JP4200377B2 - Valve timing adjustment device - Google Patents

Description

  The present invention relates to a valve timing adjusting device for an internal combustion engine (hereinafter referred to as an engine) that adjusts an opening / closing timing (hereinafter referred to as a valve timing) of at least one of an intake valve and an exhaust valve.

  Conventionally, a valve timing adjusting device is provided in a transmission system that transmits torque of a drive shaft to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve in an engine, and the rotational phase of the driven shaft with respect to the drive shaft Adjust the valve timing by changing. As one type of such valve timing adjusting device, there is known a valve timing adjusting device that changes the rotational phase of a driven shaft with respect to a drive shaft using an electric motor (see, for example, Patent Document 1).

  In a valve timing adjusting device using an electric motor, for example, the rotating shaft of the electric motor is supported by a radial bearing. In this case, the outer ring of the radial bearing is locked by the case of the electric motor, the inner ring of the radial bearing is mounted on the rotating shaft of the electric motor, and axial preload is applied to the radial bearing.

Japanese Utility Model Publication No. 4-105906

In the motor of the valve timing adjusting device described above, a spring is used to apply a preload to the radial bearing. Conventionally, this spring is used to directly urge the outer ring or inner ring of the radial bearing so that the inner part of the case is urged. Is housed in. Therefore, various types of motors with different preloads must be prepared according to the specifications of the valve timing adjusting device, which reduces the cost and makes it difficult to adjust the preload after the motor is assembled. Yes.
An object of the present invention is to provide a valve timing adjusting device that improves cost and facilitates adjustment of a preload applied to a radial bearing after the motor is assembled.

According to the first aspect of the present invention, since the biasing member biases the rotating shaft body in the axial direction, the radial bearing whose outer ring is locked to the case is the rotating shaft body mounted on the inner ring of the radial bearing. Is pressed to apply an axial preload. Therefore, it is not necessary to house the urging member inside the case so as to urge the radial bearing directly. Therefore, in the first aspect of the present invention, the urging member is interposed between the exposed portion of the rotating shaft body exposed to the outside of the case and the phase changing portion. This facilitates replacement of the urging member and adjustment of the urging force, so that a preload according to the specifications of the valve timing adjusting device can be set when necessary while generalizing the electric motor. According to the first aspect of the present invention, the cost performance is improved and the preload to the radial bearing can be easily adjusted after the motor is assembled.
According to the second aspect of the present invention, the joint member that transmits the control torque to the input member of the phase change portion in the rotating shaft also functions as an exposed portion that receives the biasing force of the biasing member. Thereby, the number of parts can be reduced and cost efficiency can be improved.

When the energization circuit is disposed on the opposite side of the phase change portion across the rotating shaft body as in the invention described in claim 4, the phase change portion locks and a thrust load acts on the rotary shaft body. The rotating shaft body may be displaced in the axial direction toward the energizing circuit to damage or break the energizing circuit. However, according to the fourth aspect of the present invention, since the restricting means restricts the axial displacement of the rotating shaft body toward the energizing circuit, it is possible to prevent the energizing circuit from being damaged and broken.
According to the invention described in claim 5, the case for locking the outer ring of the radial bearing also functions as a restricting means for restricting the axial displacement of the rotating shaft body by contacting the exposed portion of the rotating shaft body. Thereby, the number of parts can be reduced and cost efficiency can be improved.

According to the sixth aspect of the present invention, the joint member that transmits the control torque to the input member of the phase change portion in the rotating shaft body is restricted from axial displacement by abutting against the case, and the biasing force of the biasing member It also functions as an exposed part. Thereby, the number of parts can be reduced and cost efficiency can be improved.
In addition, in the invention of Claims 4-6, it can also be made not to use the biasing member of the invention of Claims 1 and 2.

Hereinafter, embodiments 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 provided in a transmission system that transmits a drive torque of a crankshaft (not shown) as a drive shaft to a camshaft 2 as a driven shaft in a vehicle engine. The valve timing adjusting device 1 adjusts the valve timing of the intake valve or the exhaust valve of the engine by changing the rotational phase of the camshaft 2 with respect to the crankshaft.
The valve timing adjustment device 1 includes a motion conversion mechanism 10, a speed reduction mechanism 40, an electric motor 50, and an urging member 70.

First, the motion conversion mechanism 10 will be described. As shown in FIGS. 1 and 2, the motion conversion mechanism 10 includes a sprocket 11, an output member 16, arm members 20 and 21, a guide member 30, a movable member 34, and the like. In FIG. 2, hatching indicating a cross section is omitted.
The support portion 12 of the sprocket 11 is formed in a cylindrical shape concentric with the rotation center line O of the camshaft 2, and is supported on the outer peripheral wall of the output member 16. With this support, the sprocket 11 can rotate around the rotation center line O as a driving side rotating body and can rotate relative to the output member 16. The gear portion 13 of the sprocket 11 is formed in a cylindrical shape having a diameter larger than that of the support portion 12 and having a plurality of teeth 13a. A chain belt (not shown) is hung on the teeth 13a of the gear portion 13, and the driving torque of the crankshaft is transmitted to the sprocket 11 through the chain belt. The sprocket 11 to which the driving torque is transmitted rotates in the clockwise direction in FIG. 2 while maintaining the rotational phase with respect to the crankshaft. In the sprocket 11, the link portion 14 that connects the support portion 12 and the gear portion 13 is formed in an annular plate shape that is concentric with the rotation center line O.

  The output member 16 has a fixed portion 17 and a link portion 18. One end of the camshaft 2 is bolted to one end of the fixed portion 17. By this fixing, the output member 16 can rotate with the camshaft 2 as a driven-side rotating body and can rotate relative to the sprocket 11. The two link portions 18 are arranged in a form protruding radially outward from two locations sandwiching the rotation center line O of the fixed portion 17 and are each formed in a rectangular plate shape.

  The arm members 20 and 21 are sandwiched together with the link portion 18, the guide member 30, the movable member 34, and the planetary gear 43 and the transmission member 46 by the cover 15 and the link portion 14 fixed to the gear portion 13. Yes. Two arm members 21 are arranged on both sides of the rotation center line O, and each is formed in a C-shaped flat plate shape. One end portion of each arm member 21 is connected to the corresponding link portion 18 via the shaft member 24, thereby forming a counter pair 25 with the corresponding link portion 18. A movable member 34 is fitted through the other end of each arm member 21. As shown in FIGS. 2 and 3, two arm members 20 are disposed on both sides of the rotation center line O, and each is formed in an oval flat plate shape. One end portion of each arm member 20 is connected to a corresponding portion of the two portions sandwiching the rotation center line O of the link portion 14 via the shaft member 22, thereby forming a counter pair 23 with the link portion 14. . The other end of each arm member 20 is connected to the corresponding arm member 21 via the movable member 34, thereby forming a counter pair 26 with the corresponding arm member 21.

  As shown in FIGS. 1 and 4, the guide member 30 is formed in a circular plate shape concentric with the rotation center line O and supported by the outer peripheral wall of the output member 16. With this support, the guide member 30 can rotate around the rotation center line O and can rotate relative to the sprocket 11. One plate surface 30a of the guide member 30 is in contact with each arm member 21 so as to be slidable relative to each other, and faces the plate surface of each arm member 20, each link portion 18, and each link portion 14. Long holes 31 that penetrate the guide member 30 in the plate thickness direction are formed at two locations on the guide member 30 across the rotation center line O. The guide passage 32 formed by each long hole 31 on the inner peripheral side is inclined with respect to the radial axis of the guide member 30 and extends in a curved shape, and the radial distance from the rotation center line O changes in the extending direction. It is made into a shape.

  As shown in FIGS. 1 and 3, two movable members 34 are provided corresponding to the long holes 31. Each movable member 34 is formed in a cylindrical shape having a center line parallel to the rotation center line O, and is sandwiched between the transmission member 46 and the link portion 14. One end of each movable member 34 is fitted to the corresponding elongated hole 31 from both sides in the width direction of the guide passage 32, and can be relatively slid in the longitudinal direction of the guide passage 32. The other end side of each movable member 34 is fitted to the corresponding arm member 20, 21 so as to be relatively rotatable.

  In the motion conversion mechanism 10 in which the elements 11, 16, 20, 21, 30, and 34 are linked in this way, the output member 16 rotates in the clockwise direction in FIG. 2 as the crankshaft rotates. During this rotation, the motion conversion mechanism 10 converts the relative rotational motion of the guide member 30 relative to the sprocket 11 into the motion of the movable member 34, and further converts the motion of the movable member 34 into the relative rotational motion of the output member 16 relative to the sprocket 11. . By this conversion action, the rotational phase of the camshaft 2 with respect to the crankshaft (hereinafter referred to as the shaft phase) changes.

  Specifically, when the guide member 30 does not rotate relative to the sprocket 11, the movable member 34 does not guide the guide passage 32 and rotates together with the guide member 30. At this time, the positions of the turning pair 26 formed by the arm members 20 and 21, the turning pair 25 formed by the link portion 18 and the arm member 21, and the turning pair 23 formed by the link portion 14 and the arm member 20 do not change. As a result, since the output member 16 rotates together with the camshaft 2 while maintaining the rotational phase with respect to the sprocket 11, the shaft phase is kept constant.

  When the guide member 30 rotates relative to the sprocket 11 in the advance angle direction X, the movable member 34 is guided along the guide passage 32 and separated from the rotation center line O. At this time, the arm member 20 rotates relative to the link portion 14 and the arm member 21 around the center line of the shaft member 22 and the movable member 34 respectively, and rotates around the position of the pair 26 according to the movement of the movable member 34. Move away from center line O. At the same time, the arm member 21 rotates relative to the link portion 18 around the center line of the shaft member 24, and turns around the position of the turning pair 25 according to the movement of the movable member 34 and retards the position of the turning pair 23. Approach in direction Y. As a result, since the output member 16 rotates relative to the sprocket 11 in the retarding direction Y, the shaft phase changes to the retarding side.

  When the guide member 30 rotates relative to the sprocket 11 in the retarding direction Y, the movable member 34 is guided through the guide passage 32 and approaches the rotation center line O. At this time, the arm member 20 rotates relative to the link portion 14 and the arm member 21 around the center line of the shaft member 22 and the movable member 34 respectively, and rotates around the position of the pair 26 according to the movement of the movable member 34. Move closer to the center line O. At the same time, the arm member 21 rotates relative to the link portion 18 around the center line of the shaft member 24, and rotates around the position of the pair 25 according to the movement of the movable member 34, and advances with respect to the position of the pair 23. Release in direction X. As a result, since the output member 16 rotates relative to the sprocket 11 in the advance angle direction X, the shaft phase changes to the advance angle side.

Next, the speed reduction mechanism 40 will be described. As shown in FIGS. 3 and 5, the speed reduction mechanism 40 includes an input member 41, a sun gear 42, a planetary gear 43, bearings 44 and 45, a transmission member 46, and the like.
The input member 41 is formed in a stepped cylindrical shape, and has a concentric part 41 a concentric with the rotation center line O and an eccentric part 41 b eccentric with respect to the rotation center line O aligned in the axial direction. The concentric part 41 a is supported on the inner peripheral wall of the output member 16 via a bearing 44. With this support, the input member 41 can rotate around the rotation center line O and can rotate relative to the sprocket 11. Two guide holes 41c are formed in the eccentric portion 41b on the electric motor 50 side from the concentric portion 41a so as to sandwich the rotation center line O and open to the inner peripheral surface of the eccentric portion 41b and the end surface opposite to the concentric portion 41a. ing. As will be described in detail later, the joint member 63 of the rotating shaft 60 of the electric motor 50 is fitted and mounted in the guide hole 41 c, and the control torque is transmitted to the input member 41 through the joint member 63.

The sun gear 42 is composed of an internal gear whose tooth tip curved surface is on the inner peripheral side of the tooth bottom curved surface, and is concentrically fixed to the inner peripheral wall of the gear portion 13. The sun gear 42 together with the sprocket 11 rotates around the rotation center line O in the clockwise direction of FIG.
The planetary gear 43 is composed of an external gear whose tooth tip curved surface is on the outer peripheral side of the tooth bottom curved surface. The planetary gear 43 has a radius of curvature of the tip curved surface that is smaller than the curvature radius of the bottom surface of the sun gear 42, and the number of teeth of the planetary gear 43 is one less than the number of teeth of the sun gear 42. The planetary gear 43 meshes with the inner peripheral side of the sun gear 42 so as to be capable of planetary movement. An eccentric portion 41 b is fitted in a cylindrical hole 47 formed concentrically with the planetary gear 43 via a bearing 45 so as to be relatively rotatable.

  The transmission member 46 is formed in an annular plate shape concentric with the rotation center line O, and is fixed to the side opposite to the plate surface 30 a of the guide member 30. Thereby, the transmission member 46 can rotate together with the guide member 30 and can rotate relative to the sprocket 11. A plurality of cylindrical hole-like engagement holes 48 are formed in the transmission member 46. The respective engagement holes 48 are arranged at equal intervals around the rotation center line O and penetrate the transmission member 46 in the plate thickness direction. The planetary gear 43 is integrally formed with a plurality of engaging protrusions 49 protruding in a columnar shape from a portion facing the engaging hole 48. The engagement protrusions 49 are arranged at equal intervals around the center line P of the eccentric portion 41 b and protrude into the corresponding engagement holes 48.

  In such a speed reduction mechanism 40, when the rotating shaft 60 does not rotate relative to the sprocket 11, the planetary gear 43 maintains the meshing position with the sun gear 42 as the crankshaft rotates, and the sprocket 11 and the input member 41. At the same time, it rotates clockwise in FIG. As a result, the engagement protrusion 49 presses the engagement hole 48 in the rotation direction, so that the transmission member 46 together with the guide member 30 rotates in the clockwise direction in FIG.

  When the rotary shaft 60 rotates relative to the sprocket 11 in the counterclockwise direction of FIG. 5 due to an increase in control torque or the like, the planetary gear 43 rotates relative to the input member 41 in the clockwise direction of FIG. Meanwhile, the meshing position with the sun gear 42 is changed. As a result, the force by which the engagement protrusion 49 presses the engagement hole 48 in the rotation direction increases, and thus the transmission member 46 rotates relative to the sprocket 11 in the advance angle direction X together with the guide member 30.

When the rotary shaft 60 rotates relative to the sprocket 11 in the clockwise direction of FIG. 5 due to an increase in control torque or the like, the planetary gear 43 rotates relative to the input member 41 in the counterclockwise direction of FIG. Meanwhile, the meshing position with the sun gear 42 is changed. As a result, the engaging protrusion 49 presses the engaging hole 48 in the counter-rotating direction, so that the transmission member 46 together with the guide member 30 rotates relative to the sprocket 11 in the retarding direction Y.
As described above, in the present embodiment, the speed reduction mechanism 40 and the motion conversion mechanism 10 jointly constitute the phase change unit described in the claims.

Next, the electric motor 50 will be described. As shown in FIG. 1, the electric motor 50 has radial bearings 51 and 52, a case 53, a rotating shaft body 60, a stator 66, a drive circuit 69, and the like.
The radial bearings 51 and 52 are radial ball bearings in which balls 51c and 52c as rolling elements are sandwiched between outer rings 51a and 52a and inner rings 51b and 52b. The outer rings 51 a and 52 a and the inner rings 51 b and 52 b of the radial bearings 51 and 52 are aligned with the rotation center line O. The radial bearing 51 is disposed on the reduction mechanism 40 side of the radial bearing 52.

  The case 53 includes a combination of a sleeve 54, a plate 55, a cover 56, a retainer 57, and a connector 58, and is fixed to the engine through a stay (not shown) so as not to be displaced. The sleeve 54 is formed in a stepped cylindrical shape which is concentric with the rotation center line O and has a smaller diameter toward the speed reduction mechanism 40 side. In the sleeve 54, the restriction portion 54 a closest to the speed reduction mechanism 40 locks the outer ring 51 a of the radial bearing 51. In the sleeve 54, a stator 66 is accommodated in an accommodating portion 54b having a diameter larger than that of the restricting portion 54a. A plate 55 is fixed to the sleeve 54 on the opposite side of the accommodating portion 54b from the restricting portion 54a. A locking hole 55 a that opens on the sleeve 54 side in the plate 55 is formed in a cylindrical hole concentric with the rotation center line O, and locks the outer ring 52 a of the radial bearing 52. In the present embodiment, the outer ring 52a forms a clearance with the inner peripheral wall of the radially outer locking hole 55a, so that the rotating shaft 60 in the electric motor 50 can be aligned. The drive circuit 69 is accommodated in the accommodation hole 55b that opens to the opposite side of the sleeve 54 in the plate 55, and the drive circuit 69 is fixed to the fixing part 55c that forms the bottom wall surface of the accommodation hole 55b. The cover 56 is fixed to the plate 55 and covers the accommodation hole 55b. The retainer 57 is disposed on the opposite side of the cover 56 from the plate 55, and is fixed to the plate 55 together with the cover 56. The connector 58 is held between the retainer 57 and the plate 55. A terminal 59 connected to the drive circuit 69 is embedded in the connector 58.

The rotating shaft body 60 is formed by combining a shaft member 61, a rotor member 62, and a joint member 63. The shaft member 61 is formed in a rod shape concentric with the rotation center line O. Inner rings 51b and 52b of the radial bearings 51 and 52 are respectively mounted by press-fitting or the like at two locations separated from each other in the axial direction of the shaft member 61. By this mounting, the shaft member 61 can rotate around the rotation center line O together with the inner rings 51b and 52b. One end portion 61 a of the shaft member 61 protrudes toward the speed reduction mechanism 40 from the restriction portion 54 a of the sleeve 54. The end face of the other end portion 61b of the shaft member 61, the fixed portion 55c is receiving bore 55b relative to the bottom wall surface of the engaging hole 55a to be formed on the opposite side, facing at a clearance C ₁ in the axial direction Yes. As a result, the drive circuit 69 fixed to the fixed portion 55 c is located on the opposite side of the rotating shaft body 60 from the speed reduction mechanism 40. A rotor member 62 is mounted at a position between the mounting portions of the inner rings 51b and 52b in the shaft member 61. By this mounting, the rotor member 62 can rotate together with the shaft member 61. As shown in FIGS. 1 and 6, the rotor member 62 is formed in a circular plate shape concentric with the rotation center line O by laminating a plurality of iron pieces. A plurality of permanent magnets 64 are embedded in the rotor member 62. The permanent magnets 64 are arranged at equal intervals around the rotation center line O.

As shown in FIGS. 3 and 8, a restricting portion 54a enters the inner peripheral side of the flange portion 63a formed in the annular plate shape as shown in FIG. In the joint member 63, a mounting portion 63b protruding from the flange portion 63a toward the speed reduction mechanism 40 is formed in a cylindrical shape as shown in FIG. 7, and a shaft is provided on the inner peripheral side of the mounting portion 63b as shown in FIG. The end 61a of the member 61 is fitted concentrically. A connection pin 65 is fitted perpendicularly to the rotation center line O between the mounting portion 63 b and the end portion 61 a of the shaft member 61. As a result, the joint member 63 is attached to the end portion 61 a of the shaft member 61 so as to be exposed to the outside of the case 53, and can be rotated together with the shaft member 61. That is, the joint member 63 corresponds to the exposed portion described in the claims. The end face of the mounting portion 63b facing the inner peripheral side space of the flange portion 63a with respect to the distal end surface of the restricting portion 54a, are facing at a clearance C ₂ in the axial direction. In the present embodiment, the clearance C ₂ is set smaller than the clearance C ₁ described above. As shown in FIG. 7, the two connection portions 63c of the joint member 63 are formed in a flat plate shape that protrudes radially outward from two locations across the rotation center line O of the mounting portion 63b. As shown in FIG. 5, each connecting portion 63c is fitted in the corresponding guide hole 41c of the eccentric portion 41b. By this fitting, the eccentric portion 41b is mounted eccentrically with respect to the joint member 63, and both the input member 41 and the rotating shaft body 60 can rotate around the rotation center line O.

  As shown in FIGS. 1 and 6, the stator 66 is disposed on the outer peripheral side of the rotor member 62, and is fixed to the inner peripheral wall of the accommodating portion 54b. Thereby, the stator 66 cannot be displaced with respect to the engine. The core 67 of the stator 66 is formed by laminating a plurality of iron pieces, and a plurality of cores 67 are arranged around the rotation center line O at equal intervals. A coil 68 is wound around each core 67 in the stator 66. A coil 68 wound around each core 67 is connected to a drive circuit 69.

The drive circuit 69 is an electric circuit that is connected through a terminal 59 to a control circuit (not shown) disposed outside the case 53. The drive circuit 69 energizes a predetermined coil 68 in accordance with a control signal received from the control circuit. By this energization, a rotating magnetic field is formed on the outer peripheral side of the rotor member 62, and each permanent magnet 64 receives the action of the rotating magnetic field. As a result, the control torque in the advance direction X or the retard direction Y according to the direction of the rotating magnetic field is applied to the rotating shaft body 60 and transmitted to the input member 41. Note that the control circuit may have only a function of generating a control signal, or may have a function of generating a control signal and other functions, for example, a function of controlling the engine.
As described above, in the present embodiment, the stator 66 corresponds to the electromagnetic unit described in the claims, and the drive circuit 69 corresponds to the energization circuit described in the claims.

  Next, the urging member 70 will be described. As shown in FIGS. 3 and 8, the urging member 70 is an annular plate spring washer, and is interposed between the end surface of the flange portion 63a on the mounting portion 63b side and the tip end surface of the eccentric portion 41b. In the present embodiment, the urging member 70 is disposed substantially concentrically with respect to the center line P of the eccentric portion 41b. Since the urging member 70 is interposed between the joint member 63 and the input member 41 in an elastically deformed state, a restoring force is applied to the joint member 63. Due to the action of the restoring force, the rotating shaft body 60 is urged in the axial direction toward the opposite side of the speed reduction mechanism 40, that is, in the axial direction from the radial bearing 51 side toward the radial bearing 52 side. Therefore, the radial bearing 52 in which the outer ring 52 a is locked to the case 53 on the front side in the direction in which the rotating shaft body 60 is urged is pressed by the rotating shaft body 60 mounted on the inner ring 52 b of the radial bearing 52. Axial preload is applied.

  According to the valve timing adjusting device 1 described above, it is possible to apply preload to the radial bearing 52 without housing the urging member 70 inside the case 53 of the electric motor 50. In addition, since the biasing member 70 is interposed between the joint member 63 exposed to the outside of the case 53 and the input member 41, the replacement of the biasing member 70 and the adjustment of the restoring force are facilitated. Therefore, it is possible to set a preload according to the specifications of the valve timing adjusting device 1 when necessary, while making the electric motor 50 versatile. According to such a valve timing adjusting device 1, cost efficiency can be improved and preload adjustment to the radial bearing 52 can be easily performed after the electric motor 50 is assembled.

  Further, according to the valve timing adjusting device 1, the biasing member 70 is not housed inside the case 53 of the electric motor 50, so that the axial length of the electric motor 50 can be shortened. In addition, since the biasing member 70 is installed using a dead space between the joint member 63 and the input member 41, the axial length of the entire valve timing adjusting device 1 can be shortened. it can.

Further, according to the valve timing adjusting device 1, when the speed reduction mechanism 40 or the motion conversion mechanism 10 is locked and a thrust load is applied to the rotary shaft body 60, the rotary shaft body 60 moves in the axial direction toward the side opposite to the speed reduction mechanism 40. There is a risk of displacement. However, since the clearance _{C 2} between the restricting portion 54a and the joint member 63 of the case 53 than the clearance _{C 1} between the fixing portion 55c and the shaft member 61 of the case 53 is small, the rotational shaft 60 is fixed portion 55c The axial displacement is regulated by contacting the regulating part 54a earlier. By this displacement restriction, it is possible to avoid the rotating shaft body 60 from coming into contact with the fixed portion 55c to which the drive circuit 69 is fixed, so that the drive circuit 69 can be prevented from being damaged or broken. As described above, the restricting portion 54a corresponds to the restricting means described in the claims.

  Furthermore, according to the valve timing adjusting device 1, the case 53 has not only a function of locking the outer rings 51 a, 52 a of the radial bearings 51, 52 and a function of housing the drive circuit 69 and the stator 66, but also the rotating shaft body 60. Also functions to regulate the axial displacement of the. Further, the joint member 63 exhibits not only a function of transmitting control torque to the input member 41 attached thereto, but also a function of contacting the case 53 so that the axial displacement of the rotary shaft body 60 is restricted. By using the case 53 and the joint member 63 that exhibit such a plurality of functions, the number of parts is reduced and the cost is further improved.

Although one embodiment of the present invention has been described above, the present invention is not construed as being limited to that embodiment.
For example, with respect to the urging member 70, an appropriate portion is provided as long as it is between the phase change portion including the speed reduction mechanism 40 and the motion conversion mechanism 10 and the exposed portion exposed to the outside of the case 53 in the rotating shaft body 60 of the electric motor 50. An appropriate number can be inserted. Further, as the urging member 70, a spring other than the spring washer, for example, a compression coil spring or a torsion spring may be used, or the urging member 70 formed in a suitable shape with a rubbery elastic material may be used. It may be. Furthermore, you may make it obtain mainly the effect by the control part 54a, without using the biasing member 70. FIG.

  As for the electric motor 50, the drive circuit 69 may be disposed inside the case 53 so as not to overlap with the projection of the shaft member 61 in the axial direction, or the drive circuit 69 may be arranged according to the control circuit. It may be disposed outside 53. Further, the electric motor 50 may have a control circuit as an energization circuit together with the drive circuit 69. In this case, the arrangement of the drive circuit 69 and the control circuit conforms to the case of the drive circuit 69 alone described above. It can be. Furthermore, the electric motor 50 may have a restricting portion that restricts the axial displacement of the rotating shaft body 60 by contacting a portion of the rotating shaft body 60 accommodated in the case 53 instead of the restricting portion 54a. In this case, the restriction portion can be formed by the case 53, for example. Furthermore, in the electric motor 50, the effect by the urging member 70 may be mainly obtained without forming the restricting portion 54a. Furthermore, the electric motor 50 may be configured so that, for example, the stator 66 and the case 53 can be rotated without being fixed to the engine. Furthermore, as the radial bearings 51 and 52 of the electric motor 50, roller bearings using rollers as rolling elements may be used.

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 a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the II-II sectional view taken on the line of FIG. It is a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the III-III sectional view taken on the line of FIG. It is a figure which shows the guide member by one Embodiment of this invention, Comprising: It is the IV-IV arrow line view of FIG. 1 is a view showing a valve timing adjusting device according to an embodiment of the present invention, and is a cross-sectional view taken along line VV in FIG. It is a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the VI-VI sectional view taken on the line of FIG. It is the front view (A) which shows the coupling by one Embodiment of this invention, and the VII-VII sectional view taken on the line of (A). It is a figure which shows the valve timing adjustment apparatus by one Embodiment of this invention, Comprising: It is the VIII-VIII sectional view taken on the line of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Valve timing adjustment device, 2 Cam shaft (driven shaft), 10 Motion conversion mechanism (phase change part), 40 Deceleration mechanism (phase change part), 41 Input member, 41a Concentric part, 41b Eccentric part, 41c Guide hole, 50 Electric motor, 51, 52 radial bearing, 51a, 52a outer ring, 51b, 52b inner ring, 51c, 52c ball, 53 case, 54 sleeve, 54a regulating part (regulating means), 54b accommodating part, 55 plate, 55a locking hole part, 55b receiving hole, 55c fixing portion, 56 cover, 57 retainer, 58 connector, 60 rotating shaft, 61 shaft member, 62 rotor member, 63 joint member (exposed portion), 63a flange portion, 63b mounting portion, 63c connecting portion , 66 Stator (electromagnetic part), 67 cores, 68 coils, 69 drive circuit (energization circuit), 70 biasing member

Claims (7)

A valve timing adjusting device that is provided in a transmission system that transmits a driving torque of a drive shaft to a driven shaft that opens and closes at least one of an intake valve and an exhaust valve in an internal combustion engine, and adjusts the opening / closing timing of the at least one valve. There,
A radial bearing, a case for locking the outer ring of the radial bearing, and a rotating shaft body mounted on the inner ring of the radial bearing, and an electric motor for applying a control torque to the rotating shaft body;
A phase changing unit that changes a rotational phase of the driven shaft with respect to the drive shaft using the control torque transmitted from the rotary shaft body;
A biasing member that is interposed between an exposed portion of the rotating shaft body exposed to the outside of the case and the phase change unit, and biases the rotating shaft body in an axial direction;
A valve timing adjusting device comprising: The rotating shaft has a shaft member attached to the inner ring, and a joint member attached to the shaft member so as to constitute the exposed portion,
The phase change unit includes an input member that is attached to the joint member and through which the control torque is transmitted through the joint member;
The valve timing adjusting device according to claim 1, wherein the biasing member is interposed between the joint member and the input member.   3. The electric motor according to claim 1, wherein the electric motor includes an electromagnetic unit that applies the control torque to the rotating shaft body by forming a magnetic field by energization, and an energization circuit that energizes the electromagnetic unit. Valve timing adjustment device. The energization circuit is disposed on the opposite side of the phase change unit across the rotating shaft body,
The valve timing adjusting device according to claim 3, wherein the electric motor has restriction means for restricting axial displacement of the rotary shaft body toward the energization circuit.   5. The valve timing adjusting device according to claim 4, wherein the restricting means is realized by the case that restricts an axial displacement of the rotating shaft body by contacting the exposed portion. The rotating shaft has a shaft member attached to the inner ring, and a joint member attached to the shaft member so as to constitute the exposed portion,
6. The valve timing adjusting device according to claim 5, wherein the phase change unit includes an input member that is attached to the joint member and through which the control torque is transmitted through the joint member.   The valve timing adjusting device according to any one of claims 1 to 6, wherein a clearance is formed between the outer ring and the case on a radially outer side.

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