JP2012219680A - Valve timing adjustment device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To increase productivity, durability and silence.SOLUTION: This valve timing adjustment device includes: a rolling bearing 60 formed by interposing a rolling element 63 between inner and outer rings 61, 62; a planetary gear 50 causing an engine phase variation by sun-and-planet motion when supported by the outer ring 62; a planetary carrier 40 which is formed with a fitting groove 42 opened in an axial end surface 402 and which allows the planetary gear 50 to perform the sun-and-planet motion by rotation when supporting the inner ring 61, the inner bottom surface 420 of the fitting groove 42 being inclined to an axial direction so that the groove depth of the fitting groove 42 is reduced as the inner bottom surface is separated from an end surface 402; an actuator 4 which has a rotating shaft 3 formed by projecting a joint 32 fitted from the end surface 402 into the fitting groove 42 and which rotatively drives the planetary carrier 40 together with the rotating shaft 3; and an elastic member 70 which axially presses the inner ring 61 to apply a preload to the rolling bearing 60 and which axially presses the planetary carrier 40 toward the end surface 402.

Description

  The present invention relates to a valve timing adjusting device that adjusts the valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine mounted on a vehicle.

  2. Description of the Related Art Conventionally, there has been known a valve timing adjusting device that causes a change in rotational phase (hereinafter referred to as “engine phase”) between a crankshaft and a camshaft by planetary movement of a planetary gear and adjusts valve timing in accordance with the change. ing.

  As a kind of such valve timing adjusting device, the disclosed device of Patent Document 1 is such that a rolling bearing that supports a planetary gear is supported by a planetary carrier, and the planetary gear is rotated in the revolving direction of the planetary gear, thereby causing the planetary gear to rotate. A configuration to exercise is provided. In such a configuration, during planetary movement of the planetary gear, since the rolling elements interposed between the inner and outer rings of the rolling bearing are in rolling contact with the inner and outer rings, the frictional resistance between the planet carrier and the planetary gear is reduced, Wear can be suppressed. Therefore, it is possible to improve the durability of the valve timing adjusting device that frequently planetarily moves the planetary gear according to the operating state of the internal combustion engine.

  Further, in the disclosed device of Patent Document 1, in order to rotationally drive the planet carrier in the revolving direction, a joint portion protruding from the rotation shaft of the actuator is provided on the end surface side in the fitting groove portion opened in the axial end surface of the planet carrier. It is inserted from. This facilitates the connecting operation between the planet carrier and the rotating shaft at the time of assembly, and can also increase productivity.

JP 2010-255474 A

  Now, in the disclosed device of Patent Document 1, the inner ring of the rolling bearing is urged in the axial direction by the snap ring. However, such an urging action is merely an action of pressing the inner ring against the projecting portion of the planet carrier, so it is difficult to apply a preload to the rolling bearing to reduce the gap between the inner and outer rings and the rolling element. Therefore, when the vehicle travels when such an internal clearance exists in the rolling bearing, the rolling element may vibrate slightly, which may cause fretting wear on the outer peripheral surface of the rolling element and the raceway surface of the inner and outer rings. Not desirable in terms of sex. At the same time, the rolling element that vibrates slightly may generate noise due to the collision with the inner and outer rings, which is not desirable in terms of quietness.

  Moreover, in order to improve productivity in the disclosed apparatus of Patent Document 1, in order to easily fit the joint portion of the rotating shaft into the fitting groove portion of the planetary carrier, a clearance is secured between the joint portion and the groove portion. It becomes important. However, when ensuring such a fitting gap, there is a risk of causing abnormal noise between the rotating shaft and the planet carrier due to wear due to relative sliding or collision, which is desirable in terms of both durability and quietness. There is no.

  The present invention has been made to solve the above-described problems all at once, and an object thereof is to improve productivity, durability, and quietness of the valve timing adjusting device.

  The invention according to claim 1 is a valve timing adjusting device that adjusts the valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine mounted on a vehicle according to a change in engine phase. A rolling bearing in which a rolling element is interposed between the inner ring and the outer ring, a planetary gear that causes a change in the engine phase by planetary movement while being supported by the outer ring, and a fitting groove that opens on the end face in the axial direction. And a planet carrier that planetarily moves the planetary gear by rotating in the revolving direction of the planetary gear while supporting the inner ring, and the inner surface of the fitting groove is separated from the end surface. A planetary carrier that is inclined with respect to the axial direction, and a rotating shaft formed by projecting a joint portion that is fitted into the fitting groove portion from the end surface side. The actuator that rotationally drives the rotor in the revolving direction and the inner ring or the outer ring are biased in the axial direction to preload the rolling bearing, and the planetary carrier is moved in the axial direction toward the end face side where the fitting groove portion opens in the planetary carrier. And an elastic member to be urged.

  In this invention, since the planet carrier further supports the rolling bearing that supports the planetary gear, when the planetary gear rotates in the direction of the planetary gear rotation, the planetary gear moves between the inner and outer rings of the rolling bearing. The mounted rolling elements make rolling contact with the inner and outer rings. Therefore, the frictional resistance between the planet carrier and the planetary gear becomes small, and wear can be suppressed. Further, in the first aspect of the invention, the inner ring or the outer ring is urged in the axial direction by the elastic member, so that a preload is applied to the rolling bearing, so that the gap between the inner and outer rings and the rolling element is reduced. Therefore, it is possible to suppress the occurrence of fretting wear and abnormal noise due to the rolling element vibrating when the vehicle travels due to the presence of such an internal gap.

  In addition, in the invention described in claim 1, the fitting groove that opens in the axial end surface of the planetary carrier is reduced inward as it is separated from the end surface, in other words, inward expansion toward the end surface. Therefore, it is easy to fit the joint portion protruding from the rotation shaft of the actuator from the end face side. Moreover, in the planetary carrier that is biased by the elastic member toward the opening end face side of the fitting groove portion in the axial direction, the inner method of the fitting groove portion is reduced as it is inclined with respect to the axial direction and separated from the end face side. The inner surface of the fitting groove part to be made can always be pressed against the fitting part fitted into the fitting groove part from the end face side. As a result of this pressing action, it is possible to suppress wear due to relative sliding and abnormal noise generation due to collision between the rotating shaft and the planet carrier.

  As described above, according to the first aspect of the present invention, it is possible to facilitate the fitting of the joint portion into the fitting groove portion to increase productivity, and to suppress wear and noise generation, thereby improving durability and quietness. Is possible.

  According to the second aspect of the present invention, the inner bottom surface of the inner surface of the fitting groove portion reduces the groove depth as the inner method as the distance from the end surface where the fitting groove portion opens in the planetary carrier in the axial direction. Tilt against. In this invention, the groove depth as the inner method of the fitting groove portion opened to the end surface in the axial direction by the planetary carrier is reduced as it is separated from the end surface side, in other words, the groove depth is reduced toward the end surface side. With the enlarged form, the fitting part can be easily fitted from the end face side, and the productivity can be improved. In addition, in the planetary carrier that is biased toward the opening end face side of the fitting groove portion in the axial direction, the inner bottom surface of the fitting groove portion that reduces the groove depth as it is inclined with respect to the axial direction and separated from the end face side. However, it can be reliably pressed from the end face side to the fitting portion fitted into the fitting groove. Therefore, between the rotating shaft and the planet carrier, it is possible to improve durability and quietness by ensuring the effect of suppressing wear due to relative sliding and the generation of abnormal noise due to collision.

  According to the third aspect of the present invention, the inner side surface of the inner surface of the fitting groove portion is reduced in the groove width as an inner method as the distance from the end surface where the fitting groove portion opens in the planetary carrier, and in the axial direction. Inclines against. According to the present invention, the groove width as an inner method of the fitting groove portion opened to the end surface in the axial direction by the planetary carrier decreases as the distance from the end surface side increases. In other words, the groove width increases toward the end surface side. Depending on the form, fitting of the joint portion from the end face side can be facilitated to increase productivity. Moreover, in the planetary carrier that is biased toward the opening end face side of the fitting groove portion in the axial direction, the inner side surface of the fitting groove portion that reduces the groove width as it is inclined with respect to the axial direction and separated from the end face side. Further, it can be surely pressed against the fitting portion fitted into the fitting groove portion from the end face side. Therefore, between the rotating shaft and the planet carrier, it is possible to improve durability and quietness by ensuring the effect of suppressing wear due to relative sliding and the generation of abnormal noise due to collision.

  According to the invention described in claim 4, the elastic member is interposed between the planet carrier and the inner ring, so that the planet carrier is moved toward the end face side opposite to the biasing direction of the inner ring in the axial direction. Energize. In this invention, the inner ring is urged in the axial direction by the elastic member between the planet carrier and preload is applied to the rolling bearing, and the gap between the inner and outer rings and the rolling element is reduced. It is possible to suppress the occurrence of fretting wear and abnormal noise caused by fine vibrations of moving objects. Further, in a planetary carrier urged by an elastic member toward the end surface side that is the axial direction opposite to the urging direction of the inner ring, the inner method is reduced as it is inclined with respect to the axial direction and separated from the end surface side. The inner surface of the joint groove portion can always be pressed against the joint portion fitted into the fitting groove portion from the end surface side. Therefore, between the rotating shaft and the planetary carrier, it is possible to enhance the durability and quietness by exhibiting the effect of suppressing wear due to relative sliding and the generation of abnormal noise due to collision.

  According to the invention described in claim 5, the elastic member is interposed between the planetary gear and the outer ring, so that the planet carrier that supports the outer ring is positioned on the end face side that is the same as the urging direction of the outer ring in the axial direction. Energize towards. In this invention, since the outer ring is urged in the axial direction by the elastic member between the planetary gears, a preload is applied to the rolling bearing, and the gap between the inner and outer rings and the rolling element is reduced. It is possible to suppress the occurrence of fretting wear and abnormal noise caused by fine vibrations of moving objects. Further, in a planetary carrier urged by an elastic member toward the end surface side that is the same axial direction as the urging direction of the outer ring, the inner method is reduced as it is inclined with respect to the axial direction and separated from the end surface side. The inner surface of the joint groove portion can always be pressed against the joint portion fitted into the fitting groove portion from the end surface side. Therefore, between the rotating shaft and the planetary carrier, it is possible to enhance the durability and quietness by exhibiting the effect of suppressing wear due to relative sliding and the generation of abnormal noise due to collision.

  According to the sixth aspect of the present invention, the space between the inner and outer rings of the rolling bearing is opened to the inside of the apparatus into which the lubricating liquid is introduced as the internal combustion engine rotates. In this invention, since the lubricating liquid introduced into the apparatus enters between the inner and outer rings of the rolling bearing that is opened inside the apparatus as the internal combustion engine rotates, the rolling elements come into rolling contact with the inner and outer rings. Wear can be suppressed. In addition, for example, in a hybrid system using an internal combustion engine and an electric motor as a vehicle drive source, even if the introduction of the lubricating liquid is stopped with the rotation of the internal combustion engine, the rolling bearing subjected to the preload causes a slight vibration of the rolling element. The resulting fretting wear and abnormal noise can also be suppressed.

It is a figure which shows the basic composition 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 the II-II sectional view taken on the line of FIG. 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 a schematic diagram for demonstrating the characteristic of the valve timing adjustment apparatus by 1st embodiment of this invention. It is a figure which shows the principal part of the valve timing adjustment apparatus by 2nd embodiment of this invention, Comprising: It is sectional drawing corresponding to FIG. It is the VIII-VIII sectional view taken on the line of FIG. It is a schematic diagram for demonstrating the characteristic of the valve timing adjustment apparatus by 2nd embodiment of this invention. It is a figure which shows the principal part of the valve timing adjustment apparatus by 3rd embodiment of this invention, Comprising: It is a figure corresponding to FIG. It is a figure which shows the principal part of the valve timing adjustment apparatus by the modification of 1st embodiment of this invention, Comprising: It is a corresponding figure of FIG. It is a figure which shows the principal part of the valve timing adjustment apparatus by the modification of 1st embodiment of this invention, Comprising: It is a corresponding figure of FIG.

  Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings. In addition, the overlapping description may be abbreviate | omitted by attaching | subjecting the same code | symbol to the corresponding component in each embodiment. When only a part of the configuration is described in each embodiment, the configuration of the other embodiment described above can be applied to the other part of the configuration. In addition, not only combinations of configurations explicitly described in the description of each embodiment, but also the configurations of a plurality of embodiments can be partially combined even if they are not explicitly specified unless there is a problem with the combination. .

(First embodiment)
FIG. 1 shows a valve timing adjusting apparatus 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 a crankshaft (not shown) of an internal combustion engine to a camshaft 2. Here, the camshaft 2 of the present embodiment opens and closes an intake valve (not shown) among the valves of the internal combustion engine by transmitting engine torque. Therefore, the valve timing adjusting device 1 adjusts the valve timing of the intake valve by changing the engine phase as the rotational phase of the camshaft 2 with respect to the crankshaft.

(Basic configuration)
Hereinafter, a basic configuration of the valve timing adjusting device 1 will be described. The valve timing adjusting device 1 is a combination of an actuator 4, an energization control circuit unit 7, a planetary gear mechanism 8, and the like.

  The actuator 4 is an electric motor such as a brushless motor, for example, and includes a case 5 fixed to a fixed node of the internal combustion engine and a rotating shaft 3 supported by the case 5 so as to be rotatable forward and backward. The energization control circuit unit 7 includes, for example, a drive driver and a control microcomputer thereof, and is disposed outside and / or inside the case 5 and is electrically connected to the actuator 4. The energization control circuit unit 7 energizes the actuator 4 for realizing the valve timing according to the operating state of the internal combustion engine, and controls the rotational drive of the rotary shaft 3.

  The planetary gear mechanism 8 includes a drive rotator 10, a driven rotator 20, a planet carrier 40, a planetary gear 50, and a rolling bearing 60.

  As shown in FIGS. 1 to 3, the drive rotor 10 that is hollow as a whole is an element that forms the outermost contour of the planetary gear mechanism 8, and the other components 20, 40, 50, 60 of the mechanism 8. 70 are accommodated in the internal space 100. The drive rotator 10 is formed by co-tightening the cylindrical wall member 14 between the gear member 12 and the sprocket member 13 on the same axis.

  As shown in FIGS. 1 and 2, the bottomed cylindrical gear member 12 has a drive-side internal gear portion 18 having a tooth tip circle on the inner peripheral side of the root circle on the peripheral wall portion. As shown in FIGS. 1 and 3, the stepped cylindrical sprocket member 13 has a plurality of teeth 19 projecting radially outward from the peripheral wall portion at equal intervals in the rotational direction. The sprocket member 13 is linked to the crankshaft by passing a timing chain (not shown) between the teeth 19 and a plurality of teeth of the crankshaft. With this connection, when the engine torque of the crankshaft is transmitted to the sprocket member 13 through the timing chain, the drive rotator 10 rotates in conjunction with the crankshaft. At this time, the rotation direction of the drive rotator 10 is the counterclockwise direction in FIG. 2 and the clockwise direction in FIG. 3.

  The bottomed cylindrical driven rotor 20 is coaxially disposed on the inner peripheral side of the cylindrical wall member 14 having a larger diameter cylindrical shape than that. As shown in FIG. 1, the driven rotating body 20 has a fixed portion 21 formed on the bottom wall portion that is coaxially fixed to the camshaft 2. With this fixed form, the driven rotor 20 can rotate in conjunction with the camshaft 2 and can rotate relative to the drive rotor 10. Here, the rotation direction of the driven rotator 20 is set to the clockwise direction of FIG.

  As shown in FIGS. 1 and 3, the driven rotating body 20 has a driven side internal gear portion 22 having a tooth tip circle on the inner peripheral side of the root circle on the peripheral wall portion. The inner diameter of the driven side internal gear portion 22 is set smaller than the inner diameter of the drive side internal gear portion 18, and the number of teeth of the driven side internal gear portion 22 is set smaller than the number of teeth of the drive side internal gear portion 18. . The driven side internal gear portion 22 is arranged so as to be shifted in the axial direction with respect to the drive side internal gear portion 18.

  As shown in FIGS. 1 to 3, the overall planetary carrier 40 is connected to a cylindrical inner peripheral surface 400 arranged coaxially with the rotary bodies 10 and 20 and the rotary shaft 3 in the peripheral wall portion. Part 41 is formed. The connection part 41 has the fitting groove part 42 with which the rotating shaft 3 is connected by fitting. With this fitting form, the planetary carrier 40 can rotate integrally with the rotary shaft 3 and can rotate relative to the drive-side internal gear portion 18.

  The planetary carrier 40 forms an eccentric support portion 46 on a cylindrical outer peripheral surface 401 arranged eccentrically from the rotating bodies 10 and 20 and the rotary shaft 3 in the peripheral wall portion. The eccentric support portion 46 is fitted to the center hole 51 of the planetary gear 50 via the rolling bearing 60 preloaded in the axial direction by the elastic member 70, thereby bearing the gear 50 so that it can perform planetary motion. . Here, the planetary motion refers to a motion in which the planetary gear 50 revolves around the rotation axis of the elements 40, 6 while rotating around the eccentric axis of the eccentric support 46 with respect to the elements 10, 20, 6. Therefore, when the planetary carrier 40 rotates in the revolving direction of the planetary gear 50 together with the rotating shaft 3, the gear 50 makes a planetary motion.

  As a whole, the stepped cylindrical planetary gear 50 includes a driving-side external gear portion 52 and a driven-side external gear portion 54 having a tip circle on the outer peripheral side of the root circle, respectively, on the large diameter portion and the small diameter portion of the peripheral wall portion. Forming. The drive-side external gear portion 52 disposed on the inner peripheral side of the drive-side internal gear portion 18 meshes with the internal gear portion 18 on the eccentric side of the eccentric support portion 46 with respect to the elements 10, 20, 6. A driven-side external gear portion 54 that is displaced in the axial direction from the drive-side external gear portion 52 and is disposed on the inner peripheral side of the driven-side internal gear portion 22 is on the eccentric side of the eccentric support portion 46 with respect to the elements 10, 20, 6. It meshes with the internal gear portion 22. The outer diameter of the driven-side external gear portion 54 is set smaller than the outer diameter of the driving-side external gear portion 52, and the number of teeth of the driven-side external gear portion 54 and the driving-side external gear portion 52 is respectively the driven-side internal gear. The number is set to be smaller by the same number than the number of teeth of the portion 22 and the drive side internal gear portion 18.

  Thus, the planetary gear mechanism 8 in which the rotating bodies 10 and 20 are geared together realizes the valve timing in accordance with the engine phase by rotating the planet carrier 40 together with the rotating shaft 3 by the actuator 4. Specifically, when the planetary carrier 40 is rotationally driven together with the rotary shaft 3 at the same speed as the drive rotator 10, the carrier 40 does not rotate relative to the drive-side internal gear portion 18, so that the planetary gear 50 is connected to the planetary gear 50. It rotates with the rotating bodies 10 and 20 without moving. As a result, the engine timing does not change, and the valve timing is maintained.

  On the other hand, when the planetary carrier 40 is rotationally driven at a higher speed than the drive rotator 10 together with the rotary shaft 3, the carrier 40 rotates relative to the drive side internal gear portion 18 toward the advance side, thereby causing the planetary gear. 50 makes a planetary movement. As a result, the driven rotator 20 rotates relative to the drive rotator 10 to the advance side, so that the engine phase changes to the advance side and the valve timing is advanced.

  On the other hand, when the planetary carrier 40 rotates with the rotating shaft 3 at a lower speed than the drive rotator 10 or is driven to rotate in the opposite direction to the drive rotator 10, the carrier 40 is delayed with respect to the drive-side internal gear portion 18. The planetary gear 50 moves in a planetary motion by rotating relative to the corner side. As a result, the driven rotator 20 rotates relative to the drive rotator 10 to the retard side, so that the engine phase changes to the retard side and the valve timing is retarded.

(Characteristic configuration)
Hereinafter, a characteristic configuration of the valve timing adjusting device 1 will be described. As shown in FIGS. 1, 4, and 5, in the planetary carrier 40 made of metal, the coupling portion 41 is provided with a pair of fitting groove portions 42 facing each other in the radial direction. Each fitting groove 42 opens in the formation inner peripheral surface 400 of the connecting portion 41 and both end surfaces 402 and 403 in the axial direction of the planetary carrier 40 and has a rectangular shape as viewed in the coaxial direction. That is, each fitting groove portion 42 is formed in a rectangular groove shape extending in the entire axial direction in a form that is recessed from the radially inner side to the outer side in the planetary carrier 40.

  As shown in FIGS. 4 and 5, the inner bottom surface 420 of the inner surface of each fitting groove portion 42 is formed with an inclined surface portion 420 a that is inclined with respect to the axial direction at a part extending from the end surface 402 on the actuator 4 side. Yes. Here, in the present embodiment, the inclined surface portions 420a of the both fitting groove portions 42 are planes that individually reduce the groove depth of the inner method of the corresponding fitting groove portions 42 as the distance from the end surface 402 of the planet carrier 40 increases. It is provided in a tapered shape. On the other hand, in the planetary carrier 40 of the present embodiment, both inner side surfaces 421 facing each other across the inner bottom surface 420 among the inner surfaces of the respective fitting groove portions 42 are in the entire region from the end surface 402 on the actuator 4 side to the end surface 403 on the opposite side. The film extends substantially parallel to the axial direction.

  The rotary shaft 3 is configured by combining a shaft main body portion 30 and a joint portion 32. A metal shaft main body 30 (see also FIG. 1) that is rotationally driven by the torque generated by the actuator 4 is formed in a shaft shape that extends along the rotational axis.

  A metal joint portion 32 formed separately from the shaft main body portion 30 has a sleeve portion 33 and a fitting convex portion 34. The cylindrical sleeve portion 33 is coaxially disposed on the outer peripheral side of the shaft main body portion 30 and the inner peripheral side of the connecting portion 41. The sleeve portion 33 can be integrally rotated with the main body portion 30 by being connected to the shaft main body portion 30 inserted on the inner peripheral side thereof via the connection pin 35. On the other hand, a pair of fitting convex portions 34 are provided in a form protruding from the outer peripheral surface of the sleeve portion 33 toward the opposite side in the radial direction. Each fitting convex part 34 has a rectangular shape as viewed in the axial direction of the rotating shaft 3, and is fitted into the corresponding fitting groove part 42 in the planetary carrier 40 from the end face 402 side.

  Here, as shown in FIG. 6, in the present embodiment, the radial distance D1 between the protrusion-side tip surfaces 340 of the fitting protrusions 34 is the end of the inclined surface portion 420a of each fitting groove 42 on the end surface 402 side. It is set smaller than the radial distance D2a between the portions 420b (see also FIGS. 4 and 5). That is, the distance D1 is set according to the distance D2a so that a gap is formed between the front end surface 340 and the end portion 420b when the fitting convex portion 34 is fitted into the fitting groove portion 42. At the same time, the radial distance D1 is set larger than the radial distance D2b between the end portions 420c (see also FIGS. 4 and 5) on the opposite side to the end surface 402 of the inclined surface portions 420a of the respective fitting groove portions 42. Yes. Further, the width W1 of each fitting protrusion 34 is set to be substantially the same or slightly smaller than the width W2 between both inner side surfaces 421 of each fitting groove 42. With these settings, as shown in FIGS. 4 and 5, the joint portion 32 is connected between the intermediate portion 420 d in the axial direction of the inclined surface portion 420 a of each fitting groove portion 42 and between the inner side surfaces 421 of each fitting groove portion 42. And the shaft main body 30 is connected to the planet carrier 40.

  As shown in FIGS. 1 and 4, the metal rolling bearing 60 is a radial bearing in which a rolling element 63 is interposed between an inner ring 61 and an outer ring 62. The inner peripheral surface 610 of the inner ring 61 is coaxially fitted and attached to the outer peripheral surface 401 forming the eccentric support portion 46 of the planetary carrier 40, so that it is supported by the support portion 46 from the inner peripheral side. On the other hand, the outer peripheral surface 620 of the outer ring 62 is coaxially fitted and mounted to the inner peripheral surface 500 forming the center hole 51 of the planetary gear 50, thereby supporting the gear 50 from the inner peripheral side. Yes. Here, as shown in FIG. 1, the rolling bearing 60 of the present embodiment has two rows of ball-shaped rolling elements 63 interposed in the axial direction between the inner and outer rings 61 and 62, and the axis between the inner and outer rings 61 and 62 is a shaft. It is an open-type compound ball bearing that is open to the internal space 100 of the drive rotor 10 on both sides in the direction.

  In the metal driven rotating body 20, an introduction passage 24 for introducing engine lubricating oil as “lubricating liquid” into the internal space 100 of the driving rotating body 10 is formed through the fixed portion 21. The introduction passage 24 communicates with the mechanical pump 9 driven by the engine torque of the crankshaft through a supply passage 2 a that penetrates the camshaft 2. With such a communication mode, the lubricating oil discharged from the pump 9 to the supply passage 2a with the rotation of the internal combustion engine is introduced into the internal space 100 of the drive rotating body 10 from the introduction passage 24, thereby entering the space 100. It enters between the inner and outer rings 61 and 62 of the rolling bearing 60 to be accommodated. Therefore, during the planetary movement of the planetary gear 50 due to the rotation of the planetary carrier 40, the rolling element 63 is in rolling contact with the inner and outer rings 61 and 62 through the lubricating oil in the rolling bearing 60 between the elements 40 and 50. Wear is suppressed.

  As shown in FIGS. 1 and 4, the metal elastic member 70 is a disc-shaped disc spring in the present embodiment, and the flange portion 47 (see FIG. 5) that protrudes from the outer peripheral surface 401 to the outer peripheral side of the planetary carrier 40. And the inner ring 61 of the rolling bearing 60 is interposed in the axial direction. The elastic member 70 is pinched coaxially between the flange portion 47 and the inner ring 61 in a compressed state, thereby applying a restoring force to both sides in the axial direction. The elastic member 70 urges the inner ring 61 toward the axial direction (the right direction in FIGS. 1 and 4) that generates a preload on the rolling bearing 60 by the restoring force action. At the same time, the elastic member 70 biases the planetary carrier 40 toward the end surface 402 side (the left direction in FIGS. 1 and 4) opposite to the biasing direction of the inner ring 61 in the axial direction.

  Thus, in the rolling bearing 60 in which the elastic member 70 urges the inner ring 61, a preload is applied to reduce the gap between the inner and outer rings 61 and 62 and the rolling element 63. Therefore, it is possible to suppress the occurrence of fretting wear and abnormal noise due to the rolling element 63 vibrating when the vehicle travels due to the presence of the internal clearance in the rolling bearing 60. For example, in a hybrid system using an internal combustion engine and an electric motor as a vehicle drive source, this can be achieved even when the rotation of the internal combustion engine and the introduction of lubricating oil into the drive rotor 10 are stopped when the electric motor is used. It is a suppressive action.

  Furthermore, the groove depth of each fitting groove portion 42 opened to the axial end surface 402 in the planetary carrier 40 decreases as the distance from the end surface 402 side increases, in other words, the groove depth increases toward the end surface 402 side. It has become. Therefore, each fitting convex part 34 of the joint part 32 protruding at the rotating shaft 3 of the actuator 4 can be easily fitted into the corresponding fitting groove part 42 from the end face 402 side. Moreover, in the planetary carrier 40 in which the elastic member 70 urges toward the end surface 402 side, the groove depth is reduced as the inner bottom surface 420 of each fitting groove portion 42 is inclined with respect to the axial direction and separated from the end surface 402 side. The inclined surface portion 420a is always pressed against the fitted fitting convex portion 34 from the end surface 402 side. Therefore, between the rotating shaft 3 and the planet carrier 40 that can reliably exert such pressing action, wear due to relative sliding and generation of abnormal noise due to collision are suppressed.

  According to the first embodiment described above, the fitting portion 32 can be easily fitted into each fitting groove portion 42 to increase productivity, and the durability and quietness can be improved by firmly suppressing wear and noise generation. It can also be increased.

(Second embodiment)
As shown in FIGS. 7 and 8, the second embodiment of the present invention is a modification of the first embodiment. In the planetary carrier 2040 of the second embodiment, each of the rectangular groove-like fitting groove portions 2042 opened to the inner peripheral surface 400 and the end surfaces 402 and 403 is axially provided to each part of both inner side surfaces 2421 extending from the end surface 402. An inclined surface portion 2421a that is inclined with respect to the surface is formed. Here, in the present embodiment, the inclined surface portions 2421a of both inner side surfaces 2421 are flat taper that jointly reduces the groove width of the inner method of the corresponding fitting groove portion 2042 as the distance from the end surface 402 of the planet carrier 2040 increases. Is provided. On the other hand, the inner bottom surface 2420 that connects between the inner side surfaces 2421 among the inner surfaces of each fitting groove 2042 is the entire area from the end surface 402 on the actuator 4 side to the end surface 403 on the opposite side in the planetary carrier 2040 of the present embodiment. It extends substantially parallel to the axial direction.

  In accordance with such a configuration, as shown in FIG. 9, the width W1 of each fitting convex portion 34 is such that the end portion 2421b on the end surface 402 side of the inclined surface portions 2421a of both inner side surfaces 2421 of each fitting groove portion 2042 (FIG. 7, 8 is also set smaller than the width W2a. That is, the distance W1 is set according to the distance W2a so that a gap is formed between the convex portion 34 and the end portion 2421b when the fitting convex portion 34 is fitted into the fitting groove portion 2042. At the same time, the width W1 is set to be larger than the width W2b between the end portions 2421c (see also FIGS. 7 and 8) opposite to the end surface 402 of the inclined surface portions 2421a of the inner side surfaces 2421 of the respective fitting groove portions 2042. ing. Further, the radial distance D1 between the protrusion-side front end surfaces 340 of the fitting convex portions 34 is set to be substantially the same or slightly smaller than the radial distance D2 between the inner bottom surfaces 2420 of the fitting groove portions 2042. ing. With these settings, as shown in FIGS. 7 and 8, the joint portion 32 is formed between the intermediate portion 2421 d in the axial direction of the inclined surface portions 2421 a of both inner side surfaces 2421 of each fitting groove portion 2042, and between the fitting groove portions 42. The shaft main body 30 is connected to the planet carrier 2040 by being fitted between the inner bottom surfaces 2420.

  As shown in FIG. 8, also in the second embodiment, an elastic member 70 is interposed between the flange portion 47 of the planet carrier 2040 and the inner ring 61 of the rolling bearing 60. Due to the restoring force action from the elastic member 70, the planetary carrier 2040 is moved to the end face 402 side (left direction in FIG. 8) that is the fitting side of the joint portion 32 into each fitting groove portion 2042, and the inner ring 61 is connected to the bearing 60. Each side is biased toward the side that reduces the internal gap (the right direction in FIG. 8).

  According to the second embodiment described so far, each fitting groove portion 2042 that opens to the axial end surface 402 in the planetary carrier 2040 has a groove width that decreases as it moves away from the end surface 402 side, in other words, toward the end surface 402 side. Thus, the groove width is increased. Therefore, each fitting convex part 34 of the joint part 32 protruding at the rotating shaft 3 of the actuator 4 is easily fitted into the corresponding fitting groove part 2042 from the end face 402 side. Moreover, in the planetary carrier 2040 urged toward the end surface 402 side, the inclined surface portion 2421a that reduces the groove width as the inner surface 2421 of each fitting groove portion 2042 is inclined with respect to the axial direction and separated from the end surface 402 side. However, it is always pressed to the fitting convex part 34 of insertion from the end surface 402 side. Therefore, between the rotating shaft 3 and the planet carrier 40 that can reliably exert such pressing action, wear due to relative sliding and generation of abnormal noise due to collision are suppressed, so the second embodiment described above. In addition, it is possible to expect the same effect as in the first embodiment.

(Third embodiment)
As shown in FIG. 10, the third embodiment of the present invention is a modification of the first embodiment. In the third embodiment, the elastic member 3070 having a different arrangement position from the elastic member 70 of the first embodiment is provided between the flange portion 3057 that protrudes toward the inner peripheral side of the planetary gear 3050 and the outer ring 62 of the rolling bearing 60. Is interposed in the axial direction. The elastic member 3070 is pinched coaxially between the flange portion 3057 and the outer ring 62 in a compressed state, thereby applying a restoring force to both sides in the axial direction. Due to this restoring force action, the elastic member 3070 urges the outer ring 62 in the axial direction (left direction in FIG. 10) in which the rolling bearing 60 generates preload. Therefore, for the planetary carrier 40 in which the inner ring 61 connected to the outer ring 62 via the rolling element 63 is engaged with the flange portion 47, the end surface 402 side (the left side in FIG. 10) is the same direction as the outer ring 62 in the axial direction. Direction).

  Thus, in the rolling bearing 60 in which the outer ring 62 is urged, a preload is applied to reduce the gap between the inner and outer rings 61 and 62 and the rolling element 63. At the same time, in the planetary carrier 40 that is biased toward the end surface 402 side, the inclined surface portion of the inner bottom surface 420 of each fitting groove portion 42 that is inclined with respect to the axial direction and reduces the groove depth as the distance from the end surface 402 side increases. 420a is always pressed from the end surface 402 side to the fitting convex portion 34. Therefore, the third embodiment described above can be expected to exhibit the same effect as the first embodiment.

(Other embodiments)
Although a plurality of embodiments of the present invention have been described above, the present invention is not construed as being limited to these embodiments, and various embodiments and combinations can be made without departing from the scope of the present invention. Can be applied.

  Specifically, in the first and second embodiments, the elastic member 3070 described in the third embodiment may be employed in addition to or instead of the elastic member 70. Here, the modification of FIG. 11 shows an example in which an elastic member 3070 is employed in addition to the elastic member 70 in the first embodiment. In the first and third embodiments, the inner side surface 2421 having the inclined surface portion 2421a described in the second embodiment may be employed instead of at least one inner side surface 421 of each fitting groove portion 42. Here, the modification of FIG. 12 shows an example in which the inner side surface 2421 is employed in place of the inner side surfaces 421 in the first embodiment. Further, in the second embodiment, the inner side surface 421 described in the first embodiment may be employed instead of any one inner side surface 2421 of each fitting groove portion 2042. Furthermore, with respect to the inclined surface portions 420a and 2421a of the first to third embodiments, the groove depth of the fitting groove portion 42 or the groove width of the fitting groove portion 2042 is reduced as the distance from the end surface 402 of the planetary carriers 40 and 2040 increases. It may be formed in a curved shape. In addition, the fitting groove portions 42 and 2042 of the first to third embodiments may be opened in the outer peripheral surface 401 of the planetary carriers 40 and 2040 forming the connecting portion 41, and the fitting portion 32 is fitted on the fitting side. It does not need to be open to the end surface 403 of the planetary carriers 40 and 2040 on the opposite side.

  The rolling bearing 60 of the first to third embodiments may be a single type in which the rolling elements 63 are arranged in a row in the axial direction or a double type radial bearing in which three or more rows are arranged in the axial direction, or the rolling element 63 is a roller-shaped radial roller bearing. It may be a closed radial bearing closed between the inner and outer rings 61 and 62. The planetary gear mechanism 8 of the first to third embodiments is not limited to the mechanism in which the planetary gears 50 and 3050 are meshed and connected to the gear portions 18 and 22 of the rotating bodies 10 and 20. As long as the effect is obtained, planetary gear mechanisms having various structures may be employed. Furthermore, in the first to third embodiments, the pump 9 that introduces the lubricating oil into the internal space 100 of the rotating body 10 may be an electric pump that operates as the internal combustion engine rotates. Furthermore, in the first to third embodiments, the lubricating liquid introduced into the internal space 100 of the rotating body 10 may be a lubricating liquid dedicated to the apparatus 1 different from the engine lubricating oil.

  The actuator 4 of the first to third embodiments may be an electric brake such as an electromagnetic or a fluid brake, and in that case, a braking force is applied to the integral rotating shaft 3 that rotates by transmission of engine torque. Thus, the rotational drive of the shaft 3 may be realized. Moreover, about the rotating shaft 3 of 1st-3rd embodiment, the joint part 32 may be integrally formed in the shaft main-body part 30. FIG. And this invention is applied to the apparatus which adjusts the valve timing of the exhaust valve as a valve, and the apparatus which adjusts the valve timing of both an intake valve and an exhaust valve besides the apparatus which adjusts the valve timing of an intake valve Is possible.

DESCRIPTION OF SYMBOLS 1 Valve timing adjusting device, 2 Cam shaft, 2a Supply path, 3 Rotating shaft, 4 Actuator, 7 Energization control circuit part, 8 Planetary gear mechanism, 9 Pump, 10 Drive rotary body, 20 Driven rotary body, 21 Fixed part, 24 Introduction passage, 30 shaft main body part, 32 joint part, 33 sleeve part, 34 fitting convex part, 35 connecting pin, 40, 2040 planet carrier, 41 connecting part, 42, 2042 fitting groove part, 46 eccentric support part, 47, 3057 Flange, 50, 3050 Planetary gear, 51 Center hole, 60 Rolling bearing, 61 Inner ring, 62 Outer ring, 63 Rolling body, 70, 3070 Elastic member, 100 Internal space, 340 Projection side tip surface, 400, 500, 610 Peripheral surface, 401,620 Outer peripheral surface, 402,403 End surface, 420, 2420 Inner bottom surface (inner surface), 420a, 24 21a Inclined surface portion, 420b, 420c, 2421b, 2421c End portion, 420d, 2421d Intermediate portion, 421, 2421 Inner side surface (inner surface), D1, D2a, D2b, D2 radial distance, W1, W2, W2a, W2b width

Claims (6)

In a valve timing adjusting device for adjusting a valve timing of a valve that opens and closes a camshaft by torque transmission from a crankshaft in an internal combustion engine mounted on a vehicle, according to a rotational phase change between the crankshaft and the camshaft,
A rolling bearing in which rolling elements are interposed between the inner ring and the outer ring;
Planetary gears that cause the rotational phase change by planetary movement in a state supported by the outer ring;
A planetary carrier that planetarily moves the planetary gear by rotating in a revolving direction of the planetary gear with a fitting groove opening in an axial end surface and supporting the inner ring, and an inner surface of the fitting groove Is a planet carrier that is inclined with respect to the axial direction in a form that reduces the inner method of the fitting groove as it is separated from the end surface;
An actuator for rotating the planetary carrier in the revolving direction together with the rotating shaft, having a rotating shaft formed by projecting a joint portion inserted into the fitting groove portion from the end face side;
An elastic member that urges the inner ring or the outer ring in the axial direction to preload the rolling bearing and urges the planetary carrier in the axial direction toward the end face;
A valve timing adjusting device comprising:   2. The valve according to claim 1, wherein an inner bottom surface of the inner surface of the fitting groove portion is inclined with respect to an axial direction in such a manner that a groove depth as an inner method is reduced as the distance from the end surface is increased. Timing adjustment device.   The inner surface of the inner surface of the fitting groove portion is inclined with respect to the axial direction in such a form that the groove width as an inner method is reduced as the distance from the end surface increases. Valve timing adjustment device.   The elastic member is interposed between the planet carrier and the inner ring, thereby biasing the planet carrier toward the end face side opposite to the biasing direction of the inner ring in the axial direction. The valve timing adjusting device according to any one of claims 1 to 3, wherein   The elastic member is interposed between the planetary gear and the outer ring so that the planetary carrier supporting the outer ring is directed toward the end face side that is the same as the biasing direction of the outer ring in the axial direction. The valve timing adjusting device according to any one of claims 1 to 4, wherein the valve timing adjusting device is biased.   6. The roller bearing according to claim 1, wherein a space between the inner ring and the outer ring is opened inside a device to which a lubricating liquid is introduced as the internal combustion engine rotates. Valve timing adjustment device.

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