JP2020112177A - Actuator - Google Patents

Abstract

To hardly cause a bearing to be pulled out of a gear.SOLUTION: An actuator 10 includes a motor 36, an output shaft 26, and a slowdown part 37 for slowing down the rotation of the motor and transmitting it to the output shaft, the slowdown part having a resin-formed intermediate gear 53 provided between a rotary shaft 55 of the motor and the output shaft and integrally having a large-diameter gear 62 and a small-diameter gear 63, an intermediate shaft 61 to be the rotation center of the intermediate gear, a rolling bearing 90 for holding the large-diameter gear rotatably relative to the intermediate shaft at the large-diameter gear side of the intermediate gear, a resin bearing 95 for holding the small-diameter gear rotatably relative to the intermediate shaft at the small-diameter gear side of the intermediate gear, and a collar 80 arranged between an outer ring 90o of the rolling bearing and the large-diameter gear and molded integrally with resin, the collar including a cylindrical part 80a to which an outer ring is fitted, and a protruded part 80b protruded outward from the cylindrical part.SELECTED DRAWING: Figure 7

Description

The present disclosure relates to actuators.

Patent Document 1 discloses an actuator used to drive a valve for supercharging pressure control of a turbocharger. The actuator decelerates the rotation of the motor with a speed reducer to rotate the output shaft with a desired torque. The rotation angle of the output shaft is detected by a non-contact rotation angle sensor having a magnetic circuit section and a detection section. The final gear of the speed reducer is a resin member integrally fixed to the output shaft, and the magnetic circuit section is molded in the final gear. Patent Document 2 discloses an actuator used for an intake valve device. The actuator of this intake valve device includes a rolling bearing between the gear and the shaft or between the shaft and the housing.

JP, 2017-8757, A JP2012-197885A

The actuator that drives the boost pressure control valve is stressed by the engine pulsation through the boost pressure control valve. Since a high-cycle impact load associated with the pulsating cycle is applied to the output shaft, wear resistance and strength of the speed reducer are required. Therefore, for example, when it is mounted on an engine with large exhaust pulsation or a supercharger with large waste gate port diameter, it is necessary to improve wear resistance and strength. Further, when the bearing structure of Patent Document 2 is applied to the actuator of Patent Document 1, when a high-cycle impact load due to the pulsating cycle is applied, the bearing may come off in the thrust direction, that is, the direction along the shaft. there were. Such a problem was a problem common to many other actuators.

According to one aspect of the present disclosure, an actuator (10) that drives a valve (19) that controls exhaust gas generated by combustion of an internal combustion engine (11) is provided. The actuator includes a motor (36), an output shaft (26), and a reduction unit (37) that reduces the rotation of the motor and transmits the rotation to the output shaft, the reduction unit rotating the motor. An intermediate gear (53) provided between the shaft (55) and the output shaft, the intermediate gear (53) made of resin integrally including a large diameter gear (62) and a small diameter gear (63); An intermediate shaft (61) serving as a rotation center, a rolling bearing (90) for rotatably holding the large diameter gear with respect to the intermediate shaft on the large diameter gear side of the intermediate gear, and the intermediate gear Between the resin bearing (95) that rotatably holds the small-diameter gear with respect to the intermediate shuff, and the outer ring (90o) of the rolling bearing and the large-diameter gear on the small-diameter gear side. A collar (80) that is disposed and integrally molded with the resin, the collar including a cylindrical portion (80a) into which the foreign trade fits, and a protrusion () protruding outward from the cylindrical portion. 80b). According to this aspect, since the collar includes the protruding portion that projects outward from the cylindrical portion, even when the intermediate gear receives a large thrust load, the collar is difficult to come off from the resin forming the intermediate gear, The rolling bearing is also hard to come off from the resin that forms the intermediate gear.

It is a schematic diagram of an intake and exhaust part of an engine to which the actuator of the first embodiment is applied. It is explanatory drawing of a supercharger. It is a top view of an actuator. It is explanatory drawing which shows each gear of a reduction part. It is the VV sectional view taken on the line of FIG. It is the VI-VI sectional view taken on the line of FIG. It is explanatory drawing which shows the state which attached the 2nd intermediate gear of 1st Embodiment to the housing typically. It is a perspective view of a color. It is explanatory drawing which shows typically the state which attached the 2nd intermediate gear of 2nd Embodiment to the housing. It is a top view of the 2nd intermediate gear of a 2nd embodiment. It is explanatory drawing which shows the state which attached the 2nd intermediate gear of 3rd Embodiment to the housing typically. It is explanatory drawing which shows the state which attached the 2nd intermediate gear of 4th Embodiment to the housing typically. It is explanatory drawing which shows typically the state which attached the 2nd intermediate gear of 5th Embodiment to the housing. It is explanatory drawing which shows typically the state which attached the 2nd intermediate gear of 6th Embodiment to the housing. It is explanatory drawing which shows the state which attached the 2nd intermediate gear of 7th Embodiment to the housing typically. It is explanatory drawing which shows typically the state which attached the 2nd intermediate gear of 8th Embodiment to the housing. It is explanatory drawing which shows typically the state which attached the 2nd intermediate gear of 9th Embodiment to the housing.

First embodiment:
As shown in FIG. 1, the actuator 10 according to the first embodiment is applied to an engine 11 which is a power source for driving a vehicle.

The engine 11 is provided with an intake passage 12 that guides intake air into a cylinder of the engine 11, and an exhaust passage 13 that exhausts exhaust gas generated in the cylinder into the atmosphere. A compressor wheel 14 a of the intake compressor 14 of the supercharger 24 and a throttle valve 15 are provided in the intake passage 12. The compressor wheel 14a supercharges intake air to the engine 11. The throttle valve 15 adjusts the amount of intake air supplied to the engine 11 according to the amount of depression of an accelerator pedal (not shown) of the vehicle.

A turbine wheel 16 a of the exhaust turbine 16 of the supercharger 24 and a catalyst 17 for purifying exhaust gas are provided in the middle of the exhaust passage 13. The turbine wheel 16a is connected to the compressor wheel 14a by a rotating shaft 30. That is, the turbine wheel 16a is rotated by the exhaust energy of the engine 11, and the compressor wheel 14a is rotated. The catalyst 17 is a well-known three-way catalyst adopting a monolith structure, and is heated to an activation temperature by exhaust gas to purify harmful substances contained in the exhaust gas by an oxidizing action and a reducing action.

A bypass passage 18 is provided in the exhaust passage 13 in parallel with the turbine wheel 16a to bypass the turbine wheel 16a and allow the exhaust gas to flow. The bypass passage 18 is provided with a waste gate valve 19 which is a supercharging pressure control valve. When the wastegate valve 19 opens, a part of the exhaust gas from the engine 11 is directly guided to the catalyst 17 through the bypass passage 18. The wastegate valve 19 opens when the pressure of the exhaust gas from the engine 11 exceeds the valve opening pressure of the wastegate valve 19. The opening/closing of the waste gate valve 19 is also controlled by an ECU (engine control unit) 22. That is, the ECU 22 drives the actuator 10 and opens and closes the waste gate valve 19 by the link mechanism 25 provided between the actuator 10 and the waste gate valve 19.

As shown in FIG. 2, the supercharger 24 includes an exhaust turbine 16, an intake compressor 14, and an actuator 10. The exhaust turbine 16 includes a turbine wheel 16a (FIG. 1) that is rotationally driven by the exhaust gas discharged from the engine 11, and a spiral turbine housing 16b that houses the turbine wheel 16a. The intake compressor 14 includes a compressor wheel 14a (FIG. 1) that rotates by receiving the rotational force of the turbine wheel 16a, and a spiral compressor housing 14b that houses the compressor wheel 14a. The turbine wheel 16a and the compressor wheel 14a are connected by the rotating shaft 30 (FIG. 1).

The turbine housing 16b is provided with a bypass passage 18 in addition to the turbine wheel 16a. The bypass passage 18 directly guides the exhaust gas flowing into the turbine housing 16b to the exhaust outlet of the turbine housing 16b without supplying it to the turbine wheel 16a. This bypass passage 18 is opened and closed by a waste gate valve 19. The wastegate valve 19 is a swing valve that is rotatably supported by a valve shaft 20 inside the turbine housing 16b. The wastegate valve 19 opens when the exhaust gas pressure exceeds the valve opening pressure of the wastegate valve 19, but is also driven by the actuator 10 to open and close.

The housing 35 that houses the actuator 10 is attached to the intake compressor 14 side of the supercharger 24, which is separated from the exhaust turbine 16. By doing so, the influence of the heat of the exhaust gas can be avoided. The supercharger 24 is provided with a link mechanism 25 (FIG. 1) for transmitting the output of the actuator 10 to the wastegate valve 19. In the present embodiment, as the link mechanism 25, a four-joint link mechanism including an actuator lever 27, a rod 28, and a valve lever 29 is adopted. The actuator lever 27 is connected to the output shaft 26 of the actuator 10 and is rotated by the actuator 10. The valve lever 29 is connected to the valve shaft 20. The rod 28 transmits the turning torque applied to the actuator lever 27 to the valve lever 29.

The operation of the actuator 10 is controlled by the ECU 22 equipped with a microcomputer. Specifically, the ECU 22 controls the actuator 10 so as to adjust the opening degree of the waste gate valve 19 when the engine 11 is rotating at high speed, and controls the supercharging pressure by the supercharger 24. Further, the ECU 22 warms up the catalyst 17 by controlling the actuator 10 so that the waste gate valve 19 is fully opened when the temperature of the catalyst 17 has not reached the activation temperature immediately after a cold start, for example. As a result, the high-temperature exhaust gas that has not been deprived of heat by the turbine wheel 16a can be directly guided to the catalyst 17, and the catalyst 17 can be warmed up in a short time.

Next, the actuator 10 will be described with reference to FIGS. The actuator 10 is housed in a housing 35 attached to the intake compressor 14. As shown in FIG. 3, the housing 35 has a first housing part 41 and a second housing part 42. The second housing part 42 is also referred to as a “case 42”. The first housing part 41 and the second housing part 42 are formed of a metal material such as aluminum, aluminum alloy, or steel. The first housing part 41 and the second housing part 42 may be made of resin. Further, the first housing part 41 and the second housing part 42 may be formed by any of the manufacturing methods such as die casting, gravity casting, injection molding and pressing. The second housing part 42 is fastened to the first housing part 41 by a fastening member 43. The output shaft 26 projects from the second housing portion 42 and is connected to the actuator lever 27.

As shown in FIGS. 4 and 5, the first housing part 41 forms a housing space 44 together with the second housing part 42. The motor 36 is housed in the housing space 44. Specifically, the motor 36 is inserted into a motor insertion hole 46 formed in the first housing portion 41, and is fixed to the first housing portion 41 by a screw 47. A wave washer 45 is installed between the motor 36 and the bottom surface of the motor insertion hole 46. The wave washer 45 may not be provided. The motor 36 may be, for example, a known DC motor, a known stepping motor, or the like regardless of the type.

As shown in FIGS. 4 and 6, the actuator 10 has a speed reducer 37. The speed reducer 37 is a parallel shaft type speed reducer that reduces the rotation of the motor 36 and transmits it to the output shaft 26, and has a plurality of gears. In the present embodiment, the plurality of gears includes a pinion gear 51, a first intermediate gear 52, a second intermediate gear 53, and an output gear 54.

The pinion gear 51 is fixed to the motor shaft 55 of the motor 36. The pinion gear 51 is a metal gear made of metal. As the metal, for example, iron-based sintered metal is used.

The first intermediate gear 52 is a compound gear having a first large diameter outer tooth portion 57 and a first small diameter outer tooth portion 58, and is rotatably supported by the first metal shaft 56. The first large-diameter outer tooth portion 57 is a large-diameter gear, and meshes with the pinion gear 51 fixed to the motor shaft 55 of the motor 36. The first small-diameter outer tooth portion 58 is a gear having a smaller diameter than the first large-diameter outer tooth portion 57. The first large-diameter outer tooth portion 57 and the first small-diameter outer tooth portion 58 are resin gears integrally formed of resin. The first large diameter outer tooth portion 57 may have a plurality of openings in order to reduce the inertia.

The second intermediate gear 53 is a compound gear having a second large diameter outer tooth portion 62 and a second small diameter outer tooth portion 63, and is rotatably supported by the second metal shaft 61. The second large-diameter outer tooth portion 62 is a large-diameter gear and meshes with the first small-diameter outer tooth portion 58 of the first intermediate gear 52. The second small-diameter outer tooth portion 63 is a gear having a smaller diameter than the second large-diameter outer tooth portion 62. The second large-diameter outer tooth portion 62 and the second small-diameter outer tooth portion 63 are resin gears integrally formed of resin. Although the first intermediate gear 52 and the second intermediate gear 53 are resin gears, either one may be a metal gear or a composite gear of a resin gear and a metal gear. The resin gear has smaller inertia than the metal gear. Therefore, when a large impact load is applied to the second intermediate gear 53 via the waste gate valve 19, the valve lever 29, the rod 28, the actuator lever 27, the output shaft 26, and the output gear 54 from the pulsation of the exhaust pressure of the engine 11, The impact can be less likely to be transmitted to gears on the upstream side (motor side) including the second intermediate gear 53, for example, the first intermediate gear 52 and the pinion gear 51. Furthermore, since the output gear 54 is a resin gear, when a large impact load is applied to the output gear 54, gears on the upstream side (motor side) including the output gear, for example, the second intermediate gear 53 and the first intermediate gear 52. The impact can be made less likely to be transmitted to the pinion gear 51. That is, when the first intermediate gear 52 and the second intermediate gear 53 are resin gears, there is an effect of reducing the transmission of impact due to the reduction in inertia as described above.

The output gear 54 meshes with the second small-diameter outer tooth portion 63, and the output shaft 26 is connected and fixed along the central axis AX3 of the output gear 54. The output gear 54 is a resin gear made of resin. Therefore, in the first embodiment, the upstream pinion gear 51 to the first small-diameter outer tooth portion 58 are metal gears, and the downstream second large-diameter outer tooth portion 62 to the output gear 54 are resin gears. .. That is, in the gear included in the reduction unit 37, the pinion gear 51 and the first intermediate gear 52 are metal gears, and the second intermediate gear 53 and the output gear 54 are resin gears.

The output gear 54 is provided with magnets 66 and 67 that are magnetic flux generating portions and yokes 68 and 69 that are magnetic flux transmitting portions. The magnets 66 and 67 and the yokes 68 and 69 form a magnetic circuit portion 64 that forms an arc-shaped closed magnetic circuit when viewed in the axial direction of the output shaft 26. The magnetic circuit portion 64 rotates integrally with the output gear 54 and the output shaft 26.

Inside the closed magnetic circuit of the magnetic circuit section 64 of the output gear 54, a magnetic flux detecting section 65 that detects the magnetic flux of the magnets 66 and 67 is arranged. The magnetic flux detection unit 65 is configured using, for example, a Hall IC. The magnetic circuit unit 64 and the magnetic flux detection unit 65 function as a rotation angle sensor 39 that detects the rotation angle of the output shaft 26. Basic applications and functions of the magnetic circuit unit 64 and the magnetic flux detection unit 65 are the same as those disclosed in JP-A-2014-126548. The rotation angle of the output shaft 26 detected by the rotation angle sensor 39 is output to the ECU 22 (see FIG. 1). The configurations of the magnetic circuit unit 64 and the magnetic flux detection unit 65 shown in FIG. 6 are examples, and other configurations may be used.

As shown in FIG. 6, the output shaft 26 is rotatably supported by a bearing 48 provided in the first housing portion 41 and a bearing 49 provided in the second housing portion 42. One end of the output shaft 26 extends out from the second housing portion 42 of the housing 35. The actuator lever 27 is fixed to the output shaft 26 outside the second housing portion 42.

FIG. 7 is an explanatory diagram schematically showing a state in which the second intermediate gear 53 is attached to the housings 41 and 42. The second large diameter outer tooth portion 62 of the second intermediate gear 53 has teeth 62t, and the second small diameter outer tooth portion 63 has teeth 63t. In this embodiment, the actuator 10 is used as an exhaust actuator. In that case, since the exhaust force may be larger than the intake force, strength and wear resistance are more required between the gear such as the second intermediate gear 53 and the shaft AX2. Therefore, in this embodiment, the collar 80 and the bearing 90 are provided. Specifically, the collar 80 and the rolling bearing 90 are provided on the shaft hole 53h side of the end portion of the second intermediate gear 53 on the second large diameter outer tooth portion 62 side. Specifically, the rolling bearing 90 is provided between the second metal shaft 61 and the second large-diameter outer tooth portion 62. The rolling bearing 90 is a ball bearing including an inner ring 90i, an outer ring 90o, and a bearing ball 90b. A collar 80 is provided between the outer ring 90o of the rolling bearing 90 and the second large diameter outer tooth portion 62. The outer ring 90o of the rolling bearing 90 contacts the collar 80, but the inner ring 90i of the rolling bearing 90 is separated from the resin forming the collar 80 and the second intermediate gear 53.

The collar 80 is a member made of metal such as stainless steel or cold rolled steel, and includes a cylindrical portion 80a, a protrusion 80b, and a brim 80c. The protruding portion 80b projects from the cylindrical surface of the cylindrical portion 80a to the side opposite to the second metal shaft 61, that is, outward, and is embedded in the resin forming the second intermediate gear 53. In the example shown in the drawing, the protrusion 80b projects from the end of the cylindrical portion 80a on the side of the second small-diameter outer tooth portion 63, but at a position other than the end of the cylindrical portion 80a on the side of the second small-diameter outer tooth portion 63. It may be projected from. It is preferable that the protruding portion 80b is embedded by being sandwiched by the resin forming the second intermediate gear 53 from the direction along the axis AX2. Such a configuration can be realized, for example, by integrally molding the collar 80 and the second intermediate gear 53 by insert molding when forming the second intermediate gear 53.

The brim 80c projects toward the second metal shaft 61 from the cylindrical surface of the cylindrical portion 80a. In the example shown in the drawing, the protrusion 80b projects from the end of the cylindrical portion 80a on the side of the second small-diameter outer tooth portion 63, but at a position other than the end of the cylindrical portion 80a on the side of the second small-diameter outer tooth portion 63. It may be projected from. In this case, the length from the end of the cylindrical portion 80a to the collar 80c is preferably equal to or larger than the width of the outer ring 90o of the rolling bearing 90. This is because the outer ring 90o of the rolling bearing 90 does not protrude from the collar 80. However, the length from the end of the cylindrical portion 80a to the collar 80c does not have to be equal to or larger than the width of the outer ring 90o of the rolling bearing 90.

The diameter of the shaft hole 53h at the end portion of the second intermediate gear 53 on the side of the first housing 41 is smaller than the diameter of the shaft hole 53h at portions other than the end portion. A resin bearing 95 is formed between the two metal shafts 61.

FIG. 8 is an explanatory diagram showing an example of the shape of the collar 80. In the example shown in FIG. 8, the collar 80 includes a cylindrical portion 80, a protrusion 80b, and a brim 80c. The protrusion 80b has an outer flange shape, and the brim 80c has an inner flange shape. The protrusion 80b may have a shape other than the outer flange shape, for example, a shape such as a rectangle, a triangle, a semicircle, or a bar. Similarly, the brim 80c may have a shape other than the inner flange shape, for example, a shape such as a rectangle, a triangle, a semicircle, or a bar.

As described above, according to the first embodiment, the protrusion 80b is provided, and the protrusion 80b is sandwiched by the resin from the direction along the axis AX2. Therefore, even when a large thrust load is applied, the collar 80 Can be prevented from coming off from the resin forming the second intermediate gear 53. That is, the protrusion 80 b has a function of preventing the collar 80 from coming off from the resin forming the second intermediate gear 53.

According to the first embodiment, since the second intermediate gear 53 includes the rolling bearing 90, it is possible to counter the load even if the load due to the exhaust force increases. Also, the resistance is low. That is, it is possible to improve the load resistance and reduce the rolling resistance at the same time. Further, since the rolling bearing 90 has a smaller amount of wear than the slide bearing, it is possible to suppress the change (deterioration) of the inter-axis distance and increase the accuracy of the inner diameter of the second intermediate gear 53. Further, it is possible to suppress the fluctuation of the input stress due to the rattling in the radial direction. Further, by suppressing the rattling in the radial direction, the variation between the axes of the second intermediate gear 53 can be reduced. As a result, the movement of the second intermediate gear 53 when receiving an input load is reduced, and the misalignment between the large teeth 62t and the small teeth 63t of the second intermediate gear 53 and the teeth of other gears is reduced. It is possible to reduce the change in meshing ratio. Moreover, sliding of the tooth surface can be reduced.

According to the first embodiment, when the rolling bearing 90 and the collar 80 are provided on the second large-diameter outer tooth portion 62 side, the radial resin thickness can be secured and a larger-diameter rolling bearing can be used. ..

According to the first embodiment, the outer ring 90o of the rolling bearing 90 contacts the collar 80, but the inner ring 90i of the rolling bearing 90 is separated from the collar 80 or the resin forming the second intermediate gear 53. As a result, the rolling bearing 90 can be press-fitted to a position where it does not protrude from the collar 80, so that the size of the second intermediate gear 53 can be reduced.

According to the first embodiment, the resin bearing 95 is in contact with the second metal shaft 61 only at the end opposite to the rolling bearing 90 and is separated from the collar 80. Therefore, the rolling bearing 90 and the resin bearing 95 are separated. Since it is possible to widen the distance between the second intermediate gear 53 and the second metal shaft 61, it is possible to prevent the second intermediate gear 53 from tilting.

In the first embodiment, the rolling bearing 90 may be press-fitted between the collar 80 and the second metal shaft 61 for both the inner ring 90i and the outer ring 90o. Further, the inner ring 90i may have an inner diameter larger than the diameter of the second metal shaft 61, and only the outer ring 90o may be press-fitted.

According to the first embodiment, since the brim 80c is provided, the rolling bearing 90 does not come into contact with the resin of the second intermediate gear 53, and the rolling bearing 90 can be prevented from coming off easily. Further, when the rolling bearing 90 is press-fitted, the brim 80c can be used as a stopper. Further, by supporting the brim 80c from the second small-diameter outer tooth portion 63 side during resin molding of the second intermediate gear 53, the position of the gate, which is the filling port of the resin into the molding die, is set to the second large-diameter outer tooth portion 62 side. That is, it can be installed on the rolling bearing 90 side, and the molding accuracy can be improved. The brim 80c may be omitted.

-Second embodiment:
The second intermediate gear 53 of the second embodiment shown in FIG. 9 is different in that the protrusion 80b of the collar 80 protrudes outward from the tip circle of the tooth 63t of the second small-diameter outer tooth 63, but The configuration of is the same as that of the first embodiment.

In the second embodiment, when the rolling bearing 90 is press-fitted into the second intermediate gear 53, the protrusion 80b can be supported by resin, for example, by the support base 100 shown in FIG. As compared with the case where 80b does not project to the outer side of the tip circle of the tooth 63t of the second small-diameter outer tooth part 63, problems such as deformation and damage of the second large-diameter outer tooth part 62 are less likely to occur. The support base 100 shown in FIG. 9 is shown for convenience of description, and is not included in the actuator 10. Further, in FIG. 9, the illustration of the second flange portion 42 is omitted. The protrusion 80b of the collar 80 does not have to project outside the tip circle of the tooth 63t of the second small-diameter outer tooth 63.

-Third embodiment:
In the second intermediate gear 53 of the third embodiment shown in FIGS. 10 and 11, the protrusion 80b of the collar 80 can be visually recognized on the end surface of the second large diameter outer tooth portion 62 on the second small diameter outer tooth portion 63 side. It has a hole 53h2. Other configurations are similar to those of the intermediate gear 53 of the first embodiment.

In the third embodiment, when the rolling bearing 90 is press-fitted into the second intermediate gear 53, the pin 101 inserted into the hole 53h2 can directly support the protrusion 80b, so that the second large-diameter outer tooth portion 62 and Problems such as deformation and damage of other parts other than the collar are unlikely to occur. The pin 101 shown in FIG. 11 is shown for convenience of description, and is not included in the actuator 10. The second intermediate gear 53 may not have the hole 53h2.

In the example shown in FIGS. 10 and 11, the hole 53h2 is formed closer to the axis AX2 side than the tip circle of the second small-diameter outer tooth part 63, but as in the second embodiment, the protrusion 80b is formed in the second part. When the outer diameter side is larger than the tip circle of the small-diameter outer tooth portion 63, it may be formed on the outer edge side of the tip circle of the second small-diameter outer tooth portion 63. That is, it suffices if the protrusion 80b of the collar 80 can be visually recognized through the hole 53h2.

-Fourth embodiment:
The second intermediate gear 53 of the fourth embodiment shown in FIG. 12 differs from the second intermediate gear 53 of the first embodiment in the shape of the collar 81. The collar 81 of the second intermediate gear 53 of the fourth embodiment includes a cylindrical first collar portion 81a, a disk portion 81c, and a cylindrical second collar portion 81d. The first collar portion 81a and the disc portion 81c have substantially the same shapes as the cylindrical portion 80a and the brim 80c of the first embodiment, respectively. The second collar portion 81d is located inside the disk portion 81c and is opposite to the first collar portion 81a along the shaft hole 53h, that is, the cylindrical first collar portion 81a and the second collar portion 81d are stepped collars. Is formed. The second collar portion 81d projects away from the contact portion between the first collar portion 81a and the outer ring 90o when viewed from the first collar portion 81a.

According to the fourth embodiment, since the first collar portion 81a and the second collar portion 81d form a long stepped collar along the axis AX2, the second large diameter outer tooth portion 62 and the second small diameter outer portion are formed. The rigidity between the tooth portion 63 and the tooth portion 63 can be increased, and the strength against the force that tries to bend the second large diameter outer tooth portion 63 with respect to the second small diameter outer tooth portion 63 can be increased. Further, since the load can be supported by the second collar portion 81d, it is not necessary to cover the first collar portion 81a with a resin, and a gate for resin filling can be arranged on the second collar portion 81d side during resin molding. The resin can be easily flowed over time.

According to the fourth embodiment, since both the first collar portion 81a and the second collar portion 81d are in contact with the resin, the frictional force can be increased. As a result, it is difficult for the collar 81 to come off even when a large thrust load is applied. That is, the second collar portion 81d has a function as a protruding portion that suppresses separation of the collar 81 from the resin.

According to the fourth embodiment, as with the first embodiment, the rolling bearing 90 is provided, so that the load can be counteracted even if the load due to the exhaust force increases. Further, since the rolling bearing 90 has a smaller amount of wear than the sliding bearing, the accuracy of the inner diameter of the second intermediate gear 53 can be maintained. Further, it is possible to suppress the fluctuation of the input stress due to the rattling in the radial direction.

According to the fourth embodiment, like the first embodiment, since the disk portion 81c is provided, the rolling bearing 90 does not come into contact with the resin of the second intermediate gear 53, and the rolling bearing 90 can be prevented from coming off easily. Further, when the rolling bearing 90 is press-fitted, the disc portion 81c can be used as a stopper. Further, by supporting the disk portion 81c from the second small-diameter outer tooth portion 63 side during resin molding of the second intermediate gear 53, the position of the gate, which is the filling port of the resin into the molding die, is set to the second large-diameter outer tooth portion 62. It can be installed on the side, that is, on the rolling bearing 90 side, and the molding accuracy can be improved.

-Fifth embodiment:
The collar 82 of the second intermediate gear 53 of the fifth embodiment shown in FIG. 13 has a first collar portion 82a, a disc portion 82c, and a second collar portion 82d, similar to the collar 81 similar to the fourth embodiment. Equipped with. The first collar portions 81a and 82a have the same shape, and the disk portions 81c and 82c have the same shape, but the second collar portions 81d and 82d have different shapes. That is, the second collar portion 81d of the fourth embodiment has a cylindrical shape whose thickness is substantially constant depending on the position, but the second collar portion 82d of the fifth embodiment has a second small diameter outer tooth that is a small diameter gear. The thickness wt on the end side which is the end on the side of the portion 63 is thicker than the thickness wb on the side of the disk portion 82c which is the side of the second large-diameter outer tooth portion 62 which is a large-diameter gear, and vice versa. It has a tapered outer shape.

According to the fifth embodiment, in addition to the effect obtained in the fourth embodiment, the second collar portion 82d has an inverse taper shape, and thus, when a large load is applied during manufacturing and use, further The collar 82 is hard to come off.

The collars 81 and 82 in the fourth and fifth embodiments may have the same configuration as the protrusion 80b in the first and second embodiments. Further, it is possible to make it difficult for the collars 81 and 82 to come off.

-Sixth embodiment:
In the first embodiment shown in FIG. 7, the diameter of the shaft hole 53h at the end portion of the second intermediate gear 53 on the side of the first housing 41 is formed smaller than the diameter of the shaft hole 53h other than the end portion. In the sixth embodiment shown in FIG. 14, the shaft hole 53h is not formed small, and the diameter d2 of the end portion of the second metal shaft 61a on the first housing 41 side is larger than the diameter d1 other than the end portion. ing. A resin bearing 95 is formed at this end.

According to the sixth embodiment, since the diameter d2 of the second metal shaft 61a in the resin bearing 95 is large, the contact area in the resin bearing 95 increases. As the contact area of the resin bearing 95 increases, the surface pressure applied to the resin decreases, so that the abrasion of the resin can be reduced.

-Seventh embodiment:
The seventh embodiment shown in FIG. 15 has both the structure of the collar 82 of the fifth embodiment shown in FIG. 13 and the structure of the second metal shaft 61a of the sixth embodiment shown in FIG.

According to the seventh embodiment, as in the fifth embodiment, the second collar portion 82d has the reverse taper shape, so that the collar 82 is more difficult to come off when a large thrust load is applied. There is.

According to the seventh embodiment, as in the sixth embodiment, the contact pressure on the resin is reduced by the increase in the contact area of the resin bearing 95, so that the abrasion of the resin can be reduced.

-Eighth embodiment:
Compared to the fourth embodiment, the second intermediate gear 53 of the eighth embodiment shown in FIG. 16 includes a rolling bearing 91 at the end on the second small diameter outer tooth portion 63 side, and the collar 83 has a first collar. In addition to the parts 83a and the disk part 83c, a disk part 83e and a third collar part 83f are different. The disk portions 83c and 83e are connected by the second collar portion 83d. The rolling bearings 90 and 91 are arranged apart from each other and are in contact with the first collar portion 83a and the third collar portion 83f, respectively.

The outer ring 90o and the inner ring 90i of the rolling bearing 90 on the second large-diameter outer tooth portion 62 side and the outer ring 91o of the rolling bearing 91 on the second small-diameter outer tooth portion 63 side are press-fitted to the second small-diameter outer tooth portion 63 side. The inner ring 91i of the rolling bearing 91 is not press-fitted. That is, the inner diameter of the inner ring 91i is larger than the diameter of the second metal shaft 61. In this way, by making the inner ring 91i of the rolling bearing 91 not press-fit, the second intermediate gear 53 can be easily assembled to the second metal shaft 61. However, you may employ|adopt the structure which press-fits also the inner ring 91i. The position in the thrust direction can be regulated by press fitting.

According to the eighth embodiment, since the two rolling bearings 90 and 91 are provided, it is possible to improve the withstand load and reduce the rolling resistance. The resin forming the second intermediate gear 53 and the second metal shaft 61 are less likely to wear.

According to the eighth embodiment, the two rolling bearings 90 and 91 can be accurately arranged by the collar 83. Since the two rolling bearings 90 and 91 are arranged apart from each other, the second intermediate gear 53 is unlikely to tilt with respect to the second metal shaft 61.

According to the eighth embodiment, the collar 83 includes the disk portions 83c and 83e, and the resin forming the second intermediate gear exists between them, so that even when a large thrust load is applied. The collar 83 is hard to come off from the resin forming the second intermediate gear 53.

According to the eighth embodiment, the collar 83 exists from one end of the second intermediate gear 53 to the other end of the second intermediate gear 53 along the shaft hole 53h. The rigidity between the second small-diameter outer tooth portion 63 and the second small-diameter outer tooth portion 63 can be increased, and the strength against the force to bend the shaft AX2 can be increased.

-Ninth embodiment:
The ninth embodiment shown in FIG. 17 has a configuration in which the collar 83 is removed from the eighth embodiment shown in FIG.

According to the ninth embodiment, since the two rolling bearings 90 and 91 are provided, the load bearing capacity can be improved and the rolling resistance can be reduced. The resin forming the second intermediate gear 53 and the second metal shaft 61 are less likely to wear.

In each of the above-described embodiments, the ball bearings (also referred to as “ball bearings”) have been described as an example of the rolling bearings. Spherical roller bearings, thrust bearings, etc. may be used.

In each of the above-described embodiments, the configuration of the collar and the bearing has been described by taking the second intermediate gear 53 as an example. However, the configuration of the collar and the bearing may be applied to the output gear 54 or the first intermediate gear 52. Is also good.

In each of the above-described embodiments, the actuator that drives the waste gate valve 19 of the supercharger 24 has been described as an example, but the actuator described in each of the embodiments drives the nozzle that changes the direction of the exhaust gas that hits the turbine of the supercharger 24. As an actuator for driving a valve for controlling supercharging pressure in a supercharger, such as an actuator for switching, a twin turbo equipped with two turbines, an actuator for switching a turbine of a two-stage turbo, an actuator for switching a turbine of a variable capacity turbo, and the like. Is also available.

The present disclosure is not limited to the above-described embodiments, and can be realized with various configurations without departing from the spirit thereof. For example, the technical features of the embodiment corresponding to the technical features in each mode described in the column of the outline of the invention are to solve some or all of the above problems, or some of the above effects. Alternatively, in order to achieve all, it is possible to appropriately replace or combine. If the technical features are not described as essential in this specification, they can be deleted as appropriate.

The present disclosure can be realized as the following modes.

(1) According to one aspect of the present disclosure, an actuator (10) that drives a valve (19) that controls exhaust generated by combustion of an internal combustion engine (11) is provided. The actuator includes a motor (36), an output shaft (26), and a reduction unit (37) that reduces the rotation of the motor and transmits the rotation to the output shaft, the reduction unit rotating the motor. An intermediate gear (53) provided between the shaft (55) and the output shaft, the intermediate gear (53) made of resin integrally including a large diameter gear (62) and a small diameter gear (63); An intermediate shaft (61) serving as a rotation center, a rolling bearing (90) for rotatably holding the large diameter gear with respect to the intermediate shaft on the large diameter gear side of the intermediate gear, and the intermediate gear Between the resin bearing (95) for rotatably holding the small-diameter gear with respect to the intermediate shuff, and the outer ring (90o) of the rolling bearing and the large-diameter gear, A collar (80) that is disposed and integrally molded with the resin, the collar including a cylindrical portion (80a) into which the foreign trade fits, and a protrusion () protruding outward from the cylindrical portion. 80b).

(2) In the above-mentioned form, the above-mentioned projection may project from the above-mentioned cylindrical part to the side opposite to the above-mentioned intermediate shaft, and may be embedded in the above-mentioned resin. According to this aspect, since the protruding portion projects from the cylindrical portion to the side opposite to the intermediate shaft and is embedded in the resin, the collar is difficult to come off from the resin forming the intermediate gear, and the rolling bearing also forms the resin forming the intermediate gear. It's hard to get out of.

(3) In the above aspect, the collar may include a collar protruding from the cylindrical portion toward the intermediate shaft. According to this aspect, when the rolling bearing 90 is press-fitted, the brim 80c can be used as a stopper.

(4) In the above-mentioned form, the above-mentioned projection may project outside the tip circle of the above-mentioned gear of a small diameter. According to this aspect, when the rolling bearing is press-fitted into the intermediate gear, the protrusion can be supported by the support member such as a support base via the resin.

(5) In the above-mentioned embodiment, the resin forming the intermediate gear has a hole inside the tip of the protrusion of the collar, the hole being visible through the hole to the outside. May be. According to this aspect, when the rolling bearing is press-fitted into the intermediate gear, the pin inserted into the hole can directly support the protrusion, so that it is difficult to damage the large-diameter gear of the intermediate gear.

(6) According to one aspect of the present disclosure, the actuator (10) that drives the valve (19) that controls the exhaust gas generated by the combustion of the internal combustion engine (11) is provided. The actuator includes a motor (36), an output shaft (26), and a reduction unit (37) that reduces the rotation of the motor and transmits the rotation to the output shaft, the reduction unit rotating the motor. An intermediate gear (53) provided between the shaft (55) and the output shaft, the intermediate gear (53) made of resin integrally including a large diameter gear (62) and a small diameter gear (63); An intermediate shaft (61) serving as a rotation center, a rolling bearing (90) for rotatably holding the large diameter gear with respect to the intermediate shaft on the large diameter gear side of the intermediate gear, and the intermediate gear Between the resin bearing (95) that rotatably holds the small-diameter gear with respect to the intermediate shuff, and the outer ring (90o) of the rolling bearing and the large-diameter gear on the small-diameter gear side. And a collar (80) integrally formed with the resin, wherein the collar is a first collar portion that is a cylindrical portion, and the collar is closer to the gear having the smaller diameter than the first collar portion. It has a stepped structure having a second collar portion (81d) which is a cylindrical portion having a diameter smaller than the diameter of one collar portion. According to this aspect, even when a large thrust load is applied, the collar can be made hard to come off from the resin forming the intermediate gear, and the rolling bearing can be made hard to come off from the resin forming the intermediate gear. Further, the rigidity between the large-diameter gear and the small-diameter gear can be increased, and the strength against the force of bending the large-diameter gear with respect to the small-diameter gear can be increased.

(7) In the above aspect, the outer diameter of the second collar portion on the side of the smaller diameter gear may be larger than the outer diameter of the second collar portion on the side of the larger diameter gear. According to this aspect, the second collar portion has a so-called reverse taper shape in which the outer diameter of the small-diameter gear side is larger than the outer diameter of the large-diameter gear side. In, the color can be more difficult to come off.

(8) In the above embodiment, the outer ring of the rolling bearing contacts the collar, but the inner ring of the rolling bearing is separated from the resin forming the collar and the intermediate gear. According to this aspect, the rolling bearing can be press-fitted to a position where it does not protrude from the collar, so that the size of the intermediate gear can be reduced.

(9) In the above aspect, the intermediate shaft has a stepped shape in which the large-diameter gear side has a small diameter (d1) and the small-diameter gear side has a large diameter (d2), and the collar has the step of the intermediate shaft. It may be separated from the large diameter portion. According to this aspect, the intermediate shaft has a stepped shape in which the large-diameter gear side has a small diameter (d1) and the small-diameter gear side has a large diameter (d2), so that the contact area in the resin bearing increases. As the contact area of the resin bearing increases, the surface pressure applied to the resin decreases, so that the abrasion of the resin can be reduced.

(10) In the above aspect, the resin bearing is in contact with the intermediate shaft only at the end opposite to the rolling bearing, and is separated from the collar. According to this aspect, since the distance between the rolling bearing and the resin bearing can be widened, it is possible to prevent the intermediate gear from tilting with respect to the intermediate shaft.

(11) In the above-mentioned form, the rolling bearing may be a rolling bearing press-fitted between the intermediate shaft and the intermediate gear for both the inner ring and the outer ring. According to this aspect, the position of the rolling bearing in the thrust direction can be regulated by press fitting.

(12) According to one aspect of the present disclosure, an actuator (10) that drives a boost pressure control valve (19) of a supercharger (24) is provided. The actuator includes a motor (36), an output shaft (26), and a reduction unit (37) that reduces the rotation of the motor and transmits the rotation to the output shaft, the reduction unit rotating the motor. An intermediate gear (53) provided between the shaft (55) and the output shaft, the intermediate gear (53) made of resin integrally including a large diameter gear (62) and a small diameter gear (63); An intermediate shaft (61) as a center of rotation, a first rolling bearing (90) provided between the intermediate shaft and the large-diameter gear side end of the intermediate gear, and the intermediate gear. A second rolling bearing (91) provided between the small-diameter gear-side end and the intermediate shaft, and the first rolling bearing and the second rolling bearing are separated from each other. It is arranged. According to this aspect, since the first rolling bearing and the second rolling bearing are arranged apart from each other, the inclination of the intermediate gear with respect to the shaft can be suppressed. As a result, it is possible to suppress the reduction of the meshing ratio due to the variation of the gear pitch caused by the inclination of the intermediate gear, reduce the torque variation caused by the reduction of the meshing ratio, and the radial movement to reduce the input stress.

(13) In the above embodiment, one of the first rolling bearing and the second rolling bearing is a rolling bearing in which the inner ring and the outer ring are press-fitted between the intermediate shaft and the intermediate gear, and the other is Although the outer ring is press-fitted between the intermediate shaft and the intermediate gear, the inner ring may be a rolling bearing that is not press-fitted between the intermediate shaft and the intermediate gear. According to this aspect, it is easy to assemble the intermediate shaft and the intermediate gear.

(14) In the above-described embodiment, a collar (83) provided between the intermediate gear and the intermediate shaft, further comprising a first collar portion (83a) of the first rolling bearing and the intermediate gear. , A collar having a third collar portion (83f) of the second rolling bearing and the intermediate gear, and a second collar portion (83d) connecting the first collar portion and the third collar portion. May be. According to this aspect, the rigidity of the large-diameter gear and the small-diameter gear can be increased, and the strength against the force of bending the large-diameter gear with respect to the small-diameter gear can be increased.

The present disclosure can be realized in various forms. For example, in addition to an actuator used for opening and closing a wastegate valve of a turbocharger, an actuator for switching turbines of a twin turbo equipped with two turbines, It can also be realized as an actuator for controlling supercharging pressure in a supercharger, such as an actuator for switching a turbine of a variable capacity turbo.

10 Actuator 11 Engine 12 Intake Passage 13 Exhaust Passage 14 Intake Compressor 14a Compressor Wheel 14b Compressor Housing 15 Throttle Valve 16 Exhaust Turbine 16a Turbine Wheel 16b Turbine Housing 17 Catalyst 18 Bypass Passage 19 Wastegate Valve 20 Valve Shaft 24 Supercharger 25 Link Mechanism 26 Output Shaft 27 Actuator Lever 28 Rod 29 Valve Lever 30 Rotating Shaft 35 Housing 36 Motor 37 Decelerator 39 Rotation Angle Sensor 41 First Housing Part 42 Second Housing Part (Case) 43 Fastening Member 44 Storage Space 45 Wave Washer 46 Motor Insertion Hole 47 Screw 48, 49 Bearing 51 Pinion gear 52 First intermediate gear 53 Second intermediate gear 53h Shaft hole 53h2 Hole 54 Output gear 55 Motor shaft 56 First metal shaft 57 First large diameter outer tooth portion 58 First small diameter outer tooth portion 61, 61a 2nd metal shaft 62 2nd large diameter outer tooth part 62t tooth 63 2nd small diameter outer tooth part 63t tooth 64 Magnetic circuit part 65 Magnetic flux detection part 66, 67 Magnet 68, 69 Yoke 80 Collar 80a Cylindrical part 80b Projection part 80c brim 81 color 81a first color part 81c disk part 81d second color part 82 color 82a first color part 82c disk part 82d second color part 83 color 83a first color part 83c disk part 83d second color part 83e disk part 83f Third collar portion 90, 91 Rolling bearing 90b, 91b Bearin Gubour 90i, 91i Inner ring 90o, 91o Outer ring 95 Resin bearing 100 Support base 101 Pins AX1, AX2, AX3 Central axis (axis) d1 Diameter d2 Diameter wb, we, thickness

Claims (14)

An actuator (10) for driving a valve (19) for controlling exhaust gas produced by combustion of an internal combustion engine (11),
A motor (36),
An output shaft (26),
A deceleration part (37) for decelerating the rotation of the motor and transmitting it to the output shaft;
Equipped with
The speed reducer is
An intermediate gear (53) which is provided between the rotary shaft (55) of the motor and the output shaft, and which is made of resin and integrally includes a large diameter gear (62) and a small diameter gear (63);
An intermediate shaft (61) serving as a rotation center of the intermediate gear,
A rolling bearing (90) for rotatably holding the large diameter gear with respect to the intermediate shaft on the large diameter gear side of the intermediate gear;
A resin bearing (95) for rotatably holding the small diameter gear with respect to the intermediate shaft on the small diameter gear side of the intermediate gear;
A collar (80) disposed between the outer ring (90o) of the rolling bearing and the large diameter gear and integrally molded with the resin;
Have
The collar includes a cylindrical portion (80a) into which the outer ring fits, and a protrusion (80b) protruding outward from the cylindrical portion.
Actuator. The actuator according to claim 1, wherein
The projecting portion projects from the cylindrical portion to the side opposite to the intermediate shaft, and is embedded in the resin.
Actuator. The actuator according to claim 2, wherein
The collar includes a collar (80c) protruding from the cylindrical portion toward the intermediate shaft,
Actuator. The actuator according to claim 2 or claim 3,
The projecting portion projects outward from a tip circle of the small-diameter gear,
Actuator. The actuator according to claim 4, wherein
The resin forming the intermediate gear has a hole inside the tip of the protruding portion of the collar, which is a hole, and through which the hole can see the collar from the outside.
Actuator. An actuator (10) for driving a valve (19) for controlling exhaust gas produced by combustion of an internal combustion engine (11),
A motor (36),
An output shaft (26),
A deceleration part (37) for decelerating the rotation of the motor and transmitting it to the output shaft;
Equipped with
An intermediate gear (53) which is provided between the rotary shaft (55) of the motor and the output shaft, and which is made of resin and integrally includes a large diameter gear (62) and a small diameter gear (63);
An intermediate shaft (61) serving as a rotation center of the intermediate gear,
A rolling bearing (90) for rotatably holding the large diameter gear with respect to the intermediate shaft on the large diameter gear side of the intermediate gear;
A resin bearing (95) for rotatably holding the small diameter gear with respect to the intermediate shaft on the small diameter gear side of the intermediate gear;
A collar (80) disposed between the outer ring (90o) of the rolling bearing and the large-diameter gear and integrally molded with the resin;
Have
The collar has a first collar portion which is a cylindrical portion, and a second collar portion (81d) which is on the gear side having the smaller diameter than the first collar portion and which is a cylindrical portion having a diameter smaller than the diameter of the first collar portion. And a stepped structure having
Actuator. The actuator according to claim 6, wherein
An outer diameter of the second collar portion on the small-diameter gear side is larger than an outer diameter of the second collar portion on the larger-diameter gear side,
Actuator. The actuator according to any one of claims 1 to 7, wherein
The outer ring of the rolling bearing contacts the collar,
The inner ring of the rolling bearing is separated from the resin forming the collar and the intermediate gear,
Actuator. The actuator according to any one of claims 1 to 8, wherein:
The intermediate shaft has a stepped shape with a small diameter (d1) on the large diameter gear side and a large diameter (d2) on the small diameter gear side,
The collar is spaced from the large diameter portion of the intermediate shaft,
Actuator. The actuator according to any one of claims 1 to 9,
The resin bearing is
Only the end opposite to the rolling bearing contacts the intermediate shaft,
Separated from the collar,
Actuator. The actuator according to any one of claims 1 to 10, wherein:
The rolling bearing is a rolling bearing in which an inner ring and an outer ring are press-fitted between the intermediate shaft and the intermediate gear.
Actuator. An actuator (10) for driving a valve (19) for controlling exhaust gas generated by combustion of an internal combustion engine (11), comprising:
A motor (36),
An output shaft (26),
A deceleration part (37) for decelerating the rotation of the motor and transmitting it to the output shaft;
Equipped with
The speed reducer is
An intermediate gear (53) which is provided between the rotary shaft (55) of the motor and the output shaft, and which is made of resin and integrally has a large diameter gear (62) and a small diameter gear (63);
An intermediate shaft (61) serving as a rotation center of the intermediate gear,
A first rolling bearing (90) provided between the large-diameter gear-side end of the intermediate gear and the intermediate shaft;
A second rolling bearing (91) provided between an end of the intermediate gear on the side of the small diameter gear and the intermediate shaft;
Have
The first rolling bearing and the second rolling bearing are arranged apart from each other,
Actuator. The actuator according to claim 12, wherein
One of the first rolling bearing and the second rolling bearing is a press-fitted rolling bearing between the intermediate shaft and the intermediate gear for both the inner ring and the outer ring, and the other is the outer ring for the intermediate shaft. The inner ring is a rolling bearing that is press-fitted between the intermediate gears but is not press-fitted between the intermediate shaft and the intermediate gears,
Actuator. The actuator according to claim 12 or claim 13, further comprising:
A collar (83) provided between the intermediate gear and the intermediate shaft, the first collar portion (83a) of the first rolling bearing and the intermediate gear, the second rolling bearing and the collar. A collar having a third collar portion (83f) with the intermediate gear and a second collar portion (83d) connecting the first collar portion and the third collar portion,
Actuator.

Images