JP2012122582A - Planetary gear mechanism and actuator for valve - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a planetary gear mechanism allowing dispersing loads while having a large reduction ratio, and an actuator for a valve having the planetary gear mechanism.SOLUTION: The planetary gear mechanism includes a sun gear 11, an internal gear 13, a planetary gear 16 and a carrier 15. The planetary gear 16 includes at least three gears (first to third gears 22-24) that sequentially transmit rotation and constitute one power transmission path.

Description

  The present invention relates to a planetary gear mechanism having a plurality of planetary gears meshing with each other and a valve actuator.

  Conventionally, when a reduction gear is configured using a planetary gear mechanism, a sun gear is often used as an input member, an internal gear is fixed, and a carrier is often used as an output member. In this type of reduction gear, in order to obtain a large reduction gear ratio, it is common to form a planetary gear relatively large. On the other hand, in order to increase the reduction ratio without changing the size of the planetary gear, it can be realized by adopting the configuration described in Patent Document 1, for example.

  The planetary gear type speed reducer disclosed in Patent Document 1 is a planetary gear unit composed of a sun gear, a planetary gear, and a carrier, which is stacked in multiple stages in the axial direction and connected in series. These planetary gear units are arranged so as to be positioned on the same axis in one internal gear. The carrier of these planetary gear units is provided so that the sun gear of the planetary gear unit adjacent to the downstream side in the power transmission direction rotates integrally.

  By the way, in a planetary gear mechanism, it is known that it is effective to disperse a load to as many gears as possible in order to improve durability and reduce manufacturing costs. In order to realize this, it is necessary to increase the number of planetary gears by forming planetary gears with a small diameter.

JP 2002-31259 A

  However, as described above, if the planetary gear is simply formed to reduce the load, the planetary gear type reduction gear has a problem that the reduction ratio becomes relatively small.

  The present invention has been made to solve such a problem, and provides a planetary gear mechanism capable of distributing a load while increasing a gear ratio and a valve actuator having the planetary gear mechanism. Objective.

  In order to achieve this object, a planetary gear mechanism according to the present invention includes a sun gear, an internal gear positioned on the same axis as the sun gear outside the radial direction of the sun gear, the sun gear and the internal gear, A planetary gear that transmits rotation between the planetary gear and a carrier that rotatably supports the planetary gear and revolves around the sun gear, and the planetary gear sequentially transmits rotation. Thus, at least three gears constituting one power transmission path are provided.

  According to the present invention, in the above invention, at least one of the plurality of gears constituting the planetary gear is formed so that the first gear member and the second gear member rotate integrally, and rotates on the carrier. The first gear member meshes with the upstream gear in the power transmission direction, and the second gear member meshes with the downstream gear in the power transmission direction. It is what.

  The present invention provides an internal gear member having a sun gear member comprising the second gear member of the two-stage gear, an internal gear positioned on the same axis as the sun gear member, and fixed to the carrier. A planetary gear member meshing with the sun gear member and an internal gear of the internal gear member, and the planetary gear member rotatably supported and revolving around the sun gear member. And a third gear member rotatably supported by the carrier so that the carrier member rotates integrally, and the third gear member transmits power. Meshing with the gear on the downstream side of the direction.

  The present invention is the above invention, wherein the planetary gear includes a first gear meshing with the sun gear, a second gear meshing with the internal gear positioned on the same axis as the sun gear, and the planetary gear unit. And a third gear that transmits rotation between the first gear and the second gear.

  According to the present invention, in the above invention, the third gear meshes with two second gears, and these second gears mesh with two third gears and the internal gear, respectively. It is what.

  According to the present invention, in the above invention, the third gear meshes with two second gears, and these second gears mesh with one third gear and the internal gear, respectively. It is what.

  According to the present invention, in the above invention, the second gear is a fourth gear member that meshes with a third gear member that rotates integrally with the carrier member in the third gear, and the fourth gear member. A sun gear member that rotates integrally with the sun gear member, an internal gear member that has an internal gear positioned on the same axis as the sun gear member and is fixed to the carrier, the sun gear member, and an internal gear of the internal gear member, A planetary gear member that meshes with the planetary gear member, a carrier member that rotatably supports the planetary gear member and revolves around the sun gear member, and the carrier member so as to rotate integrally. And a fifth gear member which is provided and meshes with the internal gear.

  The present invention is the above invention, wherein the planetary gear includes a first gear meshing with the sun gear, a second gear meshing with the internal gear located on the same axis as the sun gear, and the first gear. A third gear that transmits the rotation between the gear and the second gear is included, and the second gear includes the planetary gear unit.

  According to the present invention, in the above invention, the planetary gear unit portion includes a plurality of planetary gear units each including the sun gear member, the internal gear member, the planetary gear member, and the carrier member arranged on the same axis. Are connected to each other.

  The present invention is the above invention, wherein the carrier includes a carrier body formed in a disk shape, and a support member that stands on the carrier body and supports the planetary gear, and the support member includes the carrier It is fixed in a state of being inserted through an attachment hole formed in the main body.

  The valve actuator according to the present invention includes a housing in which an internal gear located on the same axis as the sun gear in the planetary gear mechanism described in the invention is fixed, and the planetary gear mechanism that is rotatably supported by the housing. An output shaft that rotates integrally with the carrier, and an input shaft that is rotatably supported by the housing and rotates integrally with the sun gear of the planetary gear mechanism.

In the planetary gear mechanism according to the present invention, for example, when a reduction gear having a sun gear as an input member and a carrier as an output member is configured, at least three gears are provided in a power transmission path between the sun gear and the internal gear. The number of these gears (the number of sets) is increased.
Therefore, according to the present invention, it is possible to provide a planetary gear mechanism that can disperse the load while increasing the gear ratio.

It is sectional drawing of the actuator for valves comprised using the planetary gear mechanism which concerns on this invention. It is the top view seen from the axial direction of the planetary gear type reduction gear. The figure is drawn with the planetary gear exposed. It is the III-III sectional view taken on the line in FIG. In FIG. 3, the fracture position of FIG. 2 is indicated by the line II-II. It is a top view seen from the axial direction of the planetary gear type speed reducer, in which the right half is drawn with the first and third gears exposed, and the left half exposes the second gear. It is drawn in the state. It is the VV sectional view taken on the line in FIG. In FIG. 5, the fracture position of FIG. 4 is indicated by the line IV-IV. FIG. 2 is a plan view of the planetary gear speed reducer viewed from the axial direction, in which the right half is drawn with the first and third gears exposed, and the left half exposes the planetary gear unit. It is drawn in the state. It is the VII-VII sectional view taken on the line in FIG. In FIG. 7, the fracture position of FIG. 6 is indicated by the line VII-VII. It is a disassembled perspective view which shows the structure of a planetary gear unit part. FIG. 2 is a plan view of the planetary gear speed reducer viewed from the axial direction, in which the right half is drawn with the first and third gears exposed, and the left half exposes the planetary gear unit. It is drawn in the state. It is the XX sectional view taken on the line in FIG. In FIG. 10, the fracture position of FIG. 9 is indicated by the line IX-IX. FIG. 2 is a plan view of the planetary gear speed reducer viewed from the axial direction, in which the right half is drawn with the first and third gears exposed, and the left half exposes the planetary gear unit. It is drawn in the state. It is the XII-XII sectional view taken on the line in FIG. In FIG. 12, the fracture | rupture position of FIG. 11 is shown by the XI-XI line. FIG. 2 is a plan view of the planetary gear speed reducer viewed from the axial direction, in which the right half is drawn with the first and third gears exposed, and the left half exposes the planetary gear unit. It is drawn in the state. It is the XIV-XIV sectional view taken on the line in FIG. In FIG. 14, the fracture position of FIG. 13 is indicated by the XIII-XIII line. FIG. 2 is a plan view of the planetary gear speed reducer viewed from the axial direction, in which the right half is drawn with the first and third gears exposed, and the left half exposes the planetary gear unit. It is drawn in the state. It is the top view seen from the axial direction of the planetary gear type speed reducer, and in the same figure, the right half is drawn with the second gear exposed, and the left half with the planetary gear unit exposed. It is drawn. It is the XVII-XVII sectional view taken on the line in FIG. In FIG. 17, the fracture position in FIG. 15 is indicated by the XV-XV line, and the fracture position in FIG. 16 is indicated by the XVI-XVI line. It is the top view seen from the axial direction of the planetary gear type speed reducer, and in the same figure, the right half is drawn with the first to third gears exposed, and the left half exposes the planetary gear unit. It is drawn in the state. It is the XIX-XIX sectional view taken on the line in FIG. In FIG. 19, the fracture position of FIG. 17 is indicated by the XVII-XVII line. It is sectional drawing which shows other embodiment of a planetary gear unit part.

(First embodiment)
Hereinafter, an embodiment of a planetary gear mechanism according to the present invention will be described in detail with reference to FIGS. In this embodiment, the case where the planetary gear mechanism according to the present invention is used as a speed reducer will be described. The planetary gear mechanism used in the planetary gear type reduction gear according to this embodiment constitutes the planetary gear mechanism referred to in the first and ninth aspects of the invention. The valve actuator shown in this embodiment constitutes the valve actuator referred to in the invention described in claim 10.

  A valve actuator 1 shown in FIG. 1 includes a planetary gear type speed reducer 3 constituted by a planetary gear mechanism 2 according to the present invention. The actuator 1 is for rotating the valve body 5 of the ball valve 4, and includes a housing 6 having one end fixed to the ball valve 4 and a drive motor provided at the other end of the housing 6. 7. The rotation shaft 8 of the drive motor 7 is connected to the drive shaft 9 of the ball valve 4 via the planetary gear type reduction gear 3 housed in the housing 6. In this embodiment, the rotary shaft 8 constitutes the input shaft of the planetary gear type speed reducer 3. A sun gear 11 of a planetary gear speed reducer 3 to be described later is provided at the tip of the rotating shaft 8 so as to rotate integrally.

  The planetary gear speed reducer 3 includes a casing 12 that is positioned on the outermost side in the radial direction, and is fixed to the housing 6 via the casing 12. As shown in FIGS. 2 and 3, the casing 12 is formed in a bottomed cylindrical shape including a peripheral wall 12 a and a bottom wall 12 b, and is open toward the motor 7 and is on the same axis as the rotary shaft 8. It is fixed to the housing 6 so as to be positioned. An inner gear 13 of the planetary gear type speed reducer 3 is provided on the inner peripheral portion of the peripheral wall 12a.

  The output shaft 14 of the planetary gear speed reducer 3 passes through the center portion of the bottom wall 12b of the casing 12. The output shaft 14 is rotatably supported by the casing 12 by a bearing (not shown). As shown in FIG. 1, the drive shaft 9 of the ball valve 4 is connected to the tip of the output shaft 14 so as to rotate integrally.

  As shown in FIGS. 2 and 3, the planetary gear speed reducer 3 includes the sun gear 11 provided on the rotating shaft 8 of the motor 7, the internal gear 13 provided in the casing 12, and the casing. 12 includes a carrier 15 having the output shaft 14 penetrating through 12 and a planetary gear 16 composed of a plurality of gear members supported by the carrier 15.

The internal gear 13 is located on the same axis as the sun gear 11 outside the sun gear 11 in the radial direction.
As shown in FIG. 3, the carrier 15 includes a carrier body 17 formed in a disk shape, and six first to third support shafts 18 to 20 erected on the carrier body 17. And a reinforcing plate 21 attached to the tip portions of the support shafts 18 to 20.

  The carrier body 17 is fitted with a distal end portion 8a of the rotary shaft 8 in a freely rotatable manner, and the output shaft 14 is integrally formed. The output shaft 14 can be formed separately from the carrier body 17 and can be fixed to the carrier body 17 by press fitting. The support shafts 18 to 20 are press-fitted into mounting holes 17 a to 17 c formed in the carrier body 17. In this embodiment, the support shafts 18 to 20 constitute a “support member” according to the invention of claim 9.

  The reinforcing plate 21 is formed in an annular plate shape, and the tip portions of the support shafts 18 to 20 are connected so that the tip portions of the support shafts 18 to 20 are connected via the reinforcing plate 21. Installed on. These support shafts 18 to 20 are for supporting each gear of the planetary gear 16 described later. The sun gear 11 is inserted through the opening at the center of the reinforcing plate 21.

  The planetary gear 16 is for transmitting rotation between the sun gear 11 and the internal gear 13, and is constituted by a plurality of gears supported on the support shafts 18 to 20 of the carrier 15. As shown in FIGS. 2 and 3, the planetary gear 16 according to this embodiment includes six first gears 22 that mesh with the sun gear 11 and six second gears that mesh with the internal gear 13. 23 and six third gears 24 that transmit the rotation between the first gear 22 and the second gear 23. That is, the planetary gear 16 according to this embodiment includes three gears (first to third gears 22 to 24) that sequentially transmit rotation and constitute one power transmission path. In addition, the said gearwheel which comprises the planetary gear 16 is not limited to three pieces, It can increase further.

  The first gear 22 is accommodated in a space surrounded by two third gears 24, 24 adjacent to each other and the sun gear 11. These first gears 22 are rotatably supported by the second support shaft 19. The outer diameters of the first gears 22 are smaller than those of the third gear 24 and the sun gear 11 in this embodiment. Further, the first gear 22 meshes with the third gear 24 so that the rotation of the sun gear 11 is transmitted to the two third gears 24, 24 adjacent to each other.

  The second gear 23 according to this embodiment is accommodated in a space surrounded by two third gears 24, 24 adjacent to each other and the internal gear 13. These second gears 23 are rotatably supported by the third support shaft 20. Further, the outer diameters of these second gears 23 are formed so as to be smaller than that of the third gear 24 and the sun gear 11 and larger than that of the first gear 22 in this embodiment. . Further, the second gear 23 meshes with the third gear 24 so that the rotation of the two third gears 24 adjacent to each other is transmitted to the internal gear 13.

  The six third gears 24 are arranged around the sun gear 11 and are arranged on a circumference around the sun gear 11. These third gears 24 are rotatably supported by the first support shaft 18. Further, the outer diameter of the third gear 24 is formed to be larger than the outer diameter of the sun gear 11 in this embodiment.

In the planetary gear type speed reducer 3 configured as described above, when the sun gear 11 is rotated by the drive by the drive motor 7, this rotation is transmitted to the third gear 24 via the first gear 22. The rotation of the third gear 24 is transmitted to the internal gear 13 via the second gear 23. As a result, the second gear 23 revolves around the sun gear 11 while meshing with the internal gear 13, and the carrier 15, the output shaft 14, and the drive shaft 9 of the ball valve 4 rotate together, and the ball The angle of the valve body 5 of the valve 4 changes.
For this reason, in this embodiment, the rotation of the sun gear 11 is transmitted to the internal gear 13 via the first gear 22 to the third gear 24, and the rotation of the carrier 15 is decelerated.

  Therefore, according to this embodiment, it is possible to provide the planetary gear type speed reducer 3 capable of distributing the load while maintaining the speed reduction ratio. The reduction ratio of the planetary gear type reduction gear 3 according to this embodiment is about 5.5, which is equivalent to the case where the planetary gear 16 is constituted by only four gears arranged on the same circumference. That is, the planetary gear type reduction gear 3 according to this embodiment has six first to first gears although the reduction ratio is substantially equal to that of the planetary gear type reduction device having the four planetary gears. Since the load is dispersed by the third gears 22 to 24, the durability can be improved, the size can be reduced, and the manufacturing cost can be reduced according to the selection of the load and the material.

  The reason why the durability is improved is that the load transmitted by the teeth of each gear is reduced. The reason why the manufacturing cost can be reduced is that the rigidity required for the gear is reduced, and each gear can be made of a cheaper material or can be manufactured by a general-purpose manufacturing method. For example, the first to third gears 22 to 24 can be formed by sintering, and the gears 22 to 24 can be manufactured at low cost.

The carrier 15 according to this embodiment includes a carrier main body 17 formed in a disk shape, and first to third supporting the first to third gears 22 to 24 by being erected on the carrier main body 17. The support shafts 18 to 20 are provided.
The first to third support shafts 18 to 20 are fixed in a state where the first to third support shafts 18 to 20 are inserted through attachment holes 17 a to 17 c formed in the carrier body 17.

  For this reason, when forming the planetary gear mechanism 2 in which the number and the reduction ratio of the first to third gears 22 to 24 are different, the positions and dimensions of the mounting holes 17a to 17c with respect to the carrier body 17 of the carrier 15 and the like. You just need to change. That is, in forming a plurality of types of planetary gear mechanisms 2, the carrier body 17 of the carrier 15, which is a large component, can be shared, so that the manufacturing cost can be kept low.

The valve actuator 1 according to this embodiment includes a housing 6 to which the casing 12 of the planetary gear type speed reducer 3 is fixed, and is rotatably supported by the housing 6 and integrated with a carrier 15 of the planetary gear mechanism 2. And an input shaft (rotary shaft 8) that is rotatably supported by the housing 6 and transmits the rotation to the sun gear 11 of the planetary gear mechanism 2.
For this reason, according to this embodiment, it is possible to provide the valve actuator 1 including the planetary gear type speed reducer 3 which is small but has a large reduction ratio.

  In the planetary gear speed reducer 3 according to this embodiment, a large number of planetary gears (six first to third gears 22 to 24) are accommodated between the sun gear 11 and the internal gear 13. The space utilization in the internal gear 13 is high. For this reason, according to this embodiment, it is possible to provide the planetary gear type speed reducer 3 that is improved in durability, reduced in size, and reduced in manufacturing cost in accordance with selection of a load and a material.

(Second Embodiment)
The planetary gear can be configured as shown in FIGS. 4 and 5, members identical or equivalent to those described with reference to FIGS. 1 to 3 are given the same reference numerals, and detailed description thereof is omitted as appropriate.
The planetary gear type speed reducer 3 according to this embodiment has the same configuration as the planetary gear type speed reducer shown in the first embodiment described above except that the configuration of the second gear 23 is different. The planetary gear mechanism 2 used in the planetary gear type reduction gear according to this embodiment constitutes the planetary gear mechanism referred to in the invention described in claim 2.

  The planetary gear 16 of the planetary gear type speed reducer 3 shown in FIGS. 4 and 5 includes six first gears 22 (see the right half of FIG. 4 and FIG. 5) that mesh with the sun gear 11, and an internal gear. 6 second gears 23 (see the left half of FIG. 4 and FIG. 5) and six third gears that transmit rotation between the first and second gears 22 and 23. Gear 24 (see FIG. 5).

  The third gear 24 according to this embodiment is constituted by a two-stage gear as shown in FIG. The two-stage gear is formed such that the first gear member 25 and the second gear member 26 rotate integrally. As shown in the right half of FIG. 4, the first gear member 25 meshes with the first gear 22 that is an upstream gear in the power transmission direction. As shown in the left half part of FIG. 4, the second gear member 26 meshes with a second gear 23 that is a downstream gear in the power transmission direction. In this embodiment, the first gear member 25 is formed to have a larger diameter than the second gear member 26.

  As shown in FIG. 4, the second gear 23 according to this embodiment is positioned between the two second gear members 26, 26, and the second gear members 26, 26, It meshes with the internal gear 13. The second gear 23 is rotatably supported on the third support shaft 20 of the carrier 15. As shown in FIG. 5, the planetary gear speed reducer 3 according to this embodiment includes a plate 27 for supporting the tip portion of the third support shaft 20. The plate 27 is formed in a disc shape, and is fixed to be overlapped with one end surface of the carrier 15.

In this embodiment, the rotation transmitted from the sun gear 11 via the first gear 22 is decelerated from the third gear 24 (first gear member 25) via the second gear member 26. It is transmitted to the second gear 23.
Therefore, according to this embodiment, since the third gear 24 is also decelerated, it is possible to provide a planetary gear type speed reducer 3 in which the reduction ratio is larger than in the case of adopting the form shown in the first embodiment. Can do.

(Third embodiment)
The planetary gear can be configured as shown in FIGS. 6 to 8, the same or equivalent members as those described with reference to FIGS. 1 to 5 are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate. The planetary gear mechanism 2 used in the planetary gear type reduction gear according to this embodiment constitutes the planetary gear mechanism referred to in the invention described in claims 3 to 5.

  The planetary gear 16 of the planetary gear type speed reducer 3 shown in FIGS. 6 and 7 includes six first gears 22 that mesh with the sun gear 11 and six second gears 23 that mesh with the internal gear 13 ( The left half of FIG. 6 and FIG. 7) and six sets of third gears 24 that transmit rotation between the first and second gears 22 and 23 (see the left half of FIG. 6 and FIG. 7). ) And.

  As shown in FIG. 7, the third gear 24 according to this embodiment includes a two-stage gear composed of the first gear member 25 and the second gear member 26, and a first support together with the two-stage gear. A third gear member 28 rotatably supported on the shaft 18 and a planetary gear unit 31 that transmits rotation between the two-stage gear and the third gear member 28 are configured. As shown in the left half of FIG. 6, the third gear member 28 meshes with two second gears 23 that are gears on the downstream side in the power transmission direction. The second gears 23 according to this embodiment are respectively meshed with two third gear members 28 (third gears 24).

  The first gear member 25 and the third gear member 28 are located on the same axis and are rotatably supported by the first support shaft 18. In this embodiment, the outer diameter of the first gear member 25 is formed to be larger than the outer diameter of the sun gear 11. The outer diameter of the third gear member 28 is formed to be equal to the outer diameter of the first gear member 25 in this embodiment.

  The planetary gear unit 31 is constituted by a single planetary gear unit 31A that constitutes a planetary gear reducer that decelerates the rotation of the first gear member 25 and transmits it to the third gear member 28. In the planetary gear unit 31, the second gear member 26 is a sun gear member (hereinafter referred to as a sun gear member 32), and an internal gear 33 positioned on the outer side in the radial direction of the sun gear member 32 is 6. And a planetary gear member 35 that meshes with the sun gear member 32 and the internal gear 33 of the internal gear member 34, and a carrier member 36 that rotatably supports the planetary gear member 35. ing.

  As shown in the left half of FIG. 6, the internal gear member 34 is formed by a single disk provided with internal gears 33 at six locations. The internal gear 33 of the internal gear member 34 is provided so as to penetrate through the disk at six locations corresponding to the first and third gears 25 and 28 in the disk. In this embodiment, the inner gear 33 has an inner diameter that is smaller than the outer diameter of the first gear member 25. As shown in FIG. 7, the disk constituting the internal gear member 34 is fixed to and supported by the carrier body 17 and the distal end portion of the third support shaft 20.

The carrier member 36 is constituted by a pin 36 a formed integrally with the third gear member 28. That is, the carrier member 36 is provided so as to rotate integrally with the third gear member 28. Although not shown, the pin 36 a is formed separately from the third gear member 28, and is press-fitted into an attachment hole formed in the third gear member 28, thereby providing a third gear member. 28 can be fixed. In this embodiment, six pins 36a are erected so as to be arranged on one third gear member 28 on the same circumference. For this reason, the carrier member 36 supports the six planetary gear members 35.
As described above, the third gear member 28 having the carrier member 36 is rotatably supported by the first support shaft 18. For this reason, the planetary gear member 35 is supported by the carrier member 36 so as to be rotatable (spinned) and is revolved around the sun gear member 32.

  In the planetary gear type reduction gear 3 according to this embodiment, the rotation of the first gear 22 is transmitted to the first gear member 25 of the third gear 24, and the sun gear member 32 of the planetary gear unit portion 31. Is transmitted to. That is, when the sun gear member 32 rotates, the six planetary gear members 35 meshing with the sun gear member 32 are rotated around the pins 36a of the carrier member 36, and meshed with the internal gear 33 of the internal gear member 34 while being engaged with the sun gear 33. Revolve around the member 32.

  As a result, the rotation of the sun gear member 32 is decelerated and transmitted to the carrier member 36 that supports the planetary gear member 35 and the third gear member 28, and the carrier member 36 and the third gear member 28 are transmitted to the support shaft. Rotate around 18. As the third gear member 28 rotates in this manner, the second gear 23 rotates while meshing with the internal gear 13, and the carrier 15 rotates integrally with the drive shaft 9 of the ball valve 4.

For this reason, in the planetary gear type reduction gear 3 according to this embodiment, the rotation transmitted to the third gear 24 is decelerated by the planetary gear unit 31 in the third gear 24 and is transferred to the second gear 23. Communicated.
Therefore, according to this embodiment, it is possible to configure the planetary gear type speed reducer 3 that can obtain a larger reduction ratio than that shown in the first embodiment.

(Fourth embodiment)
The planetary gear can be configured as shown in FIGS. 9 and 10, members identical or equivalent to those described with reference to FIGS. 1 to 8 are given the same reference numerals, and detailed description thereof is omitted as appropriate. The planetary gear mechanism 2 used in the planetary gear type reduction gear according to this embodiment constitutes the planetary gear mechanism referred to in the invention described in claims 3 to 5.

The planetary gear 16 of the planetary gear type reduction gear 3 shown in FIGS. 9 and 10 is different from the planetary gear 16 shown in FIGS. 6 to 8 in that the number of planetary gear members 35 is three, and each gear. The same configuration is adopted except that the outer diameter of each is different.
That is, the third gear 24 according to this embodiment includes a planetary gear unit 31 having three planetary gear members 35 as shown in FIG. The planetary gear unit 31 according to this embodiment is constituted by a single planetary gear unit 31A.

  Further, in this embodiment, the third gear member 28 of the third gear 24 is relatively different from that shown in the third embodiment described above (see FIGS. 6 to 8). It has a small diameter. The outer diameter of the third gear member 28 according to this embodiment is formed to have the same size as the sun gear member 32 of the planetary gear unit portion 31. On the other hand, the outer diameter of the second gear 23 that meshes with the third gear member 28 is formed to be larger than the outer diameter of the third gear member 28.

According to this embodiment, the rotation of the first gear member 25 and the third gear member 28 is also reduced and transmitted to the second gear 23.
Therefore, according to this embodiment, it is possible to provide the planetary gear type speed reducer 3 having a larger reduction ratio than when the third embodiment described above is employed.

(Fifth embodiment)
The planetary gear can be configured as shown in FIGS. 11 and 12, members identical or equivalent to those described with reference to FIGS. 1 to 10 are given the same reference numerals, and detailed description thereof is omitted as appropriate. The planetary gear mechanism 2 used in the planetary gear type reduction gear according to this embodiment constitutes the planetary gear mechanism referred to in the invention described in claim 6.

The planetary gear 16 of the planetary gear type speed reducer 3 shown in FIGS. 11 and 12 is different from the planetary gear 16 shown in FIGS. 6 to 8 in that the number and outer diameter of the second gear 23 are different. Have the same structure.
The third gear 24 according to this embodiment meshes with the two second gears 23 and 23. Each of these second gears 23 meshes with one third gear 24 and the internal gear 13. For this reason, since the planetary gear 16 according to this embodiment includes six sets of the third gear 24, twelve second gears 23 are used.

The outer diameters of these second gears 23 are formed in the same size as the first gears 22 in this embodiment. Each of the second gears 23 is rotatably supported by the third support shaft 20. The tip portion of the third spindle 20 according to this embodiment is fixed to the internal gear member 34 of the planetary gear unit portion 31.
In this embodiment, since two second gears 23 meshing with one set of third gears 24 are provided, the number of meshes between the second gear 23 after deceleration and the internal gear 13 ( Since the load distribution in the internal gear does not decrease, the planetary gear type speed reducer 3 is provided in which the load is further distributed as compared with the case of adopting the third and fourth embodiments (see FIGS. 6 to 10). be able to.

(Sixth embodiment)
The planetary gear can be configured as shown in FIGS. 13 and 14, the same or equivalent members as those described with reference to FIGS. 1 to 12 are given the same reference numerals, and detailed description thereof is omitted as appropriate. The planetary gear mechanism 2 used in the planetary gear type reduction gear according to this embodiment constitutes the planetary gear mechanism referred to in the invention described in claim 6.

The planetary gear 16 of the planetary gear type speed reducer 3 shown in FIGS. 13 and 14 is different from the planetary gear 16 shown in FIGS. 11 and 12 in that the number of planetary gear members 35 is three and each gear. The same configuration is adopted except that the outer diameter of each is different.
As shown in FIG. 13, the third gear 24 according to this embodiment includes a planetary gear unit 31 having three planetary gear members 35. The planetary gear unit 31 according to this embodiment is constituted by a single planetary gear unit 31A.
Further, in this embodiment, the third gear member 28 of the third gear 24 is relatively different from that shown in the fifth embodiment (see FIGS. 11 and 12) described above. It has a small diameter. The outer diameter of the third gear member 28 according to this embodiment is formed to have the same size as the sun gear member 32 of the planetary gear unit portion 31.

  The third gear 24 according to this embodiment meshes with the two second gears 23 and 23. Each of these second gears 23 meshes with one third gear 24 and the internal gear 13. For this reason, since the planetary gear 16 according to this embodiment includes six sets of the third gear 24, twelve second gears 23 are used.

  In this embodiment, since two second gears 23 meshing with one set of third gears 24 are provided, the number of meshes between the second gear 23 after deceleration and the internal gear 13 ( Since the load distribution in the internal gear does not decrease, the planetary gear type speed reducer 3 is provided in which the load is further distributed as compared with the case of adopting the third and fourth embodiments (see FIGS. 6 to 10). be able to.

(Seventh embodiment)
The planetary gear can be configured as shown in FIGS. 15 to 17, the same or equivalent members as those described with reference to FIGS. 1 to 14 are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate. The planetary gear mechanism 2 used in the planetary gear type reduction gear according to this embodiment constitutes a planetary gear mechanism referred to in the invention described in claim 7.

The planetary gear 16 of the planetary gear speed reducer 3 shown in FIGS. 15 to 17 is the same as the planetary gear 16 shown in FIGS. 13 and 14 except that the configuration of the second gear 23 is different. It has been.
The second gear 23 according to this embodiment includes a fourth gear member 41 (see the right half of FIG. 16) that meshes with the third gear member 28 and a fifth gear that meshes with the internal gear 13 of the casing 12. Gear member 42 and a planetary gear unit 43 that transmits rotation between the fourth gear member 41 and the fifth gear member 42. The planetary gear unit 43 according to this embodiment is constituted by a single planetary gear unit 43A.

  In this embodiment, the fourth gear member 41 and the fifth gear member 42 are formed to have the same outer diameter. The outer diameters of the fourth and fifth gear members 41 and 42 are formed so as to be larger than those of the third gear member 28 in this embodiment. Further, the fourth and fifth gear members 41 and 42 are rotatably supported by the third support shaft 20, respectively.

  The planetary gear unit 43 provided in the second gear 23 includes a sun gear member 44 provided in the fourth gear member 41, as shown in the left half of FIG. 16 and FIG. An internal gear member 46 having an internal gear 45 formed at a position corresponding to the fourth gear member 41, a planetary gear member 47 meshing with the sun gear member 44 and the internal gear 45, and the planetary gear member 47 And a carrier member 48 for supporting the above.

The sun gear member 44 is configured to rotate integrally with the fourth gear member 41.
The internal gear member 46 has a structure equivalent to that of the internal gear member 34 provided in the third gear 24. As shown in FIG. 17, the first support shaft 18 and the third support shaft 20 have a structure. It is fixed to the carrier 15 in a penetrating state.

  The carrier member 48 is constituted by three pins 48 a that rotatably support the planetary gear member 47. These pins 48 a protrude from the fifth gear member 42 and rotate integrally with the fifth gear member 42. In other words, the planetary gear member 47 is supported by the carrier member 48 so as to be rotatable (spinning) around the pin 48 a and is revolved around the sun gear member 44.

  In the planetary gear speed reducer 3 according to this embodiment, a planetary gear unit portion 31 provided in the third gear 24 and a planetary gear unit portion 43 provided in the second gear 23 are connected in series. Therefore, the reduction ratio can be further increased as compared with the case where the above-described embodiments are adopted.

(Eighth embodiment)
The planetary gear can be configured as shown in FIGS. 18 and 19, the same or equivalent members as those described with reference to FIGS. 1 to 17 are denoted by the same reference numerals, and detailed description thereof is omitted as appropriate. The planetary gear mechanism 2 used in the planetary gear type reduction gear according to this embodiment constitutes a planetary gear mechanism referred to in the invention described in claim 8.

  The planetary gear 16 shown in FIGS. 18 and 19 includes six first gears 22 that mesh with the sun gear 11, six sets of second gears 23 that mesh with the internal gear 13, and these first members. 6 and the third gear 24 that transmits the rotation between the second gear 23 and the second gear 23. As shown in FIG. 18, the first gear 22 and the third gear 24 according to this embodiment are positioned so as to be positioned on the diameter of the internal gear 13 when viewed from the axial direction, and mesh with each other. .

  The first and third gears 22 and 24 according to this embodiment are the same. In this embodiment, the outer diameters of the first and third gears 22 and 24 are formed to have the same size as that of the first gear 22 shown in each of the above-described embodiments. The first and third gears 22 and 24 are rotatably supported by the second support shaft 19 and the first support shaft 18, respectively.

  The second gear 23 according to this embodiment has the same configuration as that of the second gear shown in the embodiment shown in FIGS. That is, the second gear 23 includes a fourth gear member 41 (see the right half of FIG. 18) that meshes with the third gear 24 and a fifth gear member 42 (FIG. 18) that meshes with the internal gear 13. 19), and a planetary gear unit 43 that transmits rotation between the fourth gear member 41 and the fifth gear member 42. The planetary gear unit 43 according to this embodiment is constituted by a single planetary gear unit 43A.

  The planetary gear unit 43 has a sun gear member 44 provided on the fourth gear member 41 and a position corresponding to the fourth gear member 41, as shown in the left half of FIG. An internal gear member 46 having an internal gear 45 formed thereon, a planetary gear member 47 that meshes with the sun gear member 44 and the internal gear 45, and a carrier member 48 that supports the planetary gear member 47. .

  The sun gear member 44 is configured to rotate integrally with the fourth gear member 41. The internal gear member 46 has a structure equivalent to the internal gear member 34 provided in the third gear 24 shown in FIGS. 15 to 17, and as shown in FIG. 19, the first to third support members. The shafts 18 to 20 are fixed to the carrier 15 so as to penetrate therethrough.

The carrier member 48 is constituted by three pins 48 a that rotatably support the planetary gear member 47. These pins 48 a protrude from the fifth gear member 42 and rotate integrally with the fifth gear member 42. In other words, the planetary gear member 47 is supported by the carrier member 48 so as to be rotatable (spinning) around the pin 48 a and is revolved around the sun gear member 44.
Even if the planetary gear 16 is configured in this manner, the same effects as in the case of adopting the above-described embodiments are obtained.

(Ninth embodiment)
The planetary gear unit can be configured as shown in FIG. 20, members identical or equivalent to those described with reference to FIGS. 1 to 19 are given the same reference numerals, and detailed description thereof is omitted as appropriate. The planetary gear mechanism 2 used in the planetary gear type reduction gear 3 according to this embodiment constitutes a planetary gear mechanism referred to in the invention described in claim 9.

  A planetary gear unit 31 shown in FIG. 20 includes a planetary gear unit 31A composed of a sun gear member 32 constituted by the second gear member 26, a carrier member 36, an internal gear member 34, and a planetary gear member 35. And a planetary gear unit 31B having a sun gear 61 that rotates integrally with the carrier member 27.

  The planetary gear unit 31B includes the sun gear member 61 formed integrally with the carrier member 36, and an internal gear member 63 having four internal gears 62 positioned outside in the radial direction of the sun gear member 61; The planetary gear member 64 meshes with the sun gear member 61 and the internal gear 62 of the internal gear member 63, and a carrier member 65 that rotatably supports the planetary gear member 64.

The carrier member 65 is constituted by a pin 65 a formed integrally with the third gear member 28.
That is, the planetary gear unit 31 according to this embodiment is configured by arranging two planetary gear units 31A and 31B on the same axis and connecting them in multiple stages (in series).
In the planetary gear speed reducer 3 according to this embodiment, since the two planetary gear units 31A and 31B are connected in series, the reduction ratio can be further increased as compared with the case where the above-described embodiments are adopted. It becomes possible.

  In this embodiment, an example in which the planetary gear unit 31 of the first gear 24 is configured by two planetary gear units 31A and 31B has been described. However, the seventh embodiment and the eighth embodiment described above are illustrated. The planetary gear unit 43 shown in the form can also be constituted by two planetary gear units connected in multiple stages as described above.

  In addition, the number, size, and arrangement of each constituent member in each of the above-described embodiments are merely examples, and can be appropriately designed according to the intended use including the number of teeth of each gear member.

  In each of the above-described embodiments, the sun gear 11 is used as an input member, the internal gear 13 is used as a fixed member, and the carrier 15 is used as an output member. However, the input and output modes may be changed as appropriate. it can. In the above-described embodiment, an example in which the planetary gear mechanism 2 according to the present invention is used as a speed reducer has been described. However, the present invention is not limited to such a limitation and can be used as a speed increaser. it can. In this case, the carrier 15 is an input member, one of the sun gear 11 and the internal gear 13 is a fixing member, and the other is an output member.

  DESCRIPTION OF SYMBOLS 1 ... Valve actuator, 2 ... Planetary gear mechanism, 3 ... Planetary gear type reduction gear, 6 ... Housing, 7 ... Drive motor, 8 ... Rotating shaft, 11 ... Sun gear, 12 ... Casing, 13 ... Internal gear, 14 DESCRIPTION OF SYMBOLS ... Output shaft, 15 ... Carrier, 16 ... Planetary gear, 17 ... Carrier body, 17a-17c ... Mounting hole, 18 ... First spindle, 19 ... Second spindle, 20 ... Third spindle, 22 1st gear, 23 ... 2nd gear, 24 ... 3rd gear, 25 ... 1st gear member, 26 ... 2nd gear member, 28 ... 3rd gear member, 31, 43 ... planetary gear Unit part, 31A, 31B, 43A ... Planetary gear unit, 32, 44 ... Sun gear member, 36, 48 ... Carrier member, 34, 46 ... Internal gear member, 35, 47 ... Planetary gear member, 41 ... Fourth gear Member, 42... Fifth gear member.

Claims (11)

The sun gear,
An internal gear positioned on the same axis as the sun gear on the outer side in the radial direction of the sun gear;
A planetary gear for transmitting rotation between the sun gear and the internal gear;
A carrier that rotatably supports the planetary gear and supports the planetary gear so as to revolve around the sun gear;
The planetary gear mechanism includes at least three gears that sequentially transmit rotation to form one power transmission path. 2. The planetary gear mechanism according to claim 1, wherein at least one of the plurality of gears constituting the planetary gear is formed so that a first gear member and a second gear member rotate integrally, and the carrier. Is a two-stage gear rotatably supported by
The first gear member meshes with a gear on the upstream side in the power transmission direction,
The planetary gear mechanism characterized in that the second gear member meshes with a gear on the downstream side in the power transmission direction. The planetary gear mechanism according to claim 2, wherein a sun gear member comprising a second gear member of the two-stage gear;
An internal gear member having an internal gear located on the same axis as the sun gear member and fixed to the carrier;
A planetary gear member meshing with the sun gear member and an internal gear of the internal gear member;
A planetary gear unit portion comprising a carrier member that rotatably supports the planetary gear member and supports the planetary gear member so as to revolve around the sun gear member;
A third gear member rotatably supported by the carrier so that the carrier member rotates integrally,
The planetary gear mechanism characterized in that the third gear member meshes with a gear on the downstream side in the power transmission direction. The planetary gear mechanism according to claim 3, wherein the planetary gear is a first gear meshing with the sun gear;
A second gear meshing with the internal gear located on the same axis as the sun gear;
A planetary gear mechanism, characterized in that it is composed of a third gear for transmitting rotation between said planetary gear unit section having a and the first and second gears. The planetary gear mechanism according to claim 4, wherein the third gear meshes with two second gears,
Each of these second gears meshes with two third gears and the internal gear, respectively. The planetary gear mechanism according to claim 4, wherein the third gear meshes with two second gears,
Each of the second gears meshes with one third gear and the internal gear, respectively. 5. The planetary gear mechanism according to claim 4, wherein the second gear is a fourth gear member that meshes with a third gear member that rotates integrally with the carrier member in the third gear;
A sun gear member that rotates integrally with the fourth gear member;
An internal gear member having an internal gear located on the same axis as the sun gear member and fixed to the carrier;
A planetary gear member meshing with the sun gear member and an internal gear of the internal gear member;
A carrier member that rotatably supports the planetary gear member and supports the planetary gear member so as to revolve around the sun gear member;
A planetary gear mechanism comprising: a fifth gear member provided so that the carrier member rotates integrally and meshing with the internal gear. The planetary gear mechanism according to claim 3, wherein the planetary gear is a first gear meshing with the sun gear;
A second gear meshing with the internal gear located on the same axis as the sun gear;
A third gear that transmits rotation between the first gear and the second gear;
The planetary gear mechanism, wherein the second gear has the planetary gear unit.   The planetary gear mechanism according to any one of claims 3 to 8, wherein the planetary gear unit portion includes the sun gear member, the internal gear member, the planetary gear member, and the carrier member. A planetary gear mechanism comprising a plurality of planetary gear units comprising: The planetary gear mechanism according to any one of claims 1 to 9, wherein the carrier is a carrier body formed in a disc shape;
A support member that is erected on the carrier body and supports the planetary gear,
The planetary gear mechanism, wherein the support member is fixed in a state of being inserted through an attachment hole formed in the carrier body. A housing in which an internal gear located on the same axis as the sun gear in the planetary gear mechanism according to any one of claims 1 to 10 is fixed;
An output shaft that is rotatably supported by the housing and rotates integrally with the carrier of the planetary gear mechanism;
An actuator for a valve, comprising: an input shaft rotatably supported by the housing and rotating integrally with a sun gear of the planetary gear mechanism.

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