JP7175821B2 - electric actuator - Google Patents

Description

The present invention relates to an electric actuator.

As an electric actuator capable of changing the rotational phase difference between the input side to which driving force is input from the outside and the output side to output the input driving force, for example, an intake valve and an exhaust valve of an automobile engine. is known to be used in a variable valve timing device that changes the opening/closing timing of one or both of the valves.

As an example, Patent Literature 1 discloses an electric actuator that includes an electric motor and a roller speed reducer that obtains driving force from the electric motor and reduces and transmits rotational force. In this electric actuator, when the roller speed reducer is not driven by the electric motor, the input-side member (e.g., sprocket) and the output-side member (e.g., camshaft) rotate synchronously, and the roller speed reducer is driven by the electric motor. When driven, the roller speed reducer changes the rotation phase difference of the output side member with respect to the input side member, thereby adjusting the opening/closing timing of the valve.

As another example, Patent Document 2 discloses an electric actuator provided with a cycloid speed reducer. The electric actuator includes an electric motor, a cylindrical driving rotating body (input rotating body) and a driven rotating body (output rotating body), a cylindrical eccentric member that rotates integrally with the rotor of the electric motor, and an eccentric member. and a planetary rotating body (internal gear) arranged inside. The cycloid reducer of the electric actuator includes a first external tooth portion formed on the outer peripheral surface of the drive rotor, a second external tooth portion formed on the outer peripheral surface of the driven rotor, and an inner peripheral surface of the planetary rotor. A first internal toothing and a second internal toothing formed and meshing with the first external toothing and the second external toothing.

The inner peripheral surface of the eccentric member located inside the rotor is arranged eccentrically from the rotation axis (central axis) of the drive rotor and the driven rotor. The planetary rotor is rotatably supported with respect to the eccentric member by one needle roller bearing arranged inside the eccentric member. Further, the planetary rotor is arranged on the inner periphery of the eccentric member, so that it is eccentrically arranged from the rotation shafts of the drive rotor and the driven rotor.

As for the operation of the electric actuator configured as described above, in a state where the electric motor is not energized and no driving force is supplied from the electric motor to the speed reducer, when the drive rotor is rotationally driven by an external drive force, the drive rotor rotates. is transmitted to the driven rotor via the planetary rotor, the driven rotor rotates in synchronization with the drive rotor.

On the other hand, when the electric motor is energized and driving force is supplied from the electric motor to the speed reducer, the rotor and the eccentric member rotate integrally, so that the planetary rotor rotates as the drive rotor and the driven rotor. move eccentrically relative to the body. As a result, each time the eccentric member rotates once, the engaging portion between the first inner toothed portion and the first outer toothed portion is displaced in the circumferential direction by one tooth. slow down and rotate.

In addition, the rotational motion of the planetary rotor and the eccentric motion are combined, and in the relationship between the planetary rotor and the driven rotor, each rotation of the eccentric member causes the second inner toothed portion and the second outer toothed portion to rotate. The position of engagement with the tooth portion is displaced in the circumferential direction by one tooth. As a result, the driven rotor rotates at a reduced speed with respect to the planetary rotor.

JP 2014-152766 A JP 2018-194151 A

In the electric actuator disclosed in Patent Document 1, when attempting to achieve a high reduction ratio with a roller speed reducer, the radial dimension or axial dimension of the roller speed reducer becomes large, which leads to an increase in the size of the electric actuator. may invite.

In the electric actuator according to Patent Document 2, since the cycloid speed reducer is supported by the needle roller bearing, an increase in the radial dimension of the electric actuator can be suppressed. However, since it is supported only by one needle roller bearing, it cannot be said that the rigidity of the speed reducer is sufficiently ensured. In this electric actuator, the speed reducer is composed of two stages, the first internal tooth portion and the first external tooth portion, and the second internal tooth portion and the second external tooth portion. Also, when the electric motor is operated, the eccentric motion of the planetary rotor causes the radial load to become uneven, which may lead to a decrease in the efficiency of the electric actuator.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and a technical object thereof is to increase the rigidity of a speed reducer and prevent a decrease in the efficiency of an electric actuator.

An electric actuator according to the present invention is intended to solve the above problems, and includes a drive rotor rotatable about a rotation axis, a planetary rotor rotatable and revolving about the rotation axis, and a driven rotor rotatable about a rotation axis, wherein the planetary rotor meshes with the drive rotor and the driven rotor, respectively, and a first reduction gear is provided between the planetary rotor and the drive rotor; a second reduction gear is formed between the planetary rotor and the driven rotor, and the reduction ratio of the first reduction gear is different from the reduction ratio of the second reduction gear. an electric motor having a rotor that drives the planetary rotor; a first bearing that supports the planetary rotor inside the rotor; and a second bearing for supporting the rotating body, wherein the second bearing is a deep groove ball bearing.

According to this configuration, the planetary rotors constituting the first speed reducer and the second speed reducer are supported by the first bearing and the second bearing, and the second bearing is configured by a deep groove ball bearing. The rigidity of the gear and the second speed reducer can be increased. As a result, it is possible to prevent the occurrence of skew in the planetary rotating body, and in turn prevent a decrease in the efficiency of the electric actuator.

The second bearing can support both the first speed reducer and the second speed reducer. As a result, the rigidity of the first speed reducer and the second speed reducer can be increased, and a decrease in the efficiency of the electric actuator can be effectively prevented.

The differential gear includes an eccentric member that rotates integrally with the rotor and changes a rotational phase difference of the driven rotor with respect to the drive rotor, and the second bearing is fixed to the inner circumference of the eccentric member. and an inner ring fixed to the outer circumference of the planetary rotor.

The first bearing may be a needle roller bearing. Thereby, the dimension in the radial direction of the electric actuator can be made as small as possible.

An electric actuator according to the present invention includes a sprocket provided on the driving rotating body and a camshaft provided on the driven rotating body, and changes a rotational phase difference between the sprocket and the camshaft to change valve opening/closing timing. It can be applied to a variable valve timing device that changes the

ADVANTAGE OF THE INVENTION According to this invention, the rigidity of a reduction gear can be improved and the efficiency fall of an electric actuator can be prevented.

1 is a cross-sectional view of an electric actuator according to the present invention; FIG. 1 is an exploded perspective view of an electric actuator; FIG. 2 is an enlarged cross-sectional view of a main part of an electric actuator; FIG. FIG. 2 is a cross-sectional view taken along line AA of FIG. 1; FIG. 2 is a cross-sectional view taken along line BB of FIG. 1;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments for carrying out the present invention will be described based on the accompanying drawings. In addition, in each drawing for explaining the present invention, constituent elements such as members and constituent parts having the same function or shape are given the same reference numerals as much as possible, and once explained, the explanation will be repeated. omitted.

1 is a longitudinal sectional view of an electric actuator according to this embodiment, FIG. 2 is an exploded perspective view of the electric actuator, and FIG. 3 is an enlarged cross-sectional view of the main part of the electric actuator. The electric actuator according to this embodiment is used, for example, as a variable valve timing device for an engine (driving source), but is not limited to this application.

As shown in FIGS. 1 to 3, the electric actuator 1 includes a drive rotor 2, a driven rotor 3, an electric motor 4, a differential gear 5, and a casing 6 housing them as main components. Prepare as

The drive rotator 2 has a generally cylindrical shape with both ends in the axial direction open, and has a main body 21 and a sprocket 22 that serves as an input portion for driving force from the engine. The main body 21 and the sprocket 22 are coaxially arranged with the rotation axis O as the center. Therefore, the main body 21 and the sprocket 22 are integrally rotated around the rotation axis O by the driving force from the engine.

The main body 21 includes a first tubular portion 21 a provided with the sprocket 22 , a second tubular portion 21 b supported by the casing 6 , and a third tubular portion 21 c functioning as part of the differential gear 5 . The sprocket 22 is provided to the first tubular portion 21a of the main body 21 so as to be capable of transmitting torque, and is rotationally driven by the driving force transmitted from the engine via the chain.

The driven rotor 3 is a member that outputs the driving force transmitted from the drive rotor 2 and has a cylindrical main body 31 and a camshaft 32 . Camshaft 32 includes one or more cams (not shown) and is configured to drive at least one of the intake and exhaust valves of the engine. The main body 31 and the camshaft 32 are arranged coaxially on the rotation axis O and coupled to each other by a center bolt 33 . As a result, the main body 31 and the camshaft 32 rotate about the rotation axis O together.

A bearing 8 is arranged between the outer peripheral surface of the camshaft 32 and the inner peripheral surface of the first cylindrical portion 21 a of the main body 21 related to the drive rotor 2 . A bearing 9 is arranged between the casing 6 and the outer peripheral surface of the second cylindrical portion 21 b of the main body 21 relating to the drive rotor 2 . These bearings 8 and 9 allow relative rotation between the drive rotor 2 and the driven rotor 3 . The bearings 8 and 9 are configured by rolling bearings, but are not limited to this, and can be configured by sliding bearings or other bearings.

For the convenience of assembly, the casing 6 is divided into a bottomed cylindrical casing main body 6a and a lid portion 6b. The casing main body 6a and the lid portion 6b are integrated using fastening means such as bolts. The lid portion 6b has a tubular protrusion for drawing out a power supply line for supplying power to the electric motor 4 and a signal line connected to a rotation speed detection sensor (not shown) for detecting the rotation speed of the electric motor 4. 6c and 6d (see FIG. 2) are provided. A bearing 13 is arranged between the inner peripheral surface of the lid portion 6 b of the casing 6 and the outer peripheral surface of the main body 31 of the driven rotating body 3 .

The electric motor 4 is a radial gap type motor having a stator 41 fixed to the casing body 6a and a rotor 42 arranged radially inward of the stator 41 so as to face each other with a gap. The stator 41 is composed of a stator core 41a made of a plurality of magnetic steel sheets laminated in the axial direction, a bobbin 41b made of an insulating material attached to the stator core 41a, and a stator coil 41c wound around the bobbin 41b. The rotor 42 is composed of an annular rotor core (rotor inner) 42a and a plurality of magnets 42b attached to the rotor core 42a. The electric motor 4 rotates the rotor 42 about the rotation axis O by the excitation force acting between the stator 41 and the rotor 42 .

The differential gear 5 includes a main body 21 of the drive rotor 2, a main body 31 of the driven rotor 3, an eccentric member 51 that rotates integrally with the rotor 42, and planetary rotors 52 arranged on the inner periphery of the eccentric member 51. , and a first bearing 53 and a second bearing 54 arranged between the eccentric member 51 and the planetary rotor 52 as main components.

The eccentric member 51 is generally configured in a cylindrical shape with both ends in the axial direction open, and includes a large-diameter tubular portion 51a, a medium-diameter tubular portion 51b having a diameter smaller than that of the large-diameter tubular portion 51a, and a medium-diameter tubular portion 51b. It integrally has a small-diameter cylindrical portion 51c formed to have a diameter smaller than that of the portion 51b.

The large-diameter tubular portion 51a protrudes axially from the medium-diameter tubular portion 51b so as not to overlap the rotor core 42a. The large-diameter cylindrical portion 51a is rotatably supported by the casing main body 6a of the casing 6 via the bearing 17. As shown in FIG. The medium-diameter cylindrical portion 51b is fixed to the inner circumference of the rotor core 42a so as to overlap the rotor core 42a in the axial direction. The small-diameter tubular portion 51c protrudes axially (opposite to the large-diameter tubular portion 51a) from the medium-diameter tubular portion 51b so as not to overlap the rotor core 42a. The small-diameter cylindrical portion 51c is rotatably supported by the lid portion 6b of the casing 6 via the bearing 18. As shown in FIG.

The outer peripheral surface of the large-diameter tubular portion 51a, the outer peripheral surface of the medium-diameter tubular portion 51b, and the outer peripheral surface of the small-diameter tubular portion 51c are cylindrical surfaces formed coaxially with the rotation axis O. An eccentric inner peripheral surface 51 a 1 on a cylindrical surface eccentric with respect to the rotation axis O is formed on the inner peripheral surface of the large-diameter cylindrical portion 51 a of the eccentric member 51 . In addition, an eccentric inner peripheral surface 51b1 in the shape of a cylindrical surface eccentric with respect to the rotation axis O is formed on the inner peripheral surface of the medium-diameter tubular portion 51b of the eccentric member 51 . The large-diameter tubular portion 51a and the medium-diameter tubular portion 51b of the eccentric member 51 have a thick portion and a thin portion due to the relationship between the outer peripheral surface and the eccentric inner peripheral surfaces 51a1 and 51b1.

The planetary rotor 52 has a cylindrical shape with both axial ends open, and includes a large-diameter tubular portion 52a and a small-diameter tubular portion 52b. A first internal toothed portion 55 is formed on the inner periphery of the large diameter cylindrical portion 52a, and a second internal toothed portion 56 is formed on the inner periphery of the small diameter cylindrical portion 52b. Each of the first inner toothed portion 55 and the second inner toothed portion 56 is composed of a plurality of teeth whose cross section in the radial direction draws a curved line (for example, a trocolloidal curved line). The first inner toothed portion 55 and the second inner toothed portion 56 are formed at axially offset positions. The pitch circle diameter of the second internal tooth portion 56 is smaller than the pitch circle diameter of the first internal tooth portion 55 . Further, the number of teeth of the second inner toothed portion 56 is smaller than the number of teeth of the first inner toothed portion 55 .

An end portion 56a of the second internal tooth portion 56 on the side of the first internal tooth portion 55 in the face width direction is formed so as to overlap the outer peripheral surface of the large-diameter cylindrical portion 52a of the planetary rotor 52 in the axial direction. In other words, a portion (end portion 56a) of the second internal tooth portion 56 is formed so as to overlap the second bearing 54 in the axial direction (face width direction).

A first external toothed portion 57 that meshes with the first internal toothed portion 55 is formed on the outer peripheral surface of the third cylindrical portion 21 c of the main body 21 related to the drive rotor 2 . A second external toothed portion 58 that meshes with the second internal toothed portion 56 is formed on the outer peripheral surface of the main body 31 related to the driven rotating body 3 . Each of the first external tooth portion 57 and the second external tooth portion 58 is formed of a plurality of teeth having a radial cross-section that draws a curve (for example, a trochoidal curve). The pitch circle diameter of the second external tooth portion 58 is smaller than the pitch circle diameter of the first external tooth portion 57 , and the number of teeth of the second external tooth portion 58 is smaller than the number of teeth of the first external tooth portion 57 .

One end portion 58a in the face width direction of the second external tooth portion 58 is arranged so as to overlap the outer peripheral surface of the large-diameter cylindrical portion 52a of the planetary rotor 52 in the axial direction. In other words, a portion (end portion 58a) of the second external tooth portion 58 is formed so as to overlap the second bearing 54 in the axial direction (face width direction).

The number of teeth of the first external toothing 57 is less than the number of teeth of the first internal toothing 55 that mesh with each other, preferably one less. Similarly, the number of teeth of the second external toothing 58 is also less than the number of teeth of the second internal toothing 56 that mesh with each other, preferably one less. As an example, in this embodiment, the number of teeth of the first internal tooth portion 55 is 24, the number of teeth of the second internal tooth portion 56 is 20, the number of teeth of the first external tooth portion 57 is 23, and the number of teeth of the second external tooth portion 57 is 23. The tooth portion 58 has 19 teeth.

The first internal toothed portion 55 and the first external toothed portion 57 that mesh with each other constitute the first speed reducer 5a, and the second internal toothed portion 56 and the second external toothed portion 58 constitute the second speed reducer 5b. Both the first reduction gear 5a and the second reduction gear 5b are called cycloidal reduction gears. The reduction ratios of the two reduction gears 5a and 5b are different, and in this embodiment, the reduction ratio of the first reduction gear 5a is made larger than the reduction ratio of the second reduction gear 5b. By making the reduction ratios of the two reduction gears 5 a and 5 b different in this way, it is possible to change (differentially) the rotation of the camshaft 32 according to the operating state of the electric motor 4 .

The first bearing 53 is arranged between the eccentric inner peripheral surface 51 b 1 of the eccentric member 51 and the outer peripheral surface of the small-diameter cylindrical portion 52 b of the planetary rotor 52 . Therefore, the center (P) of the outer peripheral surface and the inner peripheral surface of the planetary rotor 52 is located eccentrically with respect to the rotation axis O. The planetary rotor 52 is supported by the first bearing 53 so as to be rotatable relative to the eccentric member 51 . The first bearing 53 is, for example, a needle roller bearing having an outer ring 53a and rolling elements 53b (needle rollers). The outer ring 53 a is fixed to the eccentric inner peripheral surface 51 b 1 of the medium-diameter cylindrical portion 51 b of the eccentric member 51 . The rolling element 53b is in contact with the outer peripheral surface (rolling surface) of the small-diameter cylindrical portion 51c of the planetary rotor 52 .

The second bearing 54 is axially displaced from the first bearing 53 so as not to overlap the inner circumference of the rotor core 42 a of the electric motor 4 . Specifically, the second bearing 54 is arranged between the large-diameter tubular portion 52 a of the planetary rotor 52 and the eccentric inner peripheral surface 51 a 1 of the large-diameter tubular portion 51 a related to the eccentric member 51 .

The second bearing 54 is a deep groove ball bearing having an outer ring 54a, an inner ring 54b, and rolling elements 54c (balls). The outer ring 54 a of the second bearing 54 is fixed (press-fitted) to the eccentric inner peripheral surface 51 a 1 of the large-diameter tubular portion 51 a of the eccentric member 51 . The inner ring 54 b of the second bearing 54 is fixed (press-fitted) to the outer peripheral surface of the large-diameter cylindrical portion 52 a of the planetary rotor 52 .

The second bearing 54 is arranged across the reduction gears 5a and 5b so as to support both the first reduction gear 5a and the second reduction gear 5b. That is, the second bearing 54 is formed between the eccentric member 51 and the planetary rotor 52 so as to overlap a part of the first reduction gear 5a in the axial direction and overlap a part of the second reduction gear 5b in the axial direction. placed in between. As shown in FIG. 3, the overlapping distance D1 between the second bearing 54 and the first reduction gear 5a is greater than the overlapping distance D2 between the second bearing 54 and the second reduction gear 5b.

FIG. 4 is a cross-sectional view cut along the first reduction gear 5a (cross-sectional view taken along line AA in FIG. 1), and FIG. arrow view).

As shown in FIG. 4, the center P of the first inner toothed portion 55 is radially eccentric with respect to the rotation axis O by a distance E. As shown in FIG. Therefore, the first inner toothed portion 55 and the first outer toothed portion 57 are meshed with each other in a partial region in the circumferential direction, and are not meshed with each other in a region on the opposite side in the radial direction. In addition, as shown in FIG. 5, the center P of the second inner toothed portion 56 is also eccentric to the rotation axis O by a distance E in the radial direction. , are meshed with each other in some circumferential regions, and are not meshed with each other in a region on the opposite side in the radial direction. 4 and 5, the directions of the arrows are different from each other, so the eccentric directions of the first inner toothed portion 55 and the second inner toothed portion 56 are shown in opposite left and right directions in each figure. However, the first inner toothed portion 55 and the second inner toothed portion 56 are eccentric by the same distance E in the same direction.

Here, if i is the speed reduction ratio of the differential gear 5, nm is the motor rotation speed, and ns is the rotation speed of the sprocket 22, the output rotation phase angle difference is (nm-ns)/i.

Further, when the reduction ratio of the first reduction gear 5a is i1 and the reduction ratio of the second reduction gear 5b is i2, the reduction ratio of the differential gear 5 according to the present embodiment is obtained by the following equation 1.

Reduction ratio=i1×i2/|i1-i2| Expression 1

For example, when the reduction ratio (i1) of the first reduction gear 5a is 24/23 and the reduction ratio (i2) of the second reduction gear 5b is 20/19, the reduction ratio is 120 from the above equation (1). Thus, in the differential gear 5 according to the present embodiment, it is possible to obtain high torque with a large reduction ratio.

In the electric actuator 1 of the present embodiment, since the drive rotor 2 and the driven rotor 3 are arranged on the inner diameter side of the planetary rotor 52, a hollow motor is adopted as the electric motor 4 for driving the planetary rotor 52. A layout is adopted in which this hollow motor is arranged on the outer diameter side of the planetary rotor 52 . Therefore, the space efficiency is improved, and there is an advantage that the electric actuator 1 can be made compact (especially, the size in the axial direction can be made compact).

Further, in the electric actuator 1 of the present embodiment, since the needle roller bearing is adopted as the first bearing 53 on the inner diameter side of the rotor 42, the radial dimension of the electric actuator 1 can be made as small as possible. In addition, since the deep-groove ball bearing as the second bearing 54 is arranged at a position shifted in the axial direction so as not to overlap the rotor core 42a, the first reduction gear 5a and By increasing the rigidity of the second speed reducer 5b as much as possible and suppressing the skew occurring in the planetary rotor 52, it is possible to prevent the efficiency of the electric actuator 1 from decreasing.

Next, operation of the electric actuator according to the present embodiment will be described with reference to FIGS. 1 to 5. FIG.

During operation of the engine, the drive rotor 2 is rotated by the driving force from the engine transmitted to the sprocket 22 .

When the electric motor 4 is not energized and there is no input from the electric motor 4 to the differential gear 5, the rotation of the driving rotor 2 is transmitted to the driven rotor 3 via the planetary rotor 52, causing the driven rotor 3 to rotate. rotates integrally with the drive rotor 2 . That is, the driving rotor 2 and the planetary rotor 52 rotate integrally while maintaining this meshing state due to torque transmission at the meshing portion between the first internal toothed portion 55 and the first external toothed portion 57 . Similarly, the planetary rotating body 52 and the driven rotating body 3 also rotate integrally while maintaining the meshing positions of the second internal toothed portion 56 and the second external toothed portion 58 . Therefore, the drive rotor 2 and the driven rotor 3 rotate while maintaining the same rotational phase.

After that, for example, when the engine shifts to a low speed range such as idling, the electric motor 4 is energized by known means such as electronic control, and the rotor 42 is rotated relatively slower than the sprocket 22. Or rotate faster. When the electric motor 4 is operated, the eccentric member 51 coupled to the rotor core 42a of the rotor 42 rotates about the rotation axis O together. Along with this, the pressing force due to the rotation of the eccentric member 51 having the thin-walled portion and the thick-walled portion acts on the planetary rotor 52 via the first bearing 53 . Due to this pressing force, a component of force in the circumferential direction is generated at the meshing portion between the first inner toothed portion 55 and the first outer toothed portion 57 , so that the planetary rotor 52 makes an eccentric rotational motion relative to the drive rotor 2 . I do. That is, the planetary rotor 52 revolves around the rotation axis O and rotates around the center P of the first inner toothed portion 55 and the second inner toothed portion 56 . At this time, every time the planetary rotor 52 revolves once, the engagement position between the first inner toothed portion 55 and the first outer toothed portion 57 shifts in the circumferential direction by one tooth, so the planetary rotor 52 is decelerated. It rotates (rotates).

Further, since the planetary rotor 52 performs the above-described eccentric rotational motion, the engagement portion between the second internal tooth portion 56 and the second external tooth portion 58 is increased by one tooth for each revolution of the planetary rotor 52. It shifts in the circumferential direction. As a result, the driven rotor 3 rotates while being decelerated with respect to the planetary rotor 52 . By driving the planetary rotor 52 with the electric motor 4 in this manner, the driving force from the electric motor 4 is superimposed on the driving force from the sprocket 22 , and the rotation of the driven rotor 3 is the same as the driving force from the electric motor 4 . It becomes a differential state under the influence of force. Therefore, it is possible to change the relative rotational phase difference of the driven rotor 3 with respect to the drive rotor 2 in forward and reverse directions, and change the opening/closing timing of the valve by the cam of the camshaft 32 in the advance direction or in the retard direction. can do.

By changing the opening/closing timing of the valve in this way, it is possible to stabilize the rotation of the engine during idling and improve fuel efficiency. Further, when the operation of the engine shifts from the idling state to normal operation, for example, when it shifts to high-speed rotation, by increasing the speed difference of the relative rotation of the electric motor 4 with respect to the sprocket 22, the camshaft 32 with respect to the sprocket 22 can be changed to a rotation phase difference suitable for high rotation, and it is possible to increase the output of the engine.

In addition, the present invention is not limited to the configuration of the above-described embodiment, nor is it limited to the above-described effects. Various modifications can be made to the present invention without departing from the gist of the present invention.

In the above-described embodiment, the first bearing 53 is illustrated as a needle roller bearing, but is not limited to this and may be configured by a bearing such as a deep groove ball bearing.

Reference Signs List 1 electric actuator 2 drive rotor 3 driven rotor 4 electric motor 5 differential gear 5a first reduction gear 5b second reduction gear 22 sprocket 32 camshaft 42 rotor 51 eccentric member 52 planetary rotor 53 first bearing 54 second bearing 54a Outer ring 54b of second bearing Inner ring of second bearing O Rotating shaft

Claims (5)

A driving rotor rotatable about a rotation axis, a planetary rotor rotatable about the rotation axis, and a driven rotor rotatable about the rotation axis, wherein the planetary rotor meshes with the drive rotor and the driven rotor, forming a first speed reducer between the planetary rotor and the drive rotor, and a second speed reducer between the planetary rotor and the driven rotor. a differential device forming two reduction gears, wherein the reduction ratio of the first reduction gear is different from the reduction ratio of the second reduction gear;
an electric motor having a rotor that drives the planetary rotor;
A first bearing that supports the planetary rotor inside the rotor, and a second bearing that supports the planetary rotor at a position axially displaced so as not to overlap the rotor,
The electric actuator, wherein the second bearing is a deep groove ball bearing. The electric actuator according to claim 1, wherein the second bearing supports both the first reduction gear and the second reduction gear. The differential gear includes an eccentric member that rotates integrally with the rotor and changes a rotational phase difference of the driven rotor with respect to the drive rotor,
3. The electric actuator according to claim 1, wherein the second bearing comprises an outer ring fixed to the inner periphery of the eccentric member and an inner ring fixed to the outer periphery of the planetary rotor. The electric actuator according to any one of claims 1 to 3, wherein the first bearing is a needle roller bearing. A sprocket provided on the drive rotor and a camshaft provided on the driven rotor,
The electric actuator according to any one of claims 1 to 4, wherein the electric actuator is applied to a variable valve timing device that changes the opening/closing timing of a valve by changing the rotation phase difference between the sprocket and the camshaft.

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