the link and a planetary gear, and driving the guide rotator by transmitting the control torque to the guide rotator of the link mechanism Is disclosed in Patent Document 1. In the apparatus disclosed in Patent Document 1, the guide rotating body is rotated by the control torque generated in the electric motor, and the first link and the second link are moved by the movement of the movable shaft guided in the guide groove according to the rotation. The link operation is performed to adjust the relative phase between the first and second rotating bodies that determine the valve timing.

Further, in this type of valve timing adjusting device, the link mechanism portion and the planetary gear mechanism portion are housed inside the device, so that the constituent members of the link mechanism portion and the planetary gear mechanism portion are lubricated with the lubricating oil introduced into the device. Lubricate.
JP 2005-48707 A

  By the way, in the apparatus disclosed in Patent Document 1, the constituent members of the link mechanism section and the planetary gear mechanism section are arranged in order in the rotation axis direction inside the apparatus. In such a configuration, it is necessary to set a clearance in order to make the movement of these constituent members smooth. However, if the clearance is excessive, there is a possibility that wear or noise may occur due to collision between adjacent constituent members.

  As a countermeasure, the inventor provides a first component member arranged in order in the rotation axis direction in the link mechanism unit and a second component member arranged in sequence in the rotation axis direction in the planetary gear mechanism unit. It is considered to arrange a separating member between specific constituent members adjacent to each other among the first constituent member and the second constituent member. By arranging the separating member, the clearance on the first component member side of the link mechanism portion and the clearance on the second component member side of the planetary gear mechanism portion are separated.

  In the technology for separating the clearances corresponding to the link mechanism unit and the planetary gear mechanism unit in the device, the inventor conducted further earnest studies. As a result, the following problems were found. The problem is that excessive clearance can be suppressed, but depending on the level of noise suppression required, the management of the clearance size may be indispensable. For example, the total of the above clearances is necessary for the suppression. In order to make the clearance less than or equal to the clearance, it is necessary to improve the processing accuracy of each component member, or to dispose a clearance adjustment member such as a washer for clearance adjustment on the side of each component member.

  As described above, machining each component member with high accuracy, and providing a gap adjusting member and adjusting the clearance by selecting the width in the rotation axis direction of the gap adjusting member to be incorporated are an increase in machining cost and assembly. There is a risk of reduced productivity.

  The present invention has been made in view of such circumstances, and an object of the present invention is to provide a valve timing adjusting device capable of improving productivity and reducing durability and suppressing abnormal noise generation. .

  In order to achieve the above object, the present invention comprises the following technical means.

That is, in the invention according to claims 1 to 9, in the valve timing adjusting device for an internal combustion engine that adjusts the valve timing of at least one of the intake valve and the exhaust valve whose camshaft opens and closes by transmission of driving torque from the crankshaft, A first rotating body that rotates in conjunction with one of the crankshaft and camshaft; a second rotating body that is housed in the first rotating body and rotates in conjunction with the other of the crankshaft and camshaft; A link mechanism unit that is accommodated in the rotating body and changes a relative phase between the first rotating body and the second rotating body by a link operation, and a gear unit that is accommodated in the first rotating body and provided in the first rotating body. A planetary gear mechanism that receives a control torque from the outside according to the driving torque and transmits the control torque to the link mechanism by performing a planetary movement while being fitted,
The first rotating body has a first facing portion and a second facing portion that face each other in a rotating shaft direction common to the second rotating body (hereinafter simply referred to as “rotating shaft direction”). Having a projecting portion that projects in the same rotational radial direction as the first rotating body (hereinafter simply referred to as “rotational radial direction”);
Between the first facing portion and the second facing portion, the projecting portion of the second rotating body, the link mechanism portion, and the planetary gear mechanism portion are sandwiched in this order, and the first facing portion is the anti-link mechanism at the projecting portion. The second opposing portion is disposed opposite to the second end portion in the rotational axis direction on the anti-link mechanism portion side in the planetary gear mechanism portion. And
In any one of the first facing portion and the second facing portion, a gap adjusting member that protrudes in the rotation axis direction toward the end corresponding to the facing portion is provided. A gap is provided between the facing part and the end part without contacting the end part, and the gap is adjusted from the outside.

  Thus, according to the first aspect of the present invention, the second rotating body, the link mechanism portion, and the planetary gear mechanism portion are accommodated in the first rotating body, and the first opposing portion and the second rotating body of the first rotating body are accommodated. A gap in the direction of the rotation axis (hereinafter simply referred to as “thrust clearance”) between the facing portion and the adjacent projecting portion, link mechanism portion, and planetary gear mechanism portion of the second rotating body that is a clamping element of the facing portion. ) Is formed.

  In addition, any one of the first facing portion and the second facing portion is in the direction of the rotation axis toward the end corresponding to the facing portion, that is, the end on the clamping element side adjacent to the facing portion. A protruding gap adjusting member is provided, and the gap adjusting member protruding in the rotation axis direction between the facing portion and the end portion as described above has a gap between the facing portion and the end portion without contacting the facing portion and the end portion. Since the clearance is adjusted by adjusting the clearance, the sum of the thrust clearances can be kept small by the clearance set between the facing portion and the end by the clearance adjustment member.

  According to the first aspect of the invention described above, the total sum of the thrust clearance lances formed by all the clamping elements of the projecting portion, the link mechanism portion, and the planetary gear mechanism portion of the second rotating body is suppressed to be small only by the gap adjusting member. The clearance size can be managed. Therefore, for example, there is no need to provide a separating member for separately managing the thrust clearance lances of the link mechanism unit and the planetary gear mechanism unit, and an intervening member to be inserted between adjacent ones, so that the clearance size is managed. It is possible to increase work productivity, and to reduce the durability due to wear and to suppress the generation of abnormal noise.

  According to the invention described in claims 2 to 4, the gap adjusting member includes a screwing portion that is screwed in the rotation axis direction of the facing portion with respect to the facing portion at the facing portion and the end portion provided with the gap. And a head portion in contact with the end portion, wherein the head portion is formed in a flat surface or a crowned curved surface.

  According to this, the said clearance gap which reduces the sum total of a thrust clearance lance by the screwing part (screw) of a clearance gap adjustment member can be adjusted easily. In addition, since the end surface of the head in contact with the end is formed into a flat surface or a crowned curved surface, the contact area is increased by effectively applying the end surface of the head to the end at the head and the end in contact with each other, The contact stress can be reduced. Therefore, it is possible to avoid wear of the head and the end contacting each other.

  Note that, for example, when thrust thrust of a planetary gear mechanism or the like due to planetary motion is transmitted to the head contacting the end through the end on the clamping element side, the end surface of the head may be deformed by contact stress. . The crowned curved surface is one in which the curved surface becomes flat due to deformation due to contact stress and increases the contact area.

  According to the invention described in claim 3, the facing portion has a fixing hole that is screwed together with the screwing portion, and a head receiving hole that is formed in a larger diameter than the fixing hole and receives the head. The gap adjusting member is screwed so that the end of the screwed portion opposite to the head is inserted toward the facing portion.

  According to this, the head is accommodated in the head accommodating hole having a diameter larger than that of the fixing hole that is screwed together with the threaded portion (screw), so that the screw common to the threaded portion is placed on the outer peripheral portion of the head. There is no need to form. Therefore, it is possible to avoid the occurrence of flash due to screw formation in the inner peripheral wall of the first rotating body, that is, the head receiving hole and the head of the opposing portion, and the structure of the head receiving hole and the head is less likely to remain. can do.

  According to the fourth aspect of the present invention, the gap adjusting member receives a screwing force from the outside at the end opposite to the head of the screwing portion, and reduces the amount of protrusion of the head from the facing portion. By adjusting, the gap is adjusted.

  According to this, it can be set as the structure which transmits a screwing force from the external side of a 1st rotary body to the edge part on the opposite side to the head of a screwing part. Therefore, it is possible to easily adjust the protrusion amount of the head protruding from the facing portion to the inner side (end portion side).

  According to the invention described in claim 5, it is preferable that the head is formed to have a larger diameter than the screwing portion. Thereby, the contact area of the head which contacts an edge part can be expanded easily.

  In the inventions according to claims 6 to 8, the link mechanism unit shares a guide rotating body having a guide groove and a movable shaft guided in the guide groove according to the rotation of the guide rotating body. A first link and a second link that adjust the relative phase by operating the link by movement of the first and second protrusions of the first rotating body, and a third end opposite to the second end in the planetary gear mechanism. The second link and the guide rotating body are sandwiched in this order between the end portions, and the first link is interposed between the first facing portion and the second link.

  Thus, according to the sixth aspect of the present invention, the guide rotating body, the first link, and the second link, which are constituent members in the link mechanism section, are the projecting portion of the first rotating body and the planetary gear that faces the projecting portion. Since the second link and the guide rotator are sandwiched in this order between the third end portions of the mechanism portion, and the first link is interposed between the first facing portion and the second link, the guide in the link mechanism portion is provided. The sum of the thrust clearances formed between adjacent ones of the rotating body, the first link, and the second link (hereinafter simply referred to as “the sum of the thrust clearances in the link mechanism”) is set by the gap adjusting member. It can be reduced by the gap between the facing part and the end part.

  According to the invention of claim 7, the first link shares the first series of connecting shafts with the first rotating body, and is connected to the first facing portion by the turning pair via the first series of connecting shafts. The link shares the second connecting shaft with the second rotating body, and is connected to the projecting portion by the turning pair via the second connecting shaft, and is connected to the first link by the turning pair via the movable shaft. And

  Thereby, a 1st link and a 1st opposing part can form an appropriate clearance between each other by connecting by the turning pair even via the 1st series connecting shaft. In addition, the second link and the projecting portion can be connected to each other by a turning pair via the second connecting shaft, so that an appropriate clearance can be formed between them. Furthermore, the first link and the second link can be connected to each other by a pair of turns via the movable shaft, so that an appropriate clearance can be formed between them. According to these, it is possible to suppress the occurrence of abnormal noise and the decrease in durability of the torque transmission member while smoothing the link operation of the first link and the second link and improving the valve timing adjustment responsiveness.

  According to the invention described in claim 8, the first rotating body is configured such that the guide rotating body, the first link, the second link, and the projecting portion are accommodated between the first facing portion and the second facing portion. It is characterized by having.

  In such an invention, the torque transmitting member is stretched over the first rotating body for torque transmission from the crankshaft, but the maximum relative displacement in the rotating shaft direction of the first rotating body with respect to the protrusion of the second rotating body. Since the amount is affected by the sum of the thrust clearances, depending on the maximum relative displacement amount, there is a concern that the torque transmission member may be deteriorated in durability such as breakage or wear.

  On the other hand, according to the invention described in claim 8, the first rotating body is less likely to be relatively displaced in the rotation axis direction with respect to the protruding portion of the second rotating body accommodated in the accommodating portion. It is possible to suppress a decrease in the durability of the torque transmission member that is stretched over the one rotating body.

  According to the ninth aspect of the present invention, the planetary gear mechanism is provided with torque generating means for generating a control torque, and the planetary gear mechanism unit is supported by the planetary carrier that is rotated by the control torque and the planetary gear that is supported by the planetary carrier so as to be freely planetary. The rotational movement of the planet carrier is decelerated by the planetary movement of the planetary gear, and torque is transmitted to the link mechanism.

  According to this, the planetary gear mechanism unit that rotates and transmits torque to the link mechanism unit decelerates the rotational motion of the planetary carrier by the planetary motion of the planetary gear and transmits torque to the link mechanism unit, so the rotational motion of the planetary carrier is This is done by receiving a relatively small control torque. Therefore, the thrust thrust of the planetary gear mechanism portion due to planetary motion can be kept small.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description is abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment.

(First embodiment)
1 to 6 show a valve timing adjusting device 1 according to a first embodiment of the present invention. The valve timing adjusting device 1 is mounted on a vehicle and installed in a transmission system that transmits engine torque from the crankshaft of the internal combustion engine to the camshaft 2. 4 and 5, the hatching representing the cross section is omitted.

  As shown in FIG. 3, the valve timing adjusting device 1 is formed by combining an electric unit 4, a mechanical unit 6, and the like. Here, in the present embodiment, the camshaft 2 opens and closes the intake valve of the internal combustion engine, and the valve timing adjusting device 1 adjusts the valve timing of the intake valve.

  The electric unit 4 includes an electric motor 21 and an energization control circuit 22. The electric motor 21 is, for example, a brushless motor or the like, and includes a motor case 23 fixed to the internal combustion engine and a motor shaft 24 supported by the motor case 23 so as to be rotatable forward and backward. The energization control circuit 22 includes a drive driver and a control microcomputer thereof, and is disposed outside and / or inside the motor case 23 and is electrically connected to the electric motor 21. The energization control circuit 22 controls the energization of the electric motor 21 to form a rotating magnetic field around the motor shaft 24 and generates a control torque in a direction corresponding to the rotating magnetic field on the motor shaft 24.

  The mechanical unit 6 includes a first rotating body 10, a second rotating body 18, a planetary gear mechanism unit 30, a link mechanism unit 50, and the like.

  3-5, the 1st rotary body 10 fastens the large diameter side edge part of the two-stage cylindrical sprocket 11, and the large diameter side edge part of the two-stage cylindrical cover member 12 by screwing. Become.

  The two-stage cylindrical sprocket 11 is connected between the large-diameter cylindrical portion 11b and the small-diameter cylindrical portion 11c with an annular plate-like portion (hereinafter referred to as a first annular plate-like portion). In these three outer wall elements, the link mechanism portion 50 is accommodated along the inner periphery of the large-diameter cylindrical portion 11b extending in the rotation axis direction. Here, the link mechanism unit 50 includes a guide rotating body 40 described later as a component.

  The two-stage cylindrical cover member 12 is connected between the large-diameter cylindrical portion 12b and the small-diameter cylindrical portion 12c with an annular plate portion (hereinafter referred to as a second annular plate-like portion) for the first rotation. It forms the other cylindrical outer wall of the body, and accommodates the planetary gear mechanism portion 30 along the inner periphery of the large-diameter cylindrical portion 12b extending in the direction of the rotation axis in these three outer wall elements.

  In the first rotating body, the first annular plate-like portion of the sprocket 11 and the second annular plate-like portion of the cover member 12 are opposed to each other in the direction of the rotation axis. A first facing portion 11a and a second facing portion 12a are formed by the plate-like portions, respectively. That is, in this embodiment, the 1st rotary body becomes a form where the hollow large diameter cylinder parts 11b and 12b were provided between the 1st opposing part 11a and the 2nd opposing part 12a.

  In addition, a plurality of teeth 16 are formed on the outer peripheral portion of the large-diameter cylindrical portion 11b formed by the sprocket 11 so that an annular timing chain 15 is spanned between the plurality of teeth of the crankshaft. Therefore, when the engine torque output from the crankshaft is transmitted to the sprocket 11 through the timing chain 15, the first rotating body 10 rotates in conjunction with the crankshaft while maintaining a relative phase with the crankshaft. . At this time, the rotation direction of the first rotating body 10 is the clockwise direction of FIGS.

  1-4, the 2nd rotary body 18 has the axial part 17 and a pair of protrusion part 19. As shown in FIG. The cylindrical shaft portion 17 is disposed concentrically with the first rotating body 10. One end portion of the shaft portion 17 is slidably and rotatably fitted to the inner peripheral side of the small-diameter cylindrical portion 11c, and is connected to one end portion of the coaxial cam shaft 2 by bolt fixing. As a result, the second rotating body 18 can rotate while maintaining the relative phase with the cam shaft 2 in conjunction with the cam shaft 2, and can rotate relative to the first rotating body 10. ing. The relative rotation direction in which the second rotating body 18 advances with respect to the first rotating body 10 is the direction X in FIGS. 4 to 7, and the second rotating body 18 is retarded with respect to the first rotating body 10. The relative rotation direction is the direction Y in FIGS.

  As shown in FIGS. 1 and 4, each projecting portion 19 of the second rotating body 18 is formed in a flat plate shape projecting outward in the rotational radial direction from two locations sandwiching the shaft portion 17 in the radial direction. Each protrusion 19 is accommodated in the large-diameter cylindrical portion 11b in a state adjacent to the first facing portion 11a in the rotation axis direction.

  As shown in FIGS. 1, 3, and 6, the planetary gear mechanism 30 includes a sun gear 31, a planet carrier 32, a planetary gear 33, and the like.

  The sun gear 31 formed of an external gear is concentrically riveted to the second facing portion 12 a formed by the cover member 12 and functions as a part of the first rotating body 10. That is, the sun gear 31 rotates in the clockwise direction of FIGS. 4 to 6 while maintaining a relative phase with the crankshaft in conjunction with the crankshaft.

  As shown in FIGS. 3 and 6, the planet carrier 32 has a cylindrical shape as a whole, and most of the planet carrier 32 is accommodated in the cover member 12. The planetary carrier 32 forms an input portion 35 by an inner peripheral surface portion concentric with the first rotating body 10 and the motor shaft 24. A fitting groove 36 is opened in the input portion 35, and the planetary carrier 32 is connected to the motor shaft 24 through a joint 37 that fits into the groove 36. Thereby, the planetary carrier 32 can rotate integrally with the motor shaft 24 that inputs the control torque to the input unit 35, and can rotate relative to the rotating bodies 10 and 18.

  The planet carrier 32 further forms an eccentric portion 38 by an outer peripheral surface portion that is eccentric with respect to the first rotating body 10 and the sun gear 31.

  As shown in FIGS. 1, 3, and 6, the planetary gear 33 is formed in an annular plate shape and includes an internal gear portion 39 having a predetermined number of teeth more than the sun gear 31. The planetary gear 33 is accommodated and disposed along the large-diameter cylindrical portion 12b in a state where the inner gear portion 39 is located on the outer peripheral side of the sun gear 31 and is eccentric with respect to the sun gear 31, and is opposite to the eccentric side. The internal gear 39 is engaged with the sun gear 31. The planetary gear 33 is fitted to the eccentric portion 38 of the planet carrier 32 via a bearing 34. As a result, the planetary gear 33 is supported by the planetary carrier 32 so as to be capable of planetary movement. Here, the planetary motion refers to a motion in which the planetary gear 33 revolves around the eccentric axis with respect to the sun gear 31 and revolves in the rotation direction of the planetary carrier 32.

  As shown in FIGS. 1, 3, and 5, the guide rotator 40 is formed in an annular plate shape, and between the outer peripheral portion of the planetary gear 33 and the second link 53 of the link mechanism portion 50 described later in the rotation axis direction. Are accommodated in the large-diameter cylindrical portion 11b concentrically with the rotating bodies 10 and 18 in a state of being sandwiched on the same axis. The guide rotator 40 is fitted on the outer peripheral side of the shaft portion 17 so as to be slidable and rotatable. As a result, the guide rotator 40 can rotate relative to the rotators 10 and 18.

  Such a guide rotator 40 is opposed to each of the opposing portions 11a and 12a with a spacing in the rotational direction between the first opposing portion 11a and the second opposing portion 12a. Together with the second facing portion 12a, the guide rotator 40 forms a third facing portion.

  The guide rotator 40 has a pair of guide grooves 44 that open to the opposite side of the planetary gear 33. Each guide groove 44 is provided so as to have a rotational symmetry of 180 degrees in the rotation direction of the rotating bodies 10, 18, 40. Each guide groove 44 is formed in a spiral shape that extends with a predetermined width and changes the distance from the center of the shaft portion 17 in the extending direction.

  As shown in FIGS. 1, 2, and 5, the guide rotator 40 further has a plurality of engagement holes 48 that open to the planetary gear 33 side. The engagement holes 48 are provided at equal intervals in the rotation direction of the rotating bodies 10, 18, 40, and each has a cylindrical hole shape. Correspondingly, the planetary gear 33 has a plurality of engaging protrusions 49 that protrude in a columnar shape from locations spaced equidistantly in the direction of rotation to the guide rotator 40 side. Each engagement protrusion 49 is individually loosely inserted into the corresponding engagement hole 48 and engaged therewith. The guide rotator 40 extracts the rotation motion of the planetary gear 33 by the engagement of the engagement protrusions 49 with the engagement holes 48, and realizes the rotation motion according to the rotation motion.

  In this embodiment in which the guide rotator 40 is linked to the planetary gear mechanism 30 in this way, when the planetary carrier 32 does not rotate relative to the first rotator 10, the planetary gear 33 does not perform a planetary motion and performs the first rotation. It rotates with the body 10, and each engagement protrusion 49 presses each engagement hole 48 to the rotation side. As a result, the guide rotator 40 rotates in the clockwise direction of FIG. 6 while maintaining a relative phase with the first rotator 10.

  When the planetary carrier 32 rotates relative to the first rotating body 10 in the direction X due to an increase in the control torque in the direction X or the like, the planetary gear 33 performs a planetary motion while changing the meshing teeth with the sun gear 31. The force with which each engagement protrusion 49 presses each engagement hole 48 to the rotation side increases. As a result, the guide rotator 40 rotates relative to the first rotator 10 in the direction X. On the other hand, when the planetary carrier 32 rotates relative to the first rotating body 10 in the direction Y due to the control torque increasing in the direction Y or the like, the planetary gear 33 performs planetary motion while changing the meshing teeth with the sun gear 31. Thereby, each engagement protrusion 49 presses each engagement hole 48 to the non-rotation side. As a result, the guide rotator 40 rotates relative to the first rotator 10 in the direction Y.

  As described above, in this embodiment, the planetary gear mechanism 30 decelerates the relative rotational motion of the planet carrier 32 relative to the first rotator 10 by the planetary motion of the planetary gear 33 and transmits it to the guide rotator 40. The rotating body 40 is driven to rotate relative to the first rotating body 10.

  As shown in FIGS. 1, 3, and 4, each set of link mechanism units 50 is a combination of two types of links 52 and 53, and is aligned at equal intervals in the rotational direction of the rotating bodies 10, 18, and 40. And accommodated in the large-diameter cylindrical portion 11b.

  In each set of link mechanism portions 50, the first link 52 is formed in an arc-shaped flat plate shape and has paired elements 60 and 61 at both ends, and is adjacent to the first facing portion 11a in the rotation axis direction. ing. As a result, the first link 52 of each set of link mechanism portions 50 is in a shape of being wrapped with each protruding portion 19 along the rotation axis direction.

  In the first link 52 of each pair of link mechanism portions 50, one pair of even elements 60 are fitted with a first connecting shaft 62 press-fitted and fixed to the first facing portion 11a so as to be relatively rotatable. The first link 52 is connected to the first facing portion 11a by a turning pair via the series connecting shaft 62. In addition, a movable shaft 56 that is press-fitted and fixed to the second link 53 of the link mechanism portion 50 of the same group is fitted to the other pair of elements 61 so as to be relatively rotatable. Thus, the first link 52 is connected to the second link 53.

  In each set of link mechanism portions 50, the second link 53 is formed in a ω-shaped flat plate shape and has paired elements 64, 65 in the middle portion, and the corresponding protrusions 19, the same set and other sets of links. The first link 52 of the mechanism unit 50 and the guide rotator 40 are adjacent to each other in the rotation axis direction. As a result, the first link 52 of each set of link mechanisms 50 is not only between the second link 53 and the first facing portion 11a of the same set, but also between the second link 53 and the first facing portion 11a of another set. Since it is arranged, the inclination at the time of link operation is suppressed.

  In the second link 53 of each pair of link mechanism portions 50, one pair of even elements 64 is fitted with a second connecting shaft 66 press-fitted and fixed to the corresponding projecting portion 19 so as to be relatively rotatable. The second link 53 is connected to the corresponding projecting portion 19 by a turning pair via the two connecting shafts 66. Further, as described above, a movable shaft 56 that rotates between the links 52 and 53 of the same pair of link mechanism portions 50 to form an even pair is press-fitted and fixed to the other kinematic element 65.

  As shown in FIGS. 3 and 5, the movable shaft 56 shared by the first link 52 and the second link 53 in each pair of link mechanism portions 50 is inserted into the corresponding guide groove 44 in the direction of the rotation axis. The guide rotator 40 is connected to the guide rotator 40 by a slipping pair. As a result, the movable shaft 56 of each link mechanism section 50 is slidably guided in the guide groove 44 in accordance with the relative rotation of the guide rotator 40 with respect to the first rotator 10.

  In this embodiment in which the link mechanism unit 50 is linked to the rotating bodies 10, 18, and 40 in this way, when the guide rotating body 40 maintains a relative phase with the first rotating body 10, each set of link mechanisms. The movable shaft 56 of the portion 50 rotates together with the guide rotator 40 without being guided in the guide groove 44. At this time, since the relative positional relationship between the links 52 and 53 does not change in the link mechanism section 50 of each group, the second rotating body 18 maintains the relative rotating phase with the first rotating body 10 and rotates clockwise in FIG. And the valve timing is maintained.

  When the guide rotator 40 rotates relative to the first rotator 10 in the direction X, the movable shaft 56 of each link mechanism portion 50 is guided in the guide groove 44 and moves toward the shaft portion 17. As a result, in each set of link mechanism portions 50, the second link 53 is pressed by the movable shaft 56 and driven in the direction X together with the protrusion 19, so the second rotating body 18 is moved relative to the first rotating body 10. Relative rotation in direction X advances the valve timing. On the other hand, when the guide rotator 40 rotates relative to the first rotator 10 in the direction Y, the movable shaft 56 of each link mechanism portion 50 is guided in the guide groove 44 and is opposite to the shaft portion 17. Move to. As a result, the second link 53 is pulled by the movable shaft 56 and driven in the direction Y together with the protrusion 19 in each set of link mechanism portions 50, so that the second rotary body 18 is directed in the direction with respect to the first rotary body 10. Relative rotation to Y and valve timing is retarded.

  As described above, in the present embodiment, the link mechanisms 50 of the respective groups are linked by the movement of the movable shafts 56 according to the relative rotational movement of the guide rotator 40 with respect to the first rotator 10, whereby the rotator 10, The relative phase between 18 and thus the valve timing is adjusted.

  Next, the characteristic part of this embodiment is demonstrated. In the following description, the thickness in the rotation axis direction is simply referred to as “thickness”, the gap in the rotation axis direction is simply referred to as “thrust clearance”, and the relative displacement amount in the rotation axis direction is simply referred to as “relative displacement amount”. To do.

  As shown in FIGS. 1, 2, and 4, in the present embodiment, in the outer peripheral portion of the first facing portion 11 a that wraps in a state where the protruding portions 19 are adjacent to each other, the first facing portion 11 a is screwed in the rotation axis direction, A gap adjusting member 70 for adjusting the gap S between the protruding portion 19 and the first facing portion 11a is provided. In addition, the protrusion part 19 of the 2nd rotary body 18 is the most retarded angle with respect to the 1st rotary body 10 of FIG.4 and FIG.5 with the outer peripheral part of the 1st opposing part 11a which wraps in the state in which the protrusion part 19 adjoins. In the state, and when the protrusion 19 of the second rotor 18 is in the most advanced angle state with respect to the first rotor 10 in FIG. It is the outer peripheral part of the 1st opposing part 11a.

  As shown in FIGS. 1 and 2, the gap adjusting member 70 includes a threaded portion (hereinafter referred to as a threaded portion) 71 that can be threadedly engaged with the screw hole 13 of the first facing portion 11 a and can be advanced and retracted in the rotation axis direction, and a protruding portion. 19 is provided. The screw portion 71 is provided with an input portion 73 connected to an output end portion of a screwing device as a manufacturing device, for example, at an end portion opposite to the head portion 72. The input portion 73 is formed with an I-shaped or + -shaped fitting groove that can be connected to the output end portion, or a hexagonal hole-like fitting hole. As shown in FIG. 2, the input portion 73 is formed at an end portion that protrudes on the opposite side of the gap S across the first facing portion 11 a in the screw portion 72.

Such a gap adjusting member 70 receives the screwing force generated by the external device such as the screwing device and is screwed and unscrewed in the first facing portion 11a, so that the first facing portion with respect to the protruding portion 19 is obtained. The protrusion amount of the head 72 protruding from 11a is adjusted. Thereby, the gap adjusting member 70 can adjust the gap S in the first rotating body 10 from the outside of the first rotating body 10 (hereinafter simply referred to as “external adjustment”).

According to such a configuration, between the facing portions 11a and 12a, the facing portions 11a and 12a and all the clamping elements of the projecting portion 19 of the second rotating body 18, the link mechanism portion 50, and the planetary gear mechanism portion 30 are adjacent to each other. The sum of the thrust clearances formed by the objects can be reduced by the gap S that is externally adjusted by the gap adjusting member 70. This facilitates the work of managing the clearance size.

  In addition to the above method, the following other methods can be considered as a method for managing the clearance size. That is, another first method is a method of separately managing the respective thrust clearances of the link mechanism unit and the planetary gear mechanism unit by sandwiching a separating member between the link mechanism unit and the planetary gear mechanism unit. . In addition, as another second method, between adjacent members in at least one of the link mechanism portion and the planetary gear mechanism portion, an interposed member having a selected thickness is inserted between them. This is a method for adjusting the sum of the thrust clearances.

  However, the other first method described above is to reduce the target number of clamping elements by dividing them into units of a link mechanism part and a planetary gear mechanism part, so that the sum of the thrust clearances in each unit is reduced. Although it is smaller, it does not adjust the size of the sum in that unit. Further, in the second method, it is necessary to determine the thickness of the intervening member before incorporating the pinching elements of the link mechanism portion and the planetary gear mechanism portion into the first rotating body. The clearance size cannot be adjusted without disassembling the first rotator in the state of the first rotator incorporating the.

  Further, as another method, it is conceivable to combine the other first and second methods, but in order to adjust the clearance size, the number of separation members and intervening members other than the clamping elements is increased. As a result, there is a risk that assembly productivity will decrease and costs such as processing costs will increase.

  On the other hand, in the present embodiment in which the total thrust clearance is externally adjusted by the gap adjusting member 70, there is no need to provide two members, a separating member and an interposing member. In these two members, there is no need to provide a member for the purpose of reducing the target number of clamping elements such as separating members.

  Furthermore, since this embodiment is a method of managing the clearance size by external adjustment, the productivity of the work of managing the clearance size can be improved. Therefore, the productivity of the work for managing the clearance size can be improved, and the durability can be lowered and the generation of abnormal noise can be suppressed due to the wear caused by the excessive clearance.

  In the present embodiment, the screw portion of the screw portion 71 of the gap adjusting member 70 or the screw portion of the female screw of the fixing hole 13 is pre-coated with a fixing material such as an adhesive (hereinafter simply referred to as “with fixing material”). It is preferable to be referred to as a “threaded portion”. Thereby, since the screw part 72 and the fixing hole 13 can be fixed when the screw part 72 and the fixing hole 13 are screwed together, the adjusted gap S can be maintained. Note that the “thread portion with a fixing material” is, for example, a screw portion coated with an anaerobic adhesive material as a fixing material in a microcapsule. Therefore, since the screw portion 71 is not fixed instantaneously in the process of screwing the screw portion 71 into the fixing hole 13, it is possible to secure a screwing / unscrewing operation time for adjusting the clearance S.

  Moreover, the end surface 72a of the head 72 in contact with the protruding portion 19 forms a flat surface as shown in FIG. Thereby, in the head 72 and the protrusion 19 that are in contact with each other, the end surface 72 of the head 72 can be effectively applied to the protrusion 19 to increase the contact area, thereby reducing the contact stress. Accordingly, it is possible to avoid wear of the head 72 and the protrusion 19 that are in contact with each other.

  Moreover, the head 72 is formed in a larger diameter than the screw part 71, as shown in FIG. Thereby, the contact area of the end surface 72a which contacts the protrusion part 19 can be expanded easily.

  Moreover, in the 1st opposing part 11a, the fixing hole 13 corresponding to the external thread of the thread part 71 does not penetrate the 1st opposing part 11a, but as shown in FIG. 2, the head which advances / retreats in a rotating shaft direction Preferably, a guide hole 14 having an inner circumference that wraps around 72 is provided.

  The screw portion 71 has a screw accuracy determined by a well-known screw standard. Therefore, depending on the screw accuracy, when the screw portion 71 is screwed into the fixing hole 13 and advances and retracts in the direction of the rotation axis, the head 72 may swing in accordance with the advance / retreat operation. In order to suppress the head movement of the head 72, a method of increasing the screw accuracy rank in the above-mentioned standard is conceivable. However, it is necessary to specially process the screw processing, and the screw processing cost of the screw portion 71 and the fixing hole 13 is required. Has the problem of becoming too expensive.

  On the other hand, in the present embodiment in which the fixing hole 13 and the guide hole 14 are provided in the first facing portion 11a, the inner periphery of the guide hole 14 wraps around the outer periphery of the head 72. Regardless of the accuracy, the head 72 can be advanced and retracted accurately along the inner periphery of the guide hole 14 in the direction of the rotation axis.

  The guide hole 14 is not limited to wrapping with respect to the head 72, but may simply accommodate the head 72. According to this, since the guide hole 14 has a housing function for housing at least the head 72, it is not necessary to form a screw common to the screw portion 71 on the outer peripheral portion of the head 72. Therefore, not only the occurrence of flash due to screw formation is avoided in the guide hole 14 and the head 72 of the first facing portion 11a, but also the structure of the guide hole 14 and the head 72 is a structure in which the flash does not easily remain. Can do.

  Here, in this embodiment, the machine unit 6 is manufactured as follows, for example. First, on the first opposing portion 11a in the large-diameter cylindrical portion 11b of the sprocket 11 with the small-diameter cylindrical portion 11c facing downward, the first protrusions 19 of the second rotating body 18 and the first of the link mechanism portions 50 of each set. The links 52 are overlapped, and the first links 52 are connected to the first facing portion 11 a by the first connecting shaft 62. Subsequently, the second links 53 of the link mechanism portions 50 of each set are overlapped in the large-diameter cylindrical portion 11b, and the second link shaft 66 and the movable portion are moved to the corresponding projecting portions 19 and the first links 52. They are connected by a shaft 56. Subsequently, the guide rotating body 40 that is the third opposing portion is overlapped in the large-diameter cylindrical portion 11 b, and the movable shaft 56 of each pair of link mechanism portions 50 is fitted into the guide groove 44.

  Thereafter, the planetary gear mechanism 30 is fastened to the large-diameter cylindrical portion 11b together with the cover member 12 assembled therein, whereby the mechanical unit 6 is completed.

  According to this exemplary method, each protrusion 19 and each set of the second links 53 are sandwiched between the first facing portion 11a and the guide rotating body 40, and each set of the second links 53 and the first facing portions. The structure in which the first links 52 of each set are interposed between the 11a can be manufactured relatively easily.

  Now, in this embodiment, the clearance adjustment member 70 is assembled | attached to the 1st opposing part 11a of the 1st rotary body 11 as follows, for example, and the clearance gap S is adjusted. First, in FIGS. 1 and 3, before the link mechanism portion 50 is assembled into the sprocket 11, the input portion 73 of the gap adjusting member 70 and the screw are directed toward the guide hole 14 and the fixing hole 13 of the first facing portion 11a. The screw part 71 and the fixing hole 13 are screwed together while the part 71 and the head part 72 are inserted in this order. Subsequently, the head 72 is accommodated in the guide hole 14, and the protrusion amount of the head 72 with respect to the first facing portion 11a is preset to zero or less. Subsequently, after assembling the link mechanism 50 and the planetary gear mechanism 30 by a method such as the above-described machine unit manufacturing method, the procket 11 and the cover member 12 are fastened to assemble the first rotating body 1. Complete.

  Thereafter, by applying a screwing force from the input portion 73 of the gap adjusting member 70 and screwing the screw in / out by the gap adjusting member 70, the optimum gap S can be easily adjusted by external adjustment.

  In the above method, it is preferable that the preset amount of protrusion is set to zero. According to this, the screwing amount is defined from the screw pitch of the screw part 71 and the screwing angle, and the protruding amount of the head 72 can be accurately set.

  In the present embodiment, in addition to this, in each set of link mechanism units 50, the first link 52 rotates around the first opposing unit 11 a via the first connecting shaft 62 that is shared with the first rotating body 10. Are connected by. Further, in each set of link mechanism units 50, the second link 53 is connected to the first rotating body 10 and the first link 52 via the second connecting shaft 66 and the movable shaft 56, respectively, and the protruding portion 19 and the first link 52. It is connected to one link 52 by a turning pair. Furthermore, in each set of link mechanism units 50, the first link 52 and the second link 53 are connected to the guide rotator 40 by a slipping pair through a movable shaft 56 shared with each other. Therefore, according to these connection forms, it is possible to manage the clearance formed by the adjacent elements between the first facing portion 11a and the guide rotating body 40 as the third facing portion to an appropriate size.

  Here, in the above-described embodiment, in the timing chain 15 spanned over the teeth 16 of the first rotating body 10 for transmission of the engine torque from the crankshaft, the protruding portion 19 of the second rotating body 18 is provided. Since the maximum relative displacement amount of the first rotating body 10 with respect to the above is affected by the sum of the thrust clearances, depending on the maximum relative displacement amount, there is a concern that the timing chain 15 may be deteriorated in durability such as breakage or wear. .

  On the other hand, the valve timing apparatus 1 of the present embodiment can be adjusted from the outside of the apparatus 1 in the direction of reducing the total sum of the thrust clearances by the gap adjusting member 70. The total sum can be suppressed, and hence the maximum relative displacement amount can be suppressed. In this embodiment, the durability of the timing chain 15 can also be suppressed.

  Here, the guide hole 14 of the 1st opposing part 11a of this embodiment is corresponded to the "head accommodating hole" as described in a claim, and the screw part 71 of the clearance gap adjustment member 70 is as described in a claim. Corresponds to “screwed part”. The timing chain 15 corresponds to the “torque transmission member” described in the claims, the large-diameter cylindrical portion 11b corresponds to the “accommodating portion” described in the claims, and the sprocket 11 corresponds to the claims. The sun gear 31 corresponds to the “gear portion” described in the claims, and the electric motor 21 corresponds to the “torque generation means” described in the claims.

(Second embodiment)
As shown in FIG. 8, the second embodiment of the present invention is a modification of the first embodiment. In the second embodiment, the end surface 72a of the head 72 is formed in a substantially planar shape as a contact method between the head 72 of the gap adjusting member 70 and the protruding portion 19, but the planar end surface 72a is Compared to the outer peripheral part, the inner peripheral part has a slightly convex curved surface, and it forms a smooth inclined surface so-called crowned curved surface (hereinafter simply referred to as “crowning surface”) from the outer peripheral part toward the inner peripheral part. Has been.

  According to this, since the end surface 72a of the head 72 is formed on the crowning surface, it can be effectively applied to the opposing projecting portion side end surface.

  For example, in this embodiment, since the protrusion part 19 is flat form, the protrusion part side end surface of the protrusion part 19 which the end surface 72a contacts exhibits a flat surface or a planar shape similar to this. Even when both of the end surface 72a and the projecting portion side end surface are flat surfaces, the postures of the head end surface 72a and the projecting portion side end surface are excessively inclined unless the flat surfaces ideally overlap and overlap each other. There is a risk of hitting by one factor. On the other hand, in the present embodiment in which the end surface 72a of the head 72 is the crowning surface, it can be effectively applied to the other projecting portion side end surface.

  Moreover, in this embodiment, the outer diameters of the head 72 and the screw part 71 are formed to be substantially the same. A recess 71r is provided at the end of the screw portion 71 on the head 72 side. Thereby, a screw common to the screw portion 71 is not formed on the outer peripheral portion of the head 72. Such a gap adjusting member 70 increases the degree of freedom of arrangement of the gap adjusting member 70 in the outer peripheral portion of the first facing portion 11a corresponding to the overlapping portion of the projecting portions 19 in the most retarded angle state and the most advanced angle state. The apparatus 1 can be downsized.

(Third embodiment)
As shown in FIG. 8, the third embodiment of the present invention is a modification of the first embodiment. In 3rd embodiment, the clearance gap adjustment member 70 is provided in the 2nd opposing part 12a. Such a gap adjusting member 70 sets the gap S when the head 72 comes into contact with the outer peripheral end face of the planetary gear 33.

  In the planetary gear mechanism 30, there is a concern that the thrust thrust acts on the second facing portion 12 a via the sun gear 31 with the planetary motion of the planetary gear 33. Therefore, the end surface of the head 72 is preferably a crowning surface. Thereby, even if the contact load increases due to the thrust thrust, the deformed crowning surface becomes a flat surface to increase the contact area.

(Other embodiments)
So far, one embodiment of the present invention has been described. However, the present invention is not construed as being limited to the embodiment, and can be applied to various embodiments without departing from the scope of the invention.

  For example, about the link mechanism part 50 which combines the 1st link 52 and the 2nd link 53, you may make it provide the appropriate number group according to a specification etc. other than two sets.

  As a “torque transmission member” for transmitting torque from the crankshaft to the first rotating body 10, a timing belt may be used instead of the timing chain 15, and in that case, a pulley is provided instead of the sprocket 11. The first rotating body 10 may be rotated by the timing belt.

  As the “torque generating means” for generating the control torque, an electric brake such as an electromagnetic brake or a fluid brake, or a hydraulic motor may be used instead of the electric motor 21.

  The planetary gear mechanism 30 that decelerates the rotational motion of the planetary carrier 32 and transmits it to the guide rotator 40 may be one in which the outer gear portion of the planetary gear meshes with the sun gear made of the internal gear and performs planetary motion. Good.

  In addition to the above-described device for adjusting the valve timing of the intake valve, the present invention can also be applied to a device for adjusting the valve timing of the exhaust valve and a device for adjusting the valve timing of both the intake valve and the exhaust valve. It is.

It is a figure which shows the principal part of the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It is the II sectional view taken on the line of FIG. It is sectional drawing to which the principal part in FIG. 1 was expanded. It is a figure which shows the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: It is the III-III sectional view taken on the line of FIG. It is the IV-IV sectional view taken on the line of FIG. It is the VV sectional view taken on the line of FIG. It is the VI-VI sectional view taken on the line of FIG. It is sectional drawing which shows the operation state different from FIG. It is sectional drawing which shows the principal part of the valve timing adjustment apparatus by 2nd embodiment of this invention. It is sectional drawing which shows the principal part of the valve timing adjustment apparatus by 3rd embodiment of this invention.

Explanation of symbols

1 Valve Timing Adjusting Device 2 Cam Shaft 4 Electric Unit 6 Machine Unit 10 First Rotating Body 11 Sprocket (Main Body Member)
11a 1st opposing part 11b Large diameter cylinder part (accommodating part)
11c Small diameter cylinder part 12 Cover member 12a Second opposing part 12b Large diameter cylinder part 12c Small diameter cylinder part 13 Screw hole (fixing hole)
14 Guide hole (head receiving hole)
15 Timing chain (torque transmission member)
16 teeth 17 shaft portion 18 second rotating body 19 projecting portion 21 electric motor (torque generating means)
30 planetary gear mechanism 31 sun gear (gear)
32 planetary carrier 33 planetary gear 39 internal gear part 40 guide rotor (third counter part)
44 Guide groove 50 Link mechanism 52 First link 53 Second link 56 Movable shaft 60, 61 Pairing element 62 First connecting shaft 64, 65 Pairing element 66 Second connecting shaft 70 Gap adjusting member 71 Threaded portion (threaded portion)
72 Head 72a Contact surface (end surface)
73 Input section

Claims (9)

In a valve timing adjustment device for an internal combustion engine that adjusts the valve timing of at least one of an intake valve and an exhaust valve whose camshaft opens and closes by driving torque transmission from a crankshaft,
A first rotating body that rotates in conjunction with one of the crankshaft and the camshaft;
A second rotating body housed in the first rotating body and rotating in conjunction with the other of the crankshaft and the camshaft;
A link mechanism that is housed in the first rotating body and changes a relative phase between the first rotating body and the second rotating body by a link operation;
By receiving a control torque from the outside according to the driving torque, the link mechanism unit receives the control torque from the outside by being accommodated in the first rotating body and engaging in a gear portion provided in the first rotating body. The planetary gear mechanism for transmitting the control torque;
With
The first rotating body has a first facing portion and a second facing portion that face each other in the rotation axis direction common to the second rotating body,
The second rotating body has a protruding portion that protrudes in the same radial direction as the first rotating body,
Between the first facing portion and the second facing portion, the protruding portion of the second rotating body, the link mechanism portion, and the planetary gear mechanism portion are sandwiched in this order,
The first facing portion is disposed to face the first end portion in the rotation axis direction on the anti-link mechanism portion side in the projecting portion, and the second facing portion is on the anti-link mechanism portion side in the planetary gear mechanism portion. Is disposed opposite the second end in the rotation axis direction of
In any one of the first facing portion and the second facing portion, a gap adjusting member that protrudes in the rotation axis direction toward the end corresponding to the facing portion is provided,
The said gap adjustment member provides a clearance gap between the said opposing part and the said edge part, without contacting the said opposing part and the said edge part, and adjusts the said clearance gap from the outside. The gap adjusting member includes a screwing portion that is screwed in the rotation axis direction of the facing portion with respect to the facing portion, and a head that is in contact with the end portion, in the facing portion and the end portion provided with the gap. And
2. The valve timing adjusting device according to claim 1, wherein the head is formed in a flat surface or a curved surface having a crowned end surface in contact with the end portion. The opposing portion has a fixing hole that is screwed together with the screwing portion, and a head receiving hole that is formed in a larger diameter than the fixing hole and receives the head.
3. The valve timing adjusting device according to claim 2, wherein the gap adjusting member is screwed so that an end of the screwing portion opposite to the head is inserted toward the facing portion. .   The gap adjusting member receives a screwing force from the outside at an end opposite to the head of the screwing portion, and adjusts the amount of protrusion of the head from the facing portion, whereby the gap The valve timing adjusting device according to claim 2 or 3, wherein the valve timing adjusting device is adjusted.   The valve timing adjusting device according to any one of claims 1 to 4, wherein the head is formed to have a larger diameter than the screwing portion. The link mechanism is
A guide rotor having a guide groove;
A first link and a second link that share a movable shaft guided in the guide groove according to the rotation of the guide rotating body, and operate the link by the movement of the movable shaft to adjust the relative phase;
Have
The second link and the guide rotor are sandwiched in this order between the protrusion of the first rotor and the third end of the planetary gear mechanism opposite to the second end. ,
The valve timing adjusting device according to any one of claims 1 to 5, wherein the first link is interposed between the first facing portion and the second link. The first link shares the first series of connecting shafts with the first rotating body, and is connected to the first opposing portion by a turning pair via the first series of connecting shafts,
The second link shares a second connecting shaft with the second rotating body, and is connected to the projecting portion by a rotating pair via the second connecting shaft, and is connected to the protrusion by a rotating pair via the movable shaft. The valve timing adjusting device according to claim 6, wherein the valve timing adjusting device is connected to one link.   The first rotator has an accommodating portion for accommodating the guide rotator, the first link, the second link, and the protruding portion between the first opposed portion and the second opposed portion. The valve timing adjusting device according to claim 6 or 7. Torque generating means for generating the control torque,
The planetary gear mechanism is
A planetary carrier that is rotated by the control torque, and a planetary gear that is supported by the planetary carrier so as to freely move in planetary motion, and the rotational movement of the planetary carrier is decelerated by the planetary movement of the planetary gear to transmit torque to the link mechanism unit. The valve timing adjusting device according to any one of claims 1 to 8, wherein

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