JP2012189050A - Valve timing adjustment device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve both noise suppression and productivity improvement.SOLUTION: This valve timing adjustment device includes: a first rotating body 10 in which a first inner gear part 12 is formed; a second rotating body 20 in which a second inner gear part 22 is formed coaxially with the first inner gear part 12; a first planetary gear 30 in which a first outer gear part 32 eccentric relative to the inner gear parts 12, 22 is formed and in which the gear part 32 performs planetary movement while meshing with the first inner gear part 12 at an eccentric side; a second planetary gear 40 in which a second outer gear part 42 eccentric to the opposite side of the first outer gear part 32 relative to the inner gear parts 12, 22 is formed and the gear part 42 performs planetary movement while meshing with the second inner gear part 22 at an eccentric side; a planetary carrier 50 having an outer peripheral surface 52 eccentric to the same side as the first outer gear part 32 relative to the inner gear parts 12, 22 and coaxially supporting the first planetary gear 30 by the outer peripheral surface 52; and an elastic member 60 held by the outer peripheral surface 52, biasing the second planetary gear 40 to the eccentric side of the second outer gear part 42, and biasing the planetary carrier 50 to the eccentric side of the outer peripheral surface 52.

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.

  Conventionally, a first rotating body and a second rotating body that rotate in conjunction with a crankshaft and a camshaft are linked by a planetary gear mechanism, and a rotational phase between the crankshaft and the camshaft (hereinafter referred to as “engine phase”). There is known a valve timing adjusting device that adjusts the valve timing in accordance with (1).

  For example, in the device disclosed in Patent Document 1, the common planetary gear is coaxial with respect to the first internal gear portion and the second internal gear portion that are coaxially formed on the individual first rotating body and the second rotating body. The first external gear portion and the second external gear portion that are formed are integrally eccentric and meshed on the eccentric side. In the disclosed device of Patent Document 1, as the planet carrier rotates in the revolution direction on the inner peripheral side of the planetary gear, the planetary gear coaxially supported by the planet carrier performs planetary motion. The engine phase that determines the valve timing changes. However, in the device disclosed in Patent Document 1, backlash due to manufacturing tolerances is caused at the meshing location between the first internal gear portion and the first external gear portion and the meshing location between the second internal gear portion and the second external gear portion. Since it inevitably occurs, there is concern about the generation of abnormal noise due to rattling.

  Therefore, in the device disclosed in Patent Document 2, an outer peripheral surface that is eccentric to the same side as the first external gear portion and the second external gear portion with respect to the first gear portion and the second gear portion is provided on the planet carrier, and the outer periphery is provided. The first external gear portion and the second external gear portion are biased toward the eccentric side by the elastic member held on the surface. According to the urging action of the device disclosed in Patent Document 2, the first external gear portion and the second external gear portion are respectively connected to the first internal gear portion and the second internal gear portion that mesh with each other on the eccentric side. Since the backlash can be eliminated by being pressed, it is possible to suppress the generation of abnormal noise at each meshing location.

JP 2007-71058 A JP 2009-13964 A

  However, when assembling the disclosed device of Patent Document 2, in order to simultaneously mesh the first external gear portion and the second external gear portion integrally formed with the planetary gears with the different internal gear portions, the external gear Accuracy is required for the degree of coaxiality between the parts and the internal gear parts, and the degree of contour of each gear part. As a result, the processing time of each gear portion increases, resulting in a decrease in productivity.

  The present invention has been made in view of the problems described above, and an object of the present invention is to provide a valve timing adjusting device that achieves both suppression of abnormal noise and improvement of productivity.

  According to a first aspect of the present invention, there is provided 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, comprising a first internal gear portion, A first rotating body that rotates in conjunction with one of the shaft and the cam shaft, and a second internal gear portion that is coaxial with the first internal gear portion, and that is linked with the other of the crankshaft and the cam shaft. And a first external gear portion that is eccentric with respect to the first internal gear portion and the second internal gear portion, and the first external gear portion is arranged on the eccentric side with the first internal gear portion. A first planetary gear that performs planetary movement while meshing, and a second external gear portion that is eccentric to the opposite side of the first external gear portion with respect to the first internal gear portion and the second internal gear portion are formed. The second planetary planetary motion while the outer gear portion meshes with the second inner gear portion on the eccentric side The outer peripheral surface is eccentric to the same side as the first external gear portion with respect to the first internal gear portion and the second internal gear portion, and the first planetary gear is coaxially arranged from the inner peripheral side by this outer peripheral surface. The planetary carrier to be supported and held by the outer peripheral surface on the inner peripheral side of the second planetary gear, bias the second planetary gear toward the eccentric side of the second outer gear portion, and bias the planetary carrier toward the eccentric side of the outer peripheral surface. And the planetary carrier rotates in the revolving direction of the first planetary gear and the second planetary gear, so that the engine phase is caused by the planetary movement of the first planetary gear and the second planetary gear. Change.

  In the present invention, the first planetary gear and the second planetary gear are formed separately from the first internal gear portion and the second internal gear portion that are coaxially formed on the individual first rotating body and the second rotating body. The first external gear portion and the second external gear portion to be engaged are eccentric to the opposite sides and mesh with each eccentric side. Here, the second planetary gear is urged toward the eccentric side of the second outer gear portion by the elastic member held on the outer peripheral surface of the planet carrier on the inner peripheral side thereof, so that the second planetary gear first The two external gear portions can be pressed against the second internal gear portion meshing on the eccentric side to eliminate backlash. Further, in the planetary carrier in which the elastic member is biased toward the eccentric side of the outer peripheral surface on the same side as the first outer gear portion with respect to each internal gear portion, the first planetary gear of the first planetary gear whose outer peripheral surface is coaxially supported from the inner peripheral side. About one external gear part, it can press against the 1st internal gear part mesh | engaged in the said eccentric side, and can eliminate a backlash. Further, when assembling the device, the first external gear portion and the second external gear portion formed on different planetary gears are simultaneously displaced with each other internal gear portion while being relatively displaced toward each eccentric side. Since adjustment is possible, the required accuracy with respect to the degree of contour of each gear part and the coaxiality between the internal gear parts can be reduced. According to the above, it is possible to exhibit both the effect of suppressing the generation of abnormal noise due to the disappearance of backlash and the effect of improving productivity due to a decrease in required accuracy.

  According to the second aspect of the present invention, the planetary carrier formed in a cylindrical shape supports the first planetary gear and holds the elastic member by the outer peripheral surface coaxially with the inner peripheral surface in the entire axial direction. .

  In this invention, the planet carrier that supports the first planetary gear by the outer peripheral surface and holds the elastic member is formed in a simple cylindrical shape having the outer peripheral surface coaxially with the inner peripheral surface in the entire axial direction. The processing accuracy of the planet carrier can be lowered. According to this, it can contribute to the improvement of productivity.

  According to a third aspect of the present invention, there is provided a planetary carrier having a rotation shaft coaxially with respect to the first internal gear portion and the second internal gear portion, and having a rotation shaft eccentric with respect to the inner peripheral surface. And an actuator that rotates in the revolving direction together with the rotation shaft.

  In the present invention, the first internal gear part and the second internal gear part are loosely fitted to the inner peripheral surface of a simple cylindrical planetary carrier in an eccentric state, so that The rotation shaft and the planet carrier can be rotated in the revolving direction. According to this, not only the processing accuracy of the planet carrier but also the accuracy of arrangement of the rotating shaft necessary for rotational driving of the planet carrier can be lowered, which can contribute to the improvement of productivity.

  According to a fourth aspect of the present invention, the first external gear portion and the second external gear portion are connected to each eccentric side so as to be relatively displaceable by being axially fitted to the first planetary gear and the second planetary gear. A connecting member is provided.

  In this invention, the connecting member is axially fitted to the first planetary gear and the second planetary gear, so that the eccentric form of the first external gear part and the second external gear part on the opposite side can be reliably maintained. . In addition, the first external gear portion and the second external gear portion having such an eccentric form are relatively displaced toward each eccentric side by receiving the biasing action of the elastic member, and are connected to each other internal gear portion. Since the meshing state can also be maintained, it is possible to contribute to suppressing the generation of abnormal noise by eliminating the backlash. Moreover, when assembling the device, the first external gear portion and the second external gear portion formed on different planetary gears are simultaneously displaced with each other internal gear portion while being relatively displaced toward each eccentric side. Since it can be adjusted, it can also contribute to an improvement in productivity due to a decrease in required accuracy.

It is a figure which shows the valve timing adjustment apparatus by one 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. FIG. 6 is a view showing a valve timing adjusting device according to a modification of the embodiment of the present invention, and is a cross-sectional view taken along line IV-IV in FIG. 5. It is the VV sectional view taken on the line of FIG.

  Hereinafter, an embodiment of the present invention will be described with reference to the drawings. FIG. 1 shows a valve timing adjusting apparatus 1 according to an 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. In the present embodiment, the camshaft 2 opens and closes an intake valve (not shown) of the “valve” of the internal combustion engine by transmitting engine torque. Therefore, the valve timing adjusting device 1 adjusts the valve timing corresponding to the engine phase of the camshaft 2 with respect to the crankshaft for each intake valve. Specifically, as shown in FIG. 1, the valve timing adjustment device 1 is configured by combining an actuator 4, an energization control circuit unit 7, a phase adjustment mechanism 8, and the like.

  The actuator 4 is composed of an electric motor such as a brushless motor in the present embodiment, and includes a case 5 fixed to a fixed node of the internal combustion engine and a rotating shaft 6 supported by the case 5 so as to be rotatable forward and backward. ing. The energization control circuit unit 7 includes an electronic circuit such as a drive driver and its control microcomputer, and is disposed outside and / or inside the case 5 and is electrically connected to the actuator 4. The energization control circuit unit 7 controls the rotational drive of the rotary shaft 6 by energizing the actuator 4 to adjust the valve timing to the timing according to the operating state of the internal combustion engine.

  The phase adjusting mechanism 8 includes a first rotating body 10, a second rotating body 20, a first planetary gear 30, a second planetary gear 40, a planet carrier 50, an elastic member 60, and a connecting member 70. The first rotating body 10 made of metal is formed in a hollow shape as a whole, and houses the other components 20, 30, 40, 50, 60, 70 of the phase adjusting mechanism 8 therein.

  The first rotating body 10 shown in FIGS. 1 to 3 has a cylindrical wall member 16 coaxially fastened between the gear member 11 and the sprocket member 14. The gear member 11 having a bottomed cylindrical shape has, on the peripheral wall portion, a first internal gear portion 12 having a tooth tip circle on the inner peripheral side of the root circle. The stepped cylindrical sprocket member 14 has a plurality of teeth 15 protruding in the radial direction from the peripheral wall portion in the rotational direction. The sprocket member 14 is linked to the crankshaft by passing a timing chain (not shown) between the teeth 15 and a plurality of teeth of the crankshaft. By connecting the sprocket member 14 and the crankshaft, the engine torque output from the crankshaft is transmitted to the sprocket member 14 through the timing chain, whereby the first rotating body 10 rotates in conjunction with the crankshaft. Therefore, the rotation direction of the first rotating body 10 is constant (counterclockwise in FIGS. 2 and 3).

  As shown in FIGS. 1 and 3, the second rotating body 20 made of metal having a bottomed cylindrical shape is coaxially arranged in a cylindrical wall member 16 having a cylindrical shape larger than that. The second rotating body 20 has a fixed portion 21 fixed on the camshaft 2 coaxially on the bottom wall portion. By fixing the fixing portion 21, the second rotating body 20 can rotate in conjunction with the camshaft 2 and can rotate relative to the first rotating body 10. Here, the rotation direction of the second rotary body 20 is the same direction as the first rotary body 10 (counterclockwise direction in FIG. 3).

  The 2nd rotary body 20 forms the 2nd internal gear part 22 which has a tooth tip circle in the inner peripheral side of a tooth root circle in a surrounding wall part. The second internal gear portion 22 is disposed coaxially with the first internal gear portion 12 in a state of being shifted toward the cam shaft 2 in the axial direction. The inner diameter of the second internal gear portion 22 is set smaller than the inner diameter of the first internal gear portion 12, and the number of teeth of the second internal gear portion 22 is set smaller than the number of teeth of the first internal gear portion 12. .

  As shown in FIGS. 1 and 2, the metal first planetary gear 30 having an annular plate shape has a first outer gear portion 32 having a tooth tip circle on the outer peripheral side of the root circle on the peripheral wall portion. ing. The first external gear portion 32 is arranged eccentrically in the radial direction with respect to the internal gear portions 12 and 22, and meshes with the first internal gear portion 12 on the eccentric side.

  As shown in FIGS. 1 and 3, the metal second planetary gear 40 having an annular plate shape has a second outer gear portion 42 having a tooth tip circle on the outer peripheral side of the root circle on the peripheral wall portion. ing. The second external gear portion 42 is shifted to the cam shaft 2 side in the axial direction with respect to the first external gear portion 32, and the first external gear portion in the radial direction with respect to the internal gear portions 12 and 22. It is eccentrically arranged on the opposite side to 32 and meshes with the second internal gear portion 22 on the eccentric side. The outer diameter of the second external gear portion 42 is set to be smaller than the outer diameter of the first external gear portion 32, and the number of teeth of the second external gear portion 42 and the first external gear portion 32 is engaged with each other. The number of teeth is set smaller than the number of teeth of the internal gear portion 22 and the first internal gear portion 12.

  As shown in FIGS. 1 to 3, the metal planet carrier 50 is formed in a cylindrical shape having an inner peripheral surface 51 and an outer peripheral surface 52 on the same axis in the entire region in the axial direction. The planetary carrier 50 is arranged eccentrically by the same amount to the same side as the first external gear portion 32 with respect to the internal gear portions 12 and 22, and with respect to the rotary shaft 6 coaxial with the internal gear portions 12 and 22. Is also eccentric. That is, from these configurations, the inner and outer peripheral surfaces 51 and 52 of the planetary carrier 50 are eccentric with respect to the inner gear portions 12 and 22 and the rotating shaft 6 and have a cylindrical surface shape coaxial with the first outer gear portion 32. Presents.

  The pair of fitting grooves 53 opened on the inner peripheral surface 51 of the planetary carrier 50 are linked to the joint portion 6a provided on the rotating shaft 6 in a loose fitting state in which a gap is fitted. The planetary carrier 50 can be driven to rotate together with the rotary shaft 6 by the actuator 4 and can be rotated relative to the internal gear portions 12 and 22 by the linkage of the fitting groove 53 and the joint portion 6a. .

  As shown in FIGS. 1 and 2, the outer peripheral surface 52 of the planet carrier 50 is coaxially fitted in the center hole 34 of the first planetary gear 30 at a portion including the axial end portion on the actuator 4 side. The outer peripheral surface 52 supports the first planetary gear 30 from the inner peripheral side so as to be capable of planetary movement by fitting with the center hole 34. Here, the planetary motion of the first planetary gear 30 is a planet that coincides with the central axis of the rotary shaft 6 while rotating around the eccentric axis E1 of the first outer gear portion 32 and the outer peripheral surface 52 with respect to the inner gear portions 12 and 22. It refers to a motion of revolving around the rotation axis R of the carrier 50.

  As shown in FIGS. 1 and 3, holding holes 54 for individually holding the elastic members 60 are opened in the outer peripheral surface 52 of the planetary carrier 50 including the axial end on the camshaft 2 side. . Each elastic member 60 is a metal leaf spring having a substantially V-shaped cross section, and is sandwiched between the corresponding holding hole 54 and the center hole 44 of the second planetary gear 40. Through the elastic member 60, the outer peripheral surface 52 supports the second planetary gear 40 from the inner peripheral side so as to be capable of planetary movement at the portion where the holding hole 54 is formed. Here, the planetary motion of the second planetary gear 40 refers to a motion of revolving around the rotational axis R of the planet carrier 50 while rotating around the eccentric axis E2 of the second external gear portion 42 with respect to the internal gear portions 12 and 22. .

  Each elastic member 60 generates a restoring force by elastically deforming between the planet carrier 50 and the second planetary gear 40. Here, as shown in FIG. 3, the elastic members 60 of the present embodiment disposed at symmetrical positions across the virtual plane P including the eccentric axes E1 and E2 of the external gear portions 32 and 42 are generated. A resultant force of the restoring force is applied to each of the second planetary gear 40 and the planet carrier 50 on the opposite side in the radial direction. By this restoring force action, the second planetary gear 40 is urged toward the eccentric side of the second outer gear portion 42 with respect to the inner gear portions 12, 22, while the planet carrier 50 is moved to the opposite side of the gear 40, that is, the inner gear. The outer peripheral surface 52 with respect to the portions 12 and 22 and the eccentric side of the first external gear portion 32 are biased.

  As shown in FIGS. 1 to 3, the metal connecting member 70 having an elongated cylindrical bar shape is on a virtual plane P including the rotation axis R of the planetary carrier 50 together with the eccentric axes E1 and E2 of the external gear portions 32 and 42. A pair is provided. Each connecting member 70 is disposed on both sides of the rotation axis R in the radial direction, that is, on the eccentric side of the first external gear portion 32 and the eccentric side of the second external gear portion 42. A portion of each connecting member 70 including an end portion in the axial direction on the actuator 4 side is fitted in the axial direction with respect to a corresponding one of the pair of first fitting holes 36 penetrating the first planetary gear 30. ing. Here, in the present embodiment, each connecting member 70 is fitted and fixed to each cylindrical fitting-like first fitting hole 36 in a press-fitted state. On the other hand, the portion of each connecting member 70 including the axial end on the camshaft 2 side is axially opposite to the corresponding one of the pair of second fitting holes 46 that penetrate the second planetary gear 40. It is mated. Here, in the present embodiment, each connecting member 70 is fitted to each of the elongated second fitting holes 46 extending along the virtual plane P so as to be slidable in the radial direction of the second planetary gear 40. ing. Each connecting member 70 connects the first external gear portion 32 and the second external gear portion 42 to each eccentric side so that they can be displaced relative to each other according to the fitting form in each of the second fitting holes 46. .

  With the above configuration, the phase adjusting mechanism 8 is configured to link the rotating bodies 10 and 20 via the planetary gear mechanism mainly composed of the planetary gears 30 and 40. In such a phase adjustment mechanism 8, the rotating shaft 6 is rotationally driven in the revolving direction of the planetary gears 30 and 40 together with the planetary carrier 50, whereby the engine phase is adjusted and a desired valve timing is obtained.

  Specifically, when the rotating shaft 6 is driven to rotate at the same speed as the first rotating body 10, the planetary carrier 50 does not rotate relative to the internal gear portions 12 and 22, so that both the planetary gears 30 and 40 are used. No planetary motion. As a result, the planetary gears 30 and 40 rotate with the planet carrier 50 and the rotating bodies 10 and 20, so that the engine phase does not change and the valve timing is maintained. On the other hand, when the rotating shaft 6 is rotationally driven at a higher speed than the first rotating body 10, the planetary carrier 50 rotates relative to the internal gear portions 12 and 22 toward the advance side, so that the planetary gears 30 and 40 are respectively Planetary movement. As a result, since the second rotary body 20 rotates relative to the first rotary body 10 toward the advance side, the engine phase changes to the advance side, and the valve timing advances. On the other hand, when the rotating shaft 6 is driven to rotate at a lower speed than the first rotating body 10 or is driven to rotate in the opposite direction to the first rotating body 10, the planet carrier 50 is moved with respect to the internal gear portions 12 and 22. Because of relative rotation toward the retarded angle, the planetary gears 30 and 40 each perform planetary motion. As a result, the second rotator 20 rotates relative to the first rotator 10 toward the retard side, so the engine phase changes to the retard side and the valve timing is retarded.

  As described so far, in the device 1, the external gear portions 32, 40 formed on the individual planetary gears 30, 40 with respect to the internal gear portions 12, 22 formed coaxially on the individual rotating bodies 10, 20. 42 is eccentric to the opposite side and meshes with each eccentric side. Here, since the second planetary gear 40 is urged toward the eccentric side of the second external gear portion 42 by each elastic member 60 held on the outer peripheral surface 52 of the planet carrier 50, the second external gear portion 42. Can be pressed against the second internal gear portion 22 meshing on the eccentric side to eliminate backlash. Further, in the planetary carrier 50 urged toward the eccentric side of the first external gear part 32 by each elastic member 60, the first external gear part 32 of the first planetary gear 30 whose outer peripheral surface 52 is coaxially supported from the inner peripheral side. Can be pressed against the first internal gear portion 12 meshing on the eccentric side to eliminate backlash.

  Here, in the device 1 in which the connecting member 70 is axially fitted to the planetary gears 30 and 40 to connect the external gear portions 32 and 42 to the opposite side of the external gear portions 32 and 42. The eccentric form can be reliably maintained. Further, the external gear portions 32 and 42 having such an eccentric shape are relatively displaced toward the respective eccentric sides by receiving the biasing action of the respective elastic members 60, and are engaged with the different internal gear portions 12 and 22, respectively. Since the state can also be maintained, the disappearance action of the backlash as described above is ensured. Moreover, the eccentric gears 32 and 42 formed on the different planetary gears 30 and 40 and need not have the same degree of coaxiality are relatively displaced toward the respective eccentric sides when the device 1 is assembled. The degree of meshing with the gear portions 12 and 22 can be adjusted simultaneously. Therefore, it is possible to reduce the required accuracy with respect to the contour degree of each gear portion 32, 42, 12, 22 and the coaxiality between the internal gear portions 12, 22.

  According to the above, it is possible to achieve both the effect of suppressing the generation of abnormal noise due to the disappearance of backlash and the effect of improving productivity due to a decrease in required accuracy. Furthermore, in the apparatus 1, the processing accuracy of the cylindrical planetary carrier 50 having the outer peripheral surface 52 coaxially with the inner peripheral surface 51 can be reduced in accordance with the simple shape in the entire axial direction. Can contribute to the improvement. In addition, in the apparatus 1, the rotary shaft 6 coaxial with the internal gear portions 12, 22 is loosely fitted to the inner peripheral surface 51 of the simple-shaped planet carrier 50 in an eccentric state. In addition, the planetary carrier 50 can be driven to rotate in the revolution direction. According to such an apparatus 1, not only the processing accuracy of the planetary carrier 50 but also the placement accuracy of the rotating shaft 6 necessary for rotational driving of the planetary carrier 50 can be reduced. This also contributes to the improvement of productivity. It can be done.

(Other embodiments)
Although one embodiment of the present invention has been described above, the present invention is not construed as being limited to the embodiment, and can be applied to various embodiments without departing from the gist of the present invention. it can.

  Specifically, the connecting member 70 may be fitted and fixed to the second planetary gear 40 in a press-fit state and slidably fitted to the first planetary gear 30, or may be slid on both the planetary gears 30 and 40. You may make it fit so that movement is possible. 4 and 5, the connecting member 70 may not be provided, and the eccentric form of the external gear portions 32, 42 toward the opposite side may be maintained only by the urging action of the elastic member 60. Further, the number of the elastic members 60 can be set as appropriate. For example, as shown in FIG. 5, the second planetary gear 40 and the planet carrier 50 are respectively connected by the restoring force generated by the only elastic member 60. It is good also as a structure biased to the eccentric side of the two external gear part 42, and the eccentric side of the outer peripheral surface 52 (1st external gear part 32).

  In addition, the rotating body 10 may be rotated in conjunction with the camshaft 2 and the rotating body 20 may be rotated in conjunction with the crankshaft. In addition, the planetary gear 40 is supported from the inner peripheral side by the outer peripheral surface 52 of the planet carrier 50 that is eccentric to the same side as the outer gear part 42 with respect to the inner gear parts 12, 22, and the planetary gear 30 is supported by the outer gear part. The elastic member 60 biased toward the eccentric side of 32 may be held by the outer peripheral surface 52 (in this case, “first” is referred to as “second” in the description of the above-described embodiment, and conversely “first” By replacing “two” as “first”, it can be considered as an embodiment corresponding to the invention described in the claims).

  In addition, as the actuator 4 that rotationally drives the planet carrier 50 together with the rotating shaft 6, for example, an electric brake other than the electric motor may be employed. In addition to the device that adjusts the valve timing of the intake valve, the present invention adjusts the valve timing of the exhaust valve as the “valve”, and the device that adjusts the valve timing of both the intake valve and the exhaust valve. It can be applied to.

DESCRIPTION OF SYMBOLS 1 Valve timing adjustment apparatus, 2 Cam shaft, 4 Actuator, 6 Rotating shaft, 6a Joint part, 7 Current supply control circuit part, 8 Phase adjustment mechanism, 10 1st rotary body, 11 Gear member, 12 1st internal gear part, 14 Sprocket member, 20 second rotating body, 22 second inner gear portion, 30 first planetary gear, 32 first outer gear portion, 34 center hole, 36 first fitting hole, 40 second planetary gear, 42 second outer Gear part, 44 Center hole, 46 Second fitting hole, 50 Planetary carrier, 51 Inner peripheral surface, 52 Outer peripheral surface, 53 Fitting groove, 54 Holding hole, 60 Elastic member, 70 Connecting member, E1, E2 Eccentric axis, P virtual plane, R rotation axis

Claims (4)

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,
A first rotating body that forms a first internal gear portion and rotates in conjunction with one of the crankshaft and the camshaft;
Forming a second internal gear portion coaxially with the first internal gear portion, and a second rotating body that rotates in conjunction with the other of the crankshaft and the camshaft;
A first external gear portion that is eccentric with respect to the first internal gear portion and the second internal gear portion is formed, and the first external gear portion makes a planetary movement while meshing with the first internal gear portion on the eccentric side. The first planetary gear,
A second external gear portion that is eccentric to the first internal gear portion and the second internal gear portion opposite to the first external gear portion is formed, and the second external gear portion is formed on the eccentric side on the first side. A second planetary gear that planetarily moves while meshing with the two internal gears;
The first internal gear portion and the second internal gear portion have an outer peripheral surface that is eccentric to the same side as the first external gear portion, and the outer peripheral surface allows the first planetary gear to be coaxial from the inner peripheral side. Planetary carrier that supports
The second planetary gear is held by the outer peripheral surface on the inner peripheral side, biases the second planetary gear toward the eccentric side of the second outer gear portion, and biases the planet carrier toward the eccentric side of the outer peripheral surface. An elastic member to be
The first planetary gear and the second planetary gear make a planetary motion as the planetary carrier rotates in the revolving direction of the first planetary gear and the second planetary gear, and the crankshaft and The valve timing adjusting device characterized in that a rotational phase between the cam shafts changes.   The planetary carrier formed in a cylindrical shape supports the first planetary gear and holds the elastic member by the outer peripheral surface that is coaxial with the inner peripheral surface in the entire axial direction. Item 2. The valve timing adjustment device according to Item 1. The planetary carrier having a rotation shaft coaxially with respect to the first internal gear portion and the second internal gear portion and having the rotation shaft eccentric with respect to the inner peripheral surface is loosely fitted to the rotation shaft. Together with an actuator for rotationally driving in the revolving direction,
The valve timing adjusting device according to claim 1, comprising: a valve timing adjusting device according to claim 1. A coupling member that couples the first external gear part and the second external gear part to each eccentric side so as to be relatively displaceable by axially fitting to the first planetary gear and the second planetary gear,
The valve timing adjusting device according to any one of claims 1 to 3, wherein the valve timing adjusting device is provided.

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