JP4877199B2 - Valve timing adjustment device - Google Patents

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.

  Conventionally, the rotating body that rotates in conjunction with the crankshaft and the rotating body that rotates in conjunction with the camshaft are linked by a planetary gear mechanism, and the valve timing is adjusted based on the relative phase between the rotating bodies. A known valve timing adjusting device is known (see Patent Documents 1 and 2). This type of valve timing adjusting device generates a control torque by torque generating means such as an electric motor, and uses the relative phase between the crankshaft and the camshaft (hereinafter referred to as “engine phase”) that determines the valve timing as the control torque. Adjust accordingly.

  In the case of using the differential gear mechanism mainly composed of the planetary gear as disclosed in Patent Document 1, the operating frequency of the mechanism that follows the operating state of the internal combustion engine becomes extremely high. In such cases, wear tends to occur.

  In addition, the planetary carrier as an input rotator that supports the planetary gears so as to freely move on the planetary gear and the output rotator of the electric motor are connected, and the engine phase is adjusted according to the control torque input from the electric motor to the planetary carrier. This is disclosed in Patent Document 2. In Patent Document 2, a joint mechanism that connects a pair of connecting protrusions that protrude to the opposite sides in the radial direction in the output rotating body of the electric motor and a pair of connecting recesses that open to the inner peripheral side in the planetary carrier. Adopted.

  In this joint mechanism, the pair of connecting protrusions are fitted into the pair of connecting recesses, respectively, so that the connecting protrusion and the connecting recess slide relative to each other, and the input rotating body, that is, the output rotating body of the planetary carrier. Although displacement in the radial direction is allowed, wear is likely to occur at the coupling fitting portion between the coupling projection and the coupling recess that are fitted by the planetary motion of the planetary gear.

Therefore, in the apparatus disclosed in Patent Document 1, the lubricating oil is introduced into the apparatus through the cam shaft, and the lubricating oil introduced into the apparatus includes a first lubricating path that lubricates the meshing portion of the gear, It branches and flows into a second lubrication path for lubricating the connection fitting portion of the joint mechanism, and is discharged from a predetermined discharge port provided in each path. The discharge port of the first lubrication path is provided in a rolling bearing that rotatably supports the planetary gear, and the lubricating oil is discharged from the bearing to the outside.
JP 2007-71057 A JP 2004-3419 A

  In the prior art disclosed in Patent Document 1, when the operating state of the internal combustion engine is in a low rotation range, the lubricating oil is supplied to the meshing portion of the gear and the coupling and fitting portion of the joint mechanism through both lubrication paths, so that a sufficient lubricating effect is obtained. It is possible to obtain. However, since the second lubrication path on the coupling mechanism side is arranged on the inner peripheral side with respect to the first lubrication path on the gear side, the centrifugal force of the rotating body that the lubricating oil receives increases as the internal combustion engine rotates at a higher speed. Therefore, the increased centrifugal force causes more lubricating oil to flow in the outer first lubricating path and to be discharged from the gear side. Therefore, the lubricating oil is less likely to flow into the connection fitting portion of the joint mechanism, the lubrication effect of the connection fitting portion is reduced, and wear may be promoted.

  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 having excellent durability.

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

That is, according to the first and second aspects of the present invention, in the valve timing adjusting device for adjusting the valve timing of at least one of the intake valve and the exhaust valve whose camshaft opens and closes by torque transmission from the crankshaft in the internal combustion engine, It has an output rotator provided with a protrusion, and is provided with a torque generating means for generating a control torque for rotationally driving the output rotator, and a connecting recess connected to the connecting protrusion to rotate integrally with the output rotator A phase adjusting mechanism that adjusts the relative phase between the crankshaft and the camshaft according to the control torque input to the input rotator from the output rotator, and rotates in conjunction with the crankshaft. The first rotating body, the second rotating body that rotates in conjunction with the camshaft and is supplied with lubricating fluid, and the teeth provided on at least one of the first rotating body and the second rotating body A planetary gear for changing the relative phase by a planetary motion while meshing with the part having a bearing, as well as discharging the lubricating fluid to the outside from the gap between the inner and outer rings of the bearing, the planetary motion planetary gear by a bearing A phase adjustment mechanism comprising a planet carrier as the input rotator that freely supports,
The bearing is provided with a restricting member that restricts the lubricating fluid flowing out to the outside at the other side of the gap in the rotation axis direction while the lubricating fluid that has flowed into the second rotating body is introduced at one side of the gap in the rotation axis direction. It is characterized by being.

As described above, according to the first and second aspects of the invention, in the output rotating body of the torque generating means, the connecting protrusion is connected to the connecting recess provided in the input rotating body of the phase adjusting mechanism, and the connecting protrusion and A joint mechanism is formed by the connecting recess. Here, the phase adjusting mechanism is fitted into a first rotating body and a second rotating body that are linked with the crankshaft and the camshaft, respectively, and a gear portion provided on at least one of the first rotating body and the second rotating body. In order to provide a planetary gear that changes the relative phase by planetary movement while being combined, and a planetary carrier that supports the planetary gear in a planetary motion freely by a rolling bearing, on the inner peripheral side of the planetary carrier as an input rotor, A connection protrusion and a connection recess are arranged, and a rolling bearing and a planetary gear are arranged on the outer peripheral side of the planet carrier.

  In such a phase adjustment mechanism, as the first rotating body and the second rotating body rotate in conjunction with the crankshaft and the camshaft, the lubricating fluid introduced into the second rotating body is subjected to the centrifugal force by the first rotating body. Although it is easy to move to the outer peripheral side of the first rotating body and the second rotating body, if the lubricating fluid that has moved to the outer peripheral side is discharged outside through the gap between the inner ring and the outer ring of the rolling bearing, the lubricating fluid There is a possibility that the joint protrusions and the joint recesses on the inner peripheral side of the joint will not be supplied to the joint mechanism.

In the first and second aspects of the invention, in addition to the configuration described above, the bearing is provided with a limiting member that restricts the lubricating fluid flowing out to the outside in any one of the rotation axis directions of the gap. Even if the lubricating fluid that has flowed into the second rotating body flows from one of the gaps in the direction of the rotation axis, the lubricating fluid can hardly flow out to the outside by the limiting member on the other side of the gap in the direction of the rotation axis. Thus, the lubricating fluid stored by the centrifugal force is discharged to the inner peripheral side of the planet carrier.

According to the first and second aspects of the present invention, the restricting member makes it difficult for the lubricating fluid to flow out from the gap of the bearing to the outside. Therefore, the lubricating fluid is stored in the planetary gear and the gear portion fitted to the planetary gear. Thus, the lubricating fluid can be easily discharged to the inner peripheral side of the planetary carrier so as to flow into the connecting projection and the connecting recess of the joint mechanism. Therefore, the connecting protrusion and the connecting recess of the joint mechanism are lubricated by the supply of the lubricating fluid even when the internal combustion engine rotates at a high speed and the centrifugal force increases. Wear can be avoided.

Further, according to the first aspect of the present invention, the restricting member extends toward the inner ring and shields the gap on the outer ring side between the inner ring and the outer ring.

  According to this, the lubricating fluid accumulated inside due to the centrifugal force generated by the rotation of the first rotating body and the second rotating body is such that the liquid surface on the inner peripheral side is on the outer ring side shielded by the limiting member in the gap of the bearing. Since the liquid level corresponding to the gap portion is expanded, the inner peripheral side liquid level is expanded and more accumulated lubricating fluid can be discharged to the inner peripheral side of the planet carrier, and the connection protrusion at the tip of the discharge is provided. The lubrication effect of the part and the connecting recess can be enhanced.

Further, according to the invention described in claim 1, one of the outer circumferential side rotor of the first rotating body and the second rotating body is provided with a support portion for supporting the outer ring, the support portion, the gap of the outer ring side characterized in that it forms a restriction member that shields.

  According to this, since the support part which supports an outer ring in the outer periphery side rotator of the first rotator and the second rotator forms the restricting member, the support member is in contact with the restricting member. One end face of the outer ring in the rotation axis direction is locked, and is formed to extend from the locking portion toward the inner ring so as to shield a gap on the outer ring side between the inner ring and the outer ring. Therefore, since the limiting member is formed integrally with the engaging portion of the outer peripheral rotating body at the support portion, the productivity of assembling work for assembling the phase adjusting mechanism can be enhanced.

Furthermore, according to the invention described in claim 2 , the connection recess is formed so as to penetrate the inner peripheral side of the planet carrier in the rotation axis direction, and the limiting member shields the gap between the inner ring and the outer ring and connects It protrudes to the opening part of the rotating shaft direction of a recessed part, It is characterized by the above-mentioned.

As described above, according to the second aspect of the present invention, the lubricating fluid discharged to the inner peripheral side of the planet carrier flows into the connecting recess formed through the inner peripheral side of the planet carrier in the rotation axis direction. However, there is a possibility that the lubricating fluid does not accumulate in the connecting recess and is discharged to the outside from the opening in the rotation axis direction. However, since the restricting member protrudes from the opening of the connecting recess, the restricting member makes it difficult for the lubricating fluid to flow out of the opening, thereby making it easy to collect the lubricating fluid in the connecting recess. It is.

In particular, according to the invention described in claim 3, limiting member, characterized in that it blocks the outer peripheral side of the opening in the connecting recess.

  According to this, the control member makes it difficult for the lubricating fluid to flow out from the clearance of the bearing to the outside, so that the lubricating fluid can be easily collected in the planetary gear and the gear portion, and is also blocked by the control member in the connecting recess. The lubricating fluid can be stored up to the liquid level corresponding to the outer peripheral portion of the opening. Therefore, the planetary gear and the gear portion, and the connecting protrusion and the connecting recess are reliably lubricated with the lubricating fluid, respectively, so that the lubrication effect can be exhibited and the durability can be enhanced.

According to a fourth aspect of the present invention, the limiting member is disposed between the inner ring and the outer ring so as to have a clearance gap in the direction of the rotation axis without contacting the inner ring and the outer ring.

Thus, according to the invention described in claim 4 , since the restricting member does not contact the inner ring and the outer ring between the inner ring and the outer ring, a state in which the lubricating fluid does not leak out to the outside from the clearance of the bearing is avoided. . In addition, since the flow rate of the lubricating fluid that leaks out from the bearing gap is adjusted by the separation gap, the bearing can be lubricated without causing a decrease in the durability of the bearing.

According to the fifth aspect of the present invention, the bearing includes a rolling element provided between the inner ring and the outer ring so as to be freely rotatable, and the rolling elements are arranged at a plurality of positions in a circumferential direction between the inner ring and the outer ring. It is characterized by.

  In the bearing having such a configuration, the circumferential clearance between adjacent rolling elements corresponds to the clearance of the bearing from which the lubricating fluid is discharged, but the circumferential clearance has no function of suppressing the flow of the lubricating fluid. Therefore, the lubricating fluid introduced into the inside of the device is discharged to the outside through the clearance of the bearing, and there is a possibility that the lubricating fluid may be inhibited from flowing to the device portion on the inner peripheral side of the bearing other than the clearance of the bearing. is there. However, if the restricting member restricts the lubricating fluid flowing out of the bearing gap, the lubricating fluid flows to the device portion on the inner peripheral side of the bearing while making it difficult to flow out of the bearing gap. Can be made easier.

According to a sixth aspect of the present invention, the input concave portion is formed in a cylindrical shape so that the connecting recess is connected to the connecting protrusion protruding to the pair of radially opposite sides by the pair of connecting recesses, respectively. It is a groove part which is provided in two places which mutually oppose on the inner peripheral side of a body, and a pair of connection projections are inserted along a diameter direction, and forms a clearance between a pair of connection projections. According to this, as the first rotating body and the second rotating body rotate in conjunction with the crankshaft and the camshaft in the phase adjustment mechanism, the swinging movement becomes easy, and the connecting protrusion is connected to the connecting recess. Although the sliding member is slid in the radial direction, in order to facilitate lubrication of the lubricating fluid to the connecting recess and the connecting protrusion of the joint mechanism on the inner peripheral side of the rolling bearing, The sliding wear of the connecting recess and the connecting protrusion can be avoided.

  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)
FIG. 2 shows a valve timing adjusting apparatus 1 according to the 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. The valve timing adjusting device 1 is a combination of the electric drive system 4 and the phase adjusting mechanism 8 and adjusts the engine phase between the crankshaft and the camshaft 2 that determines the valve timing. In the present embodiment, the camshaft 2 opens and closes an intake valve (not shown) of the internal combustion engine, and the valve timing adjusting device 1 adjusts the valve timing of the intake valve.

  First, the electric drive system 4 will be described. The electric drive system 4 includes an electric motor 5 and an energization control circuit 6.

  The electric motor 5 is, for example, a brushless motor or the like, and generates a control torque output from the rotating shaft body 7 by energization. The energization control circuit 6 includes, for example, a microcomputer and a motor driver, and is disposed outside and / or inside the electric motor 5. The energization control circuit 6 is electrically connected to the electric motor 5 and controls energization to the electric motor 5 in accordance with the operation status of the internal combustion engine. In response to this controlled energization, the electric motor 5 holds or increases or decreases the control torque output from the rotating shaft body 7.

  Next, the phase adjustment mechanism 8 will be described. The phase adjusting mechanism 8 includes a driving side rotating body 10, a driven side rotating body 20, a planetary carrier 40, and a planetary gear 50.

  As shown in FIGS. 2 to 4, the drive-side rotator 10 is formed by screwing a gear member 12 and a sprocket 13 both having a bottomed cylindrical shape on the same axis. The peripheral wall portion of the gear member 12 forms a drive-side internal gear portion 14 having a tip circle on the inner peripheral side of the root circle. The sprocket 13 is provided with a plurality of teeth 16 protruding outward in the radial direction. The sprocket 13 is linked to the crankshaft by winding an annular timing chain (not shown) between the teeth 16 and a plurality of teeth of the crankshaft. Therefore, when the engine torque output from the crankshaft is input to the sprocket 13 through the timing chain, the drive side rotator 10 rotates in conjunction with the crankshaft while maintaining a relative phase with respect to the crankshaft. At this time, the rotation direction of the drive-side rotator 10 is the counterclockwise direction of FIGS.

  As shown in FIGS. 2 and 3, the driven side rotating body 20 has a bottomed cylindrical shape, and is concentrically disposed on the inner peripheral side of the sprocket 13. The peripheral wall portion of the driven-side rotator 20 forms a driven-side internal gear portion 22 having a tip circle on the inner peripheral side of the root circle.

  As shown in FIG. 2, the bottom wall portion of the driven-side rotator 20 forms a connecting portion 24 that is coaxially bolted to the cam shaft 2 and connected. Due to the connection between the connecting portion 24 and the cam shaft 2, the driven side rotating body 20 can rotate while maintaining a relative phase with respect to the cam shaft 2 in conjunction with the cam shaft 2. On the other hand, it is relatively rotatable. The relative rotation direction in which the driven-side rotator 20 advances with respect to the drive-side rotator 10 is the direction X in FIGS. 3 and 4, and the driven-side rotator 20 is retarded with respect to the drive-side rotator 10. The relative rotation direction is the direction Y in FIGS.

  As shown in FIG. 2, the planetary carrier 40 has a cylindrical shape as a whole, and an input wall 42 to which control torque is input from the rotating shaft 7 of the electric drive system 4 is formed on one end side. The rotating shaft 7 is connected to the input wall 42 concentric with the rotating bodies 10 and 20. The input wall 42 is supported on the inner peripheral side of the mounting hole portion 17 of the gear member 12 via a rolling bearing 43. With this connection, the planet carrier 40 can rotate integrally with the rotating shaft 7 and can rotate relative to the rotating bodies 10 and 20.

  As shown in FIGS. 2 to 4, the planet carrier 40 further has a support wall 44 whose outer peripheral surface is eccentric with respect to the rotating bodies 10 and 20 on the end side opposite to the input wall 42. The support wall 44 is fitted on the inner peripheral side of the center hole 51 of the planetary gear 50 via a rolling bearing 45. By this fitting, the support wall 44 supports the planetary gear 50 so that the planetary gear 50 can move freely. Here, the planetary motion of the planetary gear 50 refers to the motion of the planetary gear 50 that revolves around the eccentric axis of the outer peripheral surface of the support wall 44 and revolves in the rotation direction of the support wall 44.

  The planetary gear 50 has a stepped cylindrical shape and is disposed concentrically with respect to the support wall 44. With this arrangement, the planetary gear 50 is always eccentric with respect to the gear portions 14 and 22 of the rotating bodies 10 and 20. In the planetary gear 50, a driving-side external gear portion 52 and a driven-side external gear portion 54 whose tip circles are on the outer peripheral side of the root circle are formed by a large-diameter portion and a small-diameter portion, respectively. The drive side external gear portion 52 is disposed on the inner peripheral side of the drive side internal gear portion 14 and meshes with the gear portion 14. The driven side external gear portion 54 is disposed on the inner peripheral side of the driven side internal gear portion 22 and meshes with the gear portion 22.

  With the above-described configuration, the phase adjustment mechanism 8 is formed with a differential gear type planetary mechanism 60 that decelerates the rotational motion of the planet carrier 40 and transmits it to the camshaft 2. The phase adjusting mechanism 8 having such a planetary mechanism unit 60 adjusts the engine phase according to the control torque input from the rotating shaft 7 to the planet carrier 40, so that the valve timing suitable for the internal combustion engine is obtained. Is realized.

  Specifically, when the planetary carrier 40 does not rotate relative to the drive-side rotator 10 due to the control torque being maintained or the like, the planetary gear 50 maintains the meshing position with the gear portions 14 and 22 and the rotator 10 and 20 rotate together. Therefore, the engine phase does not change, and as a result, the valve timing is kept constant.

  When the planetary carrier 40 rotates relative to the drive side rotor 10 in the direction X due to an increase in the control torque in the direction X or the like, the planetary gear 50 changes the meshing position with the gear portions 14 and 22 and performs planetary motion. As a result, the driven-side rotator 20 rotates relative to the drive-side rotator 10 in the direction X. Therefore, the engine phase changes to the advance side, and as a result, the valve timing advances.

  When the planetary carrier 40 rotates relative to the drive side rotor 10 in the direction Y due to an increase in the control torque in the direction Y or the like, the planetary gear 50 changes the meshing position with the gear portions 14 and 22 and performs planetary motion. As a result, the driven-side rotator 20 rotates relative to the drive-side rotator 10 in the direction Y. Therefore, the engine phase changes to the retard side, and as a result, the valve timing is retarded.

  Next, the characteristic part of 1st embodiment is demonstrated in detail. As shown in FIGS. 2 and 5, the rotating shaft 7 of the electric motor 5 is configured by combining a shaft member 70 and a joint member 72 as a joint mechanism.

  The shaft member 70 is made of metal and has a straight round bar shape. The shaft member 70 receives the control torque generated by the electric motor 5 and rotates in the circumferential direction.

  The joint member 72 is made of metal, and is formed, for example, by sintering a copper-containing alloy steel powder and performing a heat treatment. As shown in FIGS. 5 and 6, the joint member 72 is configured by combining two joint members 150 and 160.

  The first joint member 150 has an I-shape as a whole, and integrally includes a sleeve portion 152 and a connecting projection 154. The sleeve portion 152 is concentrically disposed on the inner peripheral side of the input portion 48. In the loose insertion hole 156 formed by the cylindrical hole-shaped inner peripheral hole, the sleeve portion 152 has one end portion of the shaft member 70 serving as a columnar output portion in the input / output axis direction (hereinafter also referred to as the rotation axis direction). It is inserted in the loose insertion form along. Thus, a clearance 158 is formed between the shaft member 70 and the loose insertion hole 156 on the outer peripheral side. A pair of connection protrusions 154 are provided in a form that protrudes from the sleeve portion 152 toward opposite sides in the input / output radial direction. Each connection protrusion 154 is fitted and connected to each groove 46 as a connection recess of the input portion 48 provided at a location facing each other in the input / output radial direction.

  The second joint member 160 is a cylindrical pin member, and penetrates the shaft member 70 and the sleeve portion 152 along the input / output radial direction. Here, the second joint member 160 is press-fitted and fixed to a cylindrical hole-shaped fixing hole 164 that is formed through the inner peripheral side portion of the sleeve portion 152 in the shaft member 70. On the other hand, as shown in FIG. 6, the second joint member 160 is slidable with respect to the cylindrical hole-shaped guide holes 166 and 167 formed through the sleeve portion 152 at two positions sandwiching the loose insertion hole 156. Has been inserted. Thus, sliding clearances 168 and 169 are formed between the guide holes 166 and 167 on the outer peripheral side of the second joint member 160.

  In the joint member 72 having such a configuration, the guide holes 166 and 167 and the second joint member 160 slide relative to each other, so that the shaft member 70 and the first joint member 150 are in the input / output radial direction within the range of the clearance 158. Can be displaced relatively. Thereby, between the shaft member 70 of the electric motor 5 and the planetary carrier 32, the mutual axial deviation and inclination are absorbed by the maximum clearance 158 minutes. As shown in FIG. 6, in this embodiment, the shaft member 70 and the first joint member 150 are arranged in the input / output radial direction Dr that is inclined within an acute angle range (for example, 30 °) with respect to the eccentric direction De of the eccentric portion 49. By setting the relative displacement direction, the effect of absorbing the misalignment and inclination between the elements 70 and 40 is enhanced.

  Next, a characteristic configuration of the lubrication structure will be described. As shown in FIGS. 2 and 3, the connection portion 24 of the driven-side rotator 20 according to the present embodiment has two introduction holes 90 for introducing lubricating oil as “lubricating fluid” into the drive-side rotator 10. Are provided at substantially equal intervals in the circumferential direction. Each introduction hole 90 is always in communication with the conveyance passage 3 of the camshaft 2 that conveys lubricating oil from the pump 9 for the internal combustion engine. As a result, the introduction hole 90 receives the lubricating oil from the transport passage 3.

  As shown in FIG. 1, the end of each introduction hole 90 on the side opposite to the transport passage 3 is on the inner peripheral side of the rolling bearings 43 and 45, and the side surface 24 a of the connecting portion 24 facing the planetary carrier 40 side in the axial direction. Is open. Thus, each introduction hole 90 is always in communication with the inside of the driving side rotating body 10 in the vicinity of the planet carrier 40, and the lubricating oil from the transport passage 3 is transmitted to the gear portion such as the driven side external gear portion 54 of the planetary rotating body 60. 14, 22, 52 and 54 are supplied.

  The lubricating oil supplied from the conveyance path 3 of the camshaft 2 is guided to the internal space 11 of the rotating bodies 10 and 20 through the introduction hole 90, but as described above, the side of the gear portions 14, 22, 52, 54, that is, the rotating body. In the internal space 11 of 10 and 20, it is easy to flow to the outer peripheral side. Further, since the centrifugal force of the rotating bodies 10 and 20 received by the lubricating oil increases as the internal combustion engine rotates at a higher speed, that is, as the number of rotations of the crankshaft and the camshaft 2 increases, the internal space 11 extends from the introduction hole 90. Lubricating oil that has flowed out to the flow is enhanced by the centrifugal force to flow toward the outer periphery of the rotating bodies 10 and 20.

  The lubricating oil flowing to the outer peripheral side in the rotating bodies 10 and 20 is discharged to the outside through the clearance of the rolling bearing 43. The clearance of the rolling bearing 43 is a clearance between the inner ring 43a and the outer ring 43b in the rolling bearing 43 configured by combining the inner ring 43a, the outer ring 43b, and a rolling element 43c such as a sphere, and more specifically, the inner ring 43a and the outer ring 43b. It is a gap in the axial direction (hereinafter referred to as the rotational axis direction) between the rolling conductors 43c, the inner ring 43a, and the outer ring 43b arranged at a plurality of positions over the circumferential direction. In other words, it is a circumferential clearance between adjacent rolling conductors 43c interposed between the inner ring 43a and the outer ring 43b.

  Therefore, in the present embodiment, as shown in FIGS. 1 and 2, the lubrication that flows out to the outside at one side of the clearance of the rolling bearing 43 in the rotation axis direction (the clearance on the left end side of the rolling bearing 43 in FIGS. 1 and 2). A restricting member 19 for restricting oil is provided. As shown in FIG. 2, the restricting member 19 is disposed in contact with one end surface (the left end surface in FIG. 2) in the rotation axis direction of the outer ring 43b, and is arranged on one end surface of the inner ring 43a side by side with the one end surface of the outer ring 43b. It is formed to extend toward. Thereby, the axial gap between the inner ring 43a and the outer ring 43b is shielded by the restricting member 19 extending from the outer ring 43b to the inner ring 43a on the inner peripheral side, and the opening area of the axial gap can be reduced. As a result, the lubricating oil flows to the outer peripheral side in the rotators 10 and 20, but the lubricating oil guided to the outer peripheral side is less likely to flow out from the gap of the rolling bearing 43 to the outside by the restricting member 19, so that the lubricating oil Oil accumulates on the outer peripheral side in the rotators 10 and 20. Further, the accumulated lubricating oil is easily discharged to the inner peripheral side of the rotating bodies 10, 20, that is, the inner peripheral side of the planetary carrier 40. Therefore, the lubricating oil accumulated on the joint mechanism 72 side on the inner peripheral side of the planetary carrier 40 is discharged, and the connecting projection 154 and the groove 46 are connected and lubricated with the lubricating oil.

  By restricting the lubricating oil flowing outside from the clearance of the rolling bearing 43 in this way by the restricting member 19, the internal combustion engine becomes high in rotation at the coupling protrusion 154 and the groove 46 of the joint mechanism 72, and the centrifugal force. Since the lubricating oil is supplied and lubricated even in the case of increasing, it is possible to avoid wear of the connecting projection 15 and the groove connected to each other.

  Further, since the limiting member 19 extends from the outer ring 43b to the inner ring 43a on the inner peripheral side as described above, the outer peripheral side of the axial gap between the inner ring 43a and the outer ring 43b (hereinafter also referred to as a gap portion on the outer ring 43b side). Shielded.

  Thereby, the inner peripheral side liquid level of the lubricating oil accumulated inside by the centrifugal force due to the rotation of the rotating bodies 10 and 20 is expanded to the liquid level corresponding to the gap portion on the outer ring 43b side shielded by the limiting member 19. Will be. Lubricating oil that has a larger inner peripheral liquid level and is stored in a larger amount can be discharged to the inner peripheral side of the planetary carrier 40, and lubrication of the connecting projection 154 and the groove 46 at the end of the discharge is possible. The effect can be enhanced.

  Moreover, in this embodiment, the said limitation member 19 is integrally formed with the gear member 12 of the drive side rotary body 10, as shown to FIG. The drive-side rotating body 10 supports the outer ring 43 b of the rolling bearing 43 on the inner peripheral side of the mounting hole 17 in the gear member 12, and the mounting hole 17 that supports the outer ring 43 b is one end surface of the rolling bearing 43. A locking portion 18 is provided to lock the locking portion 18, and the locking portion 18 and the limiting member 19 are integrally formed. By configuring the limiting member 19 in this way, the limiting member 19 is formed integrally with the locking portion 18 of the driving side rotating body 10, so that assembly work for assembling the phase adjusting mechanism 8 is produced. Can increase the sex.

  Further, the limiting member 19 is disposed in the inner ring 43a and the outer ring 43b of the rolling bearing 43 with a separation gap δ in the rotation axis direction without contacting at least the inner ring 43a.

  In some cases, the limiting member 19 extending toward the inner ring 43a overlaps one end surface of the inner ring 43a. In such a restricting member, since it does not contact the one end surfaces of both the inner ring 43a and the outer ring 43b, a state in which the lubricating oil does not leak to the outside from the gap of the rolling bearing 43 is avoided. Moreover, it is possible to adjust the flow rate of the lubricating oil leaking to the outside through the gap of the bearing 43 by adjusting the separation gap δ.

  In the present embodiment, since the phase adjustment mechanism 8 includes the planetary gear mechanism portion 60 of the operating gear type, as the rotating bodies 10 and 20 rotate in conjunction with the crankshaft and the camshaft 2, respectively, Since it becomes easy to swing, the shaft carrier 70 and the shaft member 70 are misaligned and tilted, or the connecting projection 154 of the shaft member 70 slides in the radial direction with respect to the groove 46 of the planet carrier 40. It will be.

  On the other hand, in this embodiment, the restricting member 19 makes it easy to lubricate the connecting protrusion 72 and the groove 46 of the joint mechanism 72 on the inner peripheral side of the rolling bearing 43. The sliding wear of the connecting projection 154 and the groove 46 can be avoided.

  Here, in the first embodiment, the electric motor 5 corresponds to “torque generating means” described in the claims, and the rotary shaft body 7 corresponds to “output rotating body” described in the claims. The planet carrier 40 corresponds to an “input rotator” described in the claims. The driving side rotating body 10 corresponds to a “first rotating body” described in the claims, and the driven side rotating body 20 corresponds to a “second rotating body” described in the claims. The internal gear portion 14 and the driven side internal gear portion 22 correspond to a “gear portion” recited in the claims. Further, the groove 46 corresponds to a “connection recess” described in the claims. The mounting hole portion 17 corresponds to a “support portion” described in the claims. The rolling bearing 43 corresponds to a “bearing” recited in the claims.

(Second embodiment)
As shown in FIG. 7, the second embodiment of the present invention is a modification of the first embodiment. In the second embodiment, the limiting member 19 is formed so as to overlap one end surfaces of the outer ring 43b and the inner ring 43a, but the inner peripheral side tip of the limiting member 10 is formed on the groove 46 on the further inner peripheral side of the inner ring 43a. A part of the opening 46a is blocked.

  As shown in FIG. 7, the opening 46 a of the groove 46 is formed so as to penetrate the inner peripheral side of the input wall 42 and the eccentric wall 44 of the planetary carrier 40 in the rotation axis direction. The limiting member 19 shields the gap between the outer ring 43 b and the inner ring 43 a and protrudes from the opening 46 a of the groove 46.

  When the opening 46a of the groove 46 is fully open, if the lubricating oil discharged to the inner peripheral side of the planet carrier 40 flows into the groove 46 of the planet carrier 40, the lubricating oil does not collect in the groove 46. There is a risk of being discharged from the opening 46a to the outside.

  However, in this embodiment, since the restricting member 19 protrudes into the opening 46a of the groove 46, the restricting member 19 makes it difficult for the lubricating oil to flow out of the opening 46a. Lubricating oil can be easily stored.

  Moreover, in the present embodiment, the limiting member 19 is formed so as to close the outer peripheral side of the opening 46 a in the groove 46. That is, the inner peripheral side tip, that is, the window portion of the limiting member 19 is formed in a circular opening smaller than the bottom of the groove 46.

  According to this, the control member 19 makes it difficult for the lubricating oil to flow out from the gap of the rolling bearing 43 to the outside, so that the lubricating oil can be easily stored in the gear portions 14, 22, 52, 54, and the planetary carrier 40 Lubricating oil can be accumulated up to the liquid level corresponding to the outer peripheral side portion of the opening 46 a that is blocked by the control member 19 in the groove 46. Accordingly, the gear portions 14, 22, 52, 54 of the rotating bodies 10, 20, and the connecting protrusion 154 and the groove portion 46 on the inner peripheral side of the planetary carrier 40 are reliably lubricated with the lubricating oil, so that the lubricating effect is exhibited. And durability can be improved.

  Here, although the limiting member 19 extending toward the inner ring 43a overlaps with one end surfaces of the outer ring 43b and the inner ring 43a, the limiting member 19 corresponding to one end surface of the outer ring 43b and the inner ring 43a is provided with a step 19a. The separation gap δ is secured.

  Such a restricting member avoids a state in which no lubricating oil leaks out from the gap of the rolling bearing 43 to the outside, and the lubricating oil leaks out from the gap of the bearing 43 by adjusting the separation gap δ. Can be adjusted to such a level that does not damage the rolling elements 43c, the inner ring 43a, and the outer ring 43b, so that the bearing can be lubricated without deteriorating the durability of the rolling bearing.

(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 can be applied to various embodiments without departing from the scope of the present invention. .

  For example, as the “torque generating means” that gives control torque to the planetary carrier 40, in addition to the electric motor 5, for example, an electric brake such as an electromagnetic brake or a fluid brake or a hydraulic motor may be used. For example, the connecting protrusion 154 connected to the planet carrier 40 may be formed directly on the output portion 104 itself of the motor shaft 102.

  In addition, in the first and second embodiments, the rotating shaft body 7 formed by fixing the joint member 72 to the shaft member 70 may be employed. For example, the shaft member 70 of the electric motor 5 may be fixed to the sleeve portion 152 of the first joint member 150 without providing the second joint member 160.

  Alternatively, in the first and second embodiments, the rotating shaft body 7 in which the connection protrusion 154 is directly formed on the shaft member 70 may be employed.

  In the first and second embodiments, various phase adjustment mechanisms can be employed as long as the effects of the present invention can be obtained. For example, a planetary gear is meshed with a gear portion provided on one of two rotating bodies that rotate in conjunction with the crankshaft and the camshaft, and the other of the rotating bodies is connected to the planetary gear. A phase adjustment mechanism or the like that changes the engine phase by being rotationally driven by planetary motion may be employed.

  The present invention can be applied not only to a device that adjusts the valve timing of the intake valve, but also to a device that adjusts the valve timing of the exhaust valve and a device that adjusts the valve timing of both the intake valve and the exhaust valve. it can.

It is a figure which shows the principal part of the valve timing adjustment apparatus by 1st embodiment of this invention. It is a figure which shows the valve timing adjustment apparatus by 1st embodiment of this invention, Comprising: 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. FIG. 6 is a cross-sectional view taken along line VI-VI in FIG. 5. It is sectional drawing which shows the principal part of the valve timing adjustment apparatus by 2nd embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve timing adjustment apparatus 2 Cam shaft 3 Conveyance path 4 Electric drive system 5 Electric motor (torque generation means)
7 Rotating shaft (output rotating body)
8 Phase adjustment mechanism 9 Pump 10 Drive side rotating body (first rotating body)
DESCRIPTION OF SYMBOLS 11 Internal space 12 Gear member 13 Sprocket 14 Drive side internal gear part (gear part)
17 Mounting hole (support)
18 Locking part 19 Limiting member 20 Driven side rotating body (second rotating body)
22 Driven side internal gear (gear)
40 Planetary carrier (input rotating body)
42 Input wall 43 Rolling bearing (bearing)
43a Inner ring 43b Outer ring 43c Rolling element 44 Support wall 46 Groove (connection recess)
50 planetary gear 60 planetary gear mechanism 70 shaft member 72 joint member (joint mechanism)
90 Introduction hole 150 First joint member 154 Connecting protrusion 160 Second joint member

Claims (6)

In 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,
A torque generating means for generating a control torque for rotating and driving the output rotator, the output rotator having a connecting projection;
A connection concave portion connected to the connection protrusion is provided and has an input rotator that rotates integrally with the output rotator, and the input rotator receives the control torque input from the output rotator. A phase adjusting mechanism for adjusting a relative phase between the crankshaft and the camshaft;
A first rotating body that rotates in conjunction with the crankshaft; a second rotating body that rotates in conjunction with the camshaft and that is supplied with lubricating fluid; and the first rotating body and the second rotating body A planetary gear that changes the relative phase by planetary movement while meshing with a gear portion provided on at least one of them, and a bearing, and the lubricating fluid is discharged to the outside through a gap between the inner ring and the outer ring of the bearing. A phase adjusting mechanism including a planet carrier as the input rotating body that discharges and supports the planetary gears by the bearings in a planetary motion manner;
With
In the bearing,
The lubricating fluid that has flowed into the second rotating body in one of the rotation axis directions of the gap is introduced,
A restricting member that restricts the lubricating fluid flowing out to the outside at the other of the gaps in the rotation axis direction is provided ,
The restricting member extends toward the inner ring and shields the gap on the outer ring side between the inner ring and the outer ring,
One of the outer peripheral rotating body of the first rotating body and the second rotating body includes a support portion that supports the outer ring,
The valve timing adjusting device according to claim 1, wherein the support portion forms the limiting member that shields the gap on the outer ring side .   In 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,
  A torque generating means for generating a control torque for rotating and driving the output rotator, the output rotator having a connecting projection;
  A connection concave portion connected to the connection protrusion is provided and has an input rotator that rotates integrally with the output rotator, and the input rotator receives the control torque input from the output rotator. A phase adjusting mechanism for adjusting a relative phase between the crankshaft and the camshaft;
  A first rotating body that rotates in conjunction with the crankshaft; a second rotating body that rotates in conjunction with the camshaft and that is supplied with lubricating fluid; and the first rotating body and the second rotating body A planetary gear that changes the relative phase by planetary movement while meshing with a gear portion provided on at least one of them, and a bearing, and the lubricating fluid is discharged to the outside through a gap between the inner ring and the outer ring of the bearing. A phase adjusting mechanism including a planet carrier as the input rotating body that discharges and supports the planetary gears by the bearings in a planetary motion manner;
With
  In the bearing,
  The lubricating fluid that has flowed into the second rotating body in one of the rotation axis directions of the gap is introduced,
  A restricting member that restricts the lubricating fluid flowing out to the outside at the other of the gaps in the rotation axis direction is provided,
  The connection recess is formed through the inner peripheral side of the planet carrier in the rotation axis direction,
  The valve timing adjusting device according to claim 1, wherein the limiting member shields a gap between the inner ring and the outer ring, and protrudes to an opening in a rotation axis direction of the connection recess. The valve timing adjusting device according to claim 2 , wherein the restricting member closes an outer peripheral side of the opening in the connection recess. Wherein the restriction member, the valve according to claim 2 or claim 3, characterized in that it is arranged with a spacing gap in the rotation axis direction without contact with the inner ring and the outer ring between the inner ring and the outer ring Timing adjustment device. The bearing includes a rolling element provided between the inner ring and the outer ring so as to freely roll.
The valve timing adjusting device according to any one of claims 1 to 4 , wherein the rolling elements are arranged at a plurality of locations in a circumferential direction between the inner ring and the outer ring. The connection recesses are connected to the connection projections protruding to a pair of radially opposite sides by the pair of connection recesses, respectively.
Provided at two locations facing each other on the inner peripheral side of the input rotating body having a cylindrical shape,
In any one of claims 1 to 5, characterized in that a groove portion for forming a clearance between the pair of connecting protrusions are inserted is along the radial direction of the pair of coupling projections The valve timing adjusting device described.

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