JP2014080154A - Steering machine and ship including the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a small-sized steering machine which drives a rudder at high speed-reduction ratio, and a ship including the steering machine.SOLUTION: A steering machine 100 comprises: a rudder shaft gear 2 fixed to an end portion of a rudder shaft 1; a fixed shaft gear 4 which is provided by having the same axis line as the rudder shaft 1 and fixed to an end portion of a fixed shaft 3 which is fixed to a hull side; a carrier 5 rotatably installed around the fixed shaft 3; a driving gear 6c which rotates the carrier 5; and a driving source 6a which drives the driving gear 6c. The carrier 5 has a plurality of planetary shafts 30a,30b, each of the plurality of planetary shafts 30a,30b rotatably supports planetary gears 10a,10b meshed with fixed shaft gear 4 and planetary gears 20a,20b meshed with the rudder shaft gear 2, and an intermeshing pitch circle diameter of the rudder shaft gear 2 with which the planetary gears 20a,20b are meshed is different from an intermeshing pitch circle diameter of the fixed shaft gear 4 with which the planetary gears 10a,10b are meshed.

Description

  The present invention relates to a steering machine and a ship equipped with the steering machine.

  2. Description of the Related Art Conventionally, hydraulic steering machines such as a Rapson slide type steering machine have been known as steering machines for operating a boat rudder. Although the hydraulic steering machine has the advantage that it can give a large rotational force to the rudder shaft connected to the rudder, it converts the electric power into hydraulic pressure using an electric motor or the like, so that the energy efficiency is deteriorated. There is. In addition, hydraulic steerers may cause marine pollution due to leakage of hydraulic oil to the outside.

In view of the problems of the hydraulic steering as described above, other types of steering are proposed.
For example, Patent Literature 1 discloses a steering machine that rotates a gear provided on a turning wheel fixed to a steering shaft of a ship via a pinion attached to an electric motor.

JP 2007-8189 A

However, the steering machine disclosed in Patent Document 1 has the following problems, for example.
In order to transmit sufficient torque to the rudder shaft, it is necessary to sufficiently increase the ratio (reduction ratio) of the rotational speed of the pinion attached to the electric motor to the rotational speed of the gear provided on the turning wheel. However, in order to increase the reduction ratio, it is necessary to make the number of gear teeth provided on the swivel wheel sufficiently larger than the number of teeth of the pinion. If it does so, the gearwheel provided in a turning wheel will enlarge, As a result, there exists a problem that the whole steering machine will enlarge.

  Further, the steering machine disclosed in Patent Document 1 performs one-stage deceleration with the pinion of the electric motor and the gear provided on the swivel wheel, so that the drive shaft of the electric motor is compared with the case of performing multi-stage deceleration. A large force (reaction force) is applied. Therefore, it is necessary to take measures such as sufficiently thickening the drive shaft and increasing the strength of the case that houses the electric motor. Furthermore, since a large force is also applied to the seat on which the electric motor is installed, it is necessary to reinforce the seat.

  This invention is made | formed in view of such a situation, and it aims at providing the steering machine which drives a rudder with a small reduction ratio and a high reduction ratio, and a ship provided with the same.

In order to achieve the above object, the present invention employs the following means.
A steering machine according to the present invention is a steering machine for driving a ship's rudder via a rudder shaft connected to the rudder, the rudder shaft gear fixed to the end of the rudder shaft, and the rudder A fixed shaft gear fixed to the end of a fixed shaft fixed on the hull side and provided around the fixed shaft and provided with a carrier gear on the outer periphery. A carrier, a drive gear that transmits a driving force to the carrier gear and rotates the carrier around the fixed shaft, and a drive source that drives the drive gear, and the carrier has a plurality of planetary shafts. Each of the plurality of planetary shafts rotatably supports a first planetary gear that meshes with the fixed shaft gear and a second planetary gear that meshes with the rudder shaft gear, and the rudder shaft that meshes with the second planetary gear. The meshing pitch circle diameter of the gear and the first planetary gear are in mesh Cormorant wherein a working pitch circle diameter of the fixed shaft gears are different from each other.

  The steering machine according to the present invention is provided with a rudder shaft gear fixed to the end portion of the rudder shaft, the same axis as the rudder shaft, and fixed to the end portion of the fixed shaft fixed to the hull side. A fixed shaft gear, a carrier rotatably installed around the fixed shaft and provided with a carrier gear on the outer periphery, a drive gear for transmitting a driving force to the carrier gear and rotating the carrier around the fixed shaft, and a drive gear And a drive source for driving. The carrier has a plurality of planetary shafts, and each of the plurality of planetary shafts rotatably supports a first planetary gear that meshes with a fixed shaft gear and a second planetary gear that meshes with a rudder shaft gear. Furthermore, the meshing pitch circle diameter of the rudder shaft gear meshed with the second planetary gear is different from the meshing pitch circle diameter of the fixed shaft gear meshed with the first planetary gear.

  According to the steering machine of the present invention, the driving force of the driving source is transmitted from the driving gear to the carrier gear, and the driving force is transmitted from the second planetary gear supported by the plurality of planetary shafts of the carrier to the rudder shaft gear. Is done. Thus, by setting it as the structure which transmits the driving force of a drive source to a steering shaft in two steps, each gear is reduced in size, As a result, a steering machine is reduced in size. Further, since the meshing pitch circle diameter of the rudder shaft gear meshed with the second planetary gear and the meshing pitch circle diameter of the fixed shaft gear meshed with the first planetary gear are different, the fixed shaft is adjusted in accordance with the rotation of the carrier around the fixed shaft. The rudder shaft rotates relative to the rotation. In this way, the drive source transmits the driving force to the rudder shaft via the two-stage gear, and the rudder shaft rotates relative to the fixed shaft, so the steering machine drives the rudder with a high reduction ratio. Can be provided.

  In the steering machine according to the first aspect of the present invention, modules of the rudder shaft gear, the fixed shaft gear, the first planetary gear, and the second planetary gear are equal, and the fixed shaft gear and the first planetary gear are the same. The total number of teeth of the gear is equal to the total number of teeth of the rudder shaft gear and the second planetary gear. By doing in this way, when using gears with the same module, the first planetary gear and the second planetary gear can be appropriately supported by the same planetary shaft.

  In the steering gear according to the second aspect of the present invention, the first planetary gear and the second planetary gear have the same number of teeth, and the first planetary gear and the second planetary gear have different shift amounts. And By doing in this way, the number of teeth of a fixed axis gear and a rudder axis gear can be varied, making the number of teeth of a 1st planetary gear and the 2nd planetary gear equal.

  In the steering machine according to the second aspect of the present invention, the first planetary gear and the second planetary gear may be integrally formed. By subjecting the integrally formed gear to a process in which the shift amount of the portion engaged with the fixed shaft gear and the portion engaged with the rudder shaft gear are made different, the gear can function as the first planetary gear and the second planetary gear.

  The steering machine according to the third aspect of the present invention includes a plurality of the driving sources, and each of the plurality of driving sources transmits a driving force to the carrier gear via the driving gear. . By doing so, the driving force transmitted to the carrier is enhanced, and even when a certain driving source fails, the driving force can be transmitted to the carrier using another driving source.

  The steering machine according to a fourth aspect of the present invention includes a bearing pad that is disposed between the rudder shaft gear and the fixed shaft gear and supports an axial load of the rudder shaft. By doing in this way, while the axial load of a rudder axle is supported appropriately, a steering machine can be reduced in size compared with the case where the axial load of a rudder axle is supported by other structures. it can.

  Moreover, the steering machine of the 5th aspect of this invention is arrange | positioned between the said rudder axis | shaft and the said fixed axis | shaft, and is provided with the journal bearing which supports the said rudder axis | shaft rotatably. By doing in this way, the steering machine which enabled it to support appropriately the load added to the radial direction orthogonal to the axial direction of a steering shaft can be provided.

  In the steering machine of the sixth aspect of the present invention, the drive source is installed on a seat on which the fixed shaft is installed. By doing in this way, a drive source can be installed in the base in which a fixed axis is installed, and the drive force of a drive source can be transmitted to a carrier appropriately.

  The steering machine according to a seventh aspect of the present invention includes a protective cover that protects the rudder shaft gear, the fixed shaft gear, and the carrier from the outside, and the drive source is installed above the protective cover. A drive shaft for driving the drive gear protrudes downward from the upper portion of the protective cover, and the carrier gear is disposed on the upper portion of the carrier and meshes with the drive gear driven by the drive shaft. It is characterized by that.

  In this way, the drive source is installed on the top of the protective cover that protects the carrier from the outside, so the length of the fixed shaft is shorter than when the drive source is installed on the seat on which the fixed shaft is installed. can do.

  In the steering machine according to the eighth aspect of the present invention, the carrier has a flange portion disposed above the rudder shaft gear, and is disposed between the rudder shaft gear and the flange portion, and the carrier. And a thrust bearing for supporting the load. By doing in this way, the load of a carrier can be appropriately supported with the thrust bearing arrange | positioned between the rudder axle gearwheel and the flange part.

  Moreover, the ship which concerns on this invention is equipped with the steering machine mentioned above, It is characterized by the above-mentioned.

  ADVANTAGE OF THE INVENTION According to this invention, the small steering gear which drives a rudder with a high reduction ratio, and a ship provided with the same can be provided.

It is a fragmentary longitudinal cross-sectional view of the steering machine of 1st Embodiment. It is an AA arrow cross-sectional view of the steering machine shown in FIG. It is a BB arrow cross-sectional view of the steering machine shown in FIG. It is the elements on larger scale of the rudder shaft gear of a 1st embodiment, and the 2nd planetary gear. It is the elements on larger scale of the fixed shaft gear of a 1st embodiment, and the 1st planetary gear. It is a fragmentary longitudinal cross-sectional view of the steering machine of 2nd Embodiment. It is a figure which shows the dislocation amount of a gearwheel, (a) shows a minus dislocation and (b) shows a plus dislocation. It is a partial longitudinal cross-sectional view of the steering machine of 3rd Embodiment. It is a fragmentary longitudinal cross-sectional view of the steering machine of 4th Embodiment. It is a partial longitudinal cross-sectional view of the steering machine of 5th Embodiment. It is a fragmentary longitudinal cross-sectional view of the steering machine of 6th Embodiment. It is a top view which shows the steering shaft gear of the steering machine of 7th Embodiment. It is a top view which shows the steering shaft gear of the steering machine of 8th Embodiment.

[First Embodiment]
Hereinafter, the steering machine 100 of 1st Embodiment is demonstrated using FIG. 1 and FIG. FIG. 1 is a partial vertical cross-sectional view of a steering machine 100 according to the first embodiment. Moreover, FIG. 2 is an AA arrow cross-sectional view of the steering machine 100 shown in FIG.

  As shown in FIG. 1, the steering machine 100 according to the present embodiment is a device that drives a rudder (not shown) of a ship via a rudder shaft 1 connected to the rudder. The steering machine 100 includes a rudder shaft 1, a rudder shaft gear 2, a fixed shaft 3, a fixed shaft gear 4, a carrier 5, and a drive device 6. Moreover, the ship which concerns on this embodiment obtains a propulsive force with the screw driven by an internal combustion engine (not shown), and propels it. And in the ship which concerns on this embodiment, the steering machine 100 is being fixed to the hull, By operating the rudder with the steering machine 100, the advancing direction of a ship can be controlled arbitrarily.

  The rudder shaft 1 is a cylindrical member disposed along the central axis C in the vertical direction, and a rudder is coupled to the lower end portion. A rudder shaft gear 2 is fixed to the upper end portion of the rudder shaft 1. The rudder shaft gear 2 is fastened to the rudder shaft 1 by, for example, a bolt or the like, and when the rudder shaft gear 2 rotates, the rudder shaft 1 fixed to the rudder shaft gear 2 also rotates. Therefore, as the rudder shaft gear 2 rotates, the rudder connected to the rudder shaft 1 rotates around the central axis C. The rudder shaft 1 is provided with a flange portion 1a having a diameter larger than that of the rudder shaft 1, and rotates integrally with the rudder shaft 1.

Next, the rudder shaft support mechanism 18 that supports the weight of the rudder shaft 1 will be described. The rudder shaft support mechanism 18 includes a rudder bearing 15, a support shaft 16, and a seat 17.
The support shaft 16 is a cylindrical member provided with the same axis as that of the rudder shaft 1, and a lower end portion thereof is fixed to a seat 17 on the hull side by a fastening member such as a bolt. A rudder bearing 15 that supports the load in the axial direction of the rudder shaft 1 is disposed between the upper surface of the support shaft 16 and the lower surface of the flange portion 1a. The rudder bearing 15 is fixed to the outer peripheral end portion of the upper surface of the support shaft 16, and is in contact with the lower surface of the flange portion 1a. The load of the rudder shaft 1 is transmitted to the support shaft 16 fixed to the seat on the hull side via the rudder bearing 15.

  The fixed shaft 3 is a cylindrical member provided with the same axis as the rudder shaft 1, and the lower end portion is fixed to a seat 7 on the hull side by a fastening member such as a bolt. A fixed shaft gear 4 is fixed to an upper end portion of the fixed shaft 3 by a fastening member such as a bolt. The inner diameter of the fixed shaft 3 is larger than the outer diameter of the rudder shaft 1.

  The inner surface of the inner ring of the carrier bearing 8 that supports the load of the carrier 5 is fitted to the outer surface of the fixed shaft 3 in a press-fit state. Further, the inner surface of the annular member 9 is fitted into the outer surface of the fixed shaft 3 in a press-fit state, and the annular member 9 is disposed below the carrier bearing 8. The lower end of the annular member 9 is supported by the seat 7, and the upper end of the annular member 9 is in contact with the lower surface of the inner ring of the carrier bearing 8.

  The outer surface of the outer ring of the carrier bearing 8 is fitted in a stepped portion 5 a provided on the carrier 5 in a press-fitted state. The carrier bearing 8 is a rolling bearing, and as described above, the inner surface of the inner ring is fitted into the outer surface of the fixed shaft 3 in a press-fit state. Therefore, the carrier 5 is rotatably installed around the fixed shaft 3.

  A load of the carrier 5 is applied to the upper surface of the outer ring of the carrier bearing 8 via a step portion 5a. The load of the carrier 5 applied to the upper surface of the outer ring of the carrier bearing 8 is transmitted to the annular member 9 via the lower surface of the inner ring of the carrier bearing 8. Thus, the carrier bearing 8 has a function of supporting the load of the carrier 5 and installing the carrier 5 around the fixed shaft 3 so as to be rotatable.

  The carrier 5 is a member having a circular cross-sectional shape in the direction of the central axis C, and is rotatably installed around the fixed shaft 3. The carrier 5 is provided with a carrier gear 5b on the outer circumferential surface on the radially outer side of the stepped portion 5a. The carrier gear 5 b is provided by processing the outer peripheral surface of the carrier 5.

  The carrier gear 5b meshes with a drive gear 6c connected to a drive source 6a via a drive shaft 6b. The drive source 6a is composed of an electric motor and a speed reducer, and rotates the drive gear 6c via the drive shaft 6b. The driving gear 6 c transmits driving force to the carrier gear 5 b and rotates the carrier 5 around the fixed shaft 3. The driving source 6a drives the driving gear 6c to transmit the driving force to the carrier gear 5b. The drive source 6a is installed on a seat 7 on which the fixed shaft 3 is installed.

  The carrier 5 has four planetary shafts 30a, 30b, 30c (not shown), 30d (not shown). Since FIG. 1 is a partial longitudinal sectional view of the steering gear 100, the planetary shaft 30a and the planetary shaft 30b are shown. The planetary shaft 30a is a shaft-like member whose upper end and lower end are fixed to the carrier 5, respectively. The planetary shaft 30a is provided with two rolling bearings (not shown) in which the inner ring is fitted in a press-fit state, and the planetary gear 10a and the planetary gear 20a are fitted in the outer ring of the two rolling bearings in a press-fit state. Yes. In this way, the planetary shaft 30a rotatably supports the planetary gear 10a (first planetary gear) that meshes with the fixed shaft gear 4 and the planetary gear 20a (second planetary gear) that meshes with the rudder shaft gear 2. .

  Similarly, the planetary shaft 30b rotatably supports the planetary gear 10b and the planetary gear 20b. Similarly, the planetary shaft 30c rotatably supports the planetary gear 10c (not shown) and the planetary gear 20c (not shown). Similarly, the planetary shaft 30d rotatably supports the planetary gear 10d (not shown) and the planetary gear 20d (not shown). The planetary gears 10 a to 10 d (first planetary gear) are engaged with the fixed shaft gear 4, and the planetary gears 20 a to 20 d (second planetary gear) are engaged with the rudder shaft gear 2.

  FIG. 2 is a cross-sectional view of the steering machine 100 shown in FIG. As shown in FIG. 2, the planetary gears 20 a to 20 d are arranged at four locations in the circumferential direction of the rudder shaft gear 2 so as to mesh with the rudder shaft gear 2 with an interval of 90 ° each. . The planetary gear 20 (generic name of the planetary gears 20a to 20d) rotates with respect to the fixed shaft 3 while maintaining the interval of 90 ° as the carrier 5 rotates around the fixed shaft 3.

  3 is a cross-sectional view of the steering machine 100 shown in FIG. As shown in FIG. 3, the planetary gears 10 a to 10 d are arranged at four locations in the circumferential direction of the fixed shaft gear 4 so as to mesh with the fixed shaft gear 4 with an interval of 90 °. . The planetary gear 10 (generic name of the planetary gears 10a to 10d) rotates with respect to the fixed shaft 3 while maintaining the interval of 90 ° as the carrier 5 rotates around the fixed shaft 3.

  Here, the speed ratio (reduction ratio) of the driving force transmitted from the drive gear 6c to the rudder shaft gear 2 in the present embodiment will be described. In the following description, it is assumed that the module of the fixed shaft gear 4 and the module of the planetary gear 10 are the same when the fixed shaft gear 4 meshes with the planetary gear 10. In addition, when the rudder shaft gear 2 meshes with the planetary gear 20, the module of the rudder shaft gear 2 and the module of the planetary gear 20 are the same. Here, the module means a value obtained by dividing the pitch circle diameter by the number of teeth.

The steering machine 100 according to the present embodiment satisfies the following conditional expression.
i ₀ = (Zb · Zd) / (Za · Zd) (1)
i ₁ = (1−i ₀ ) / i ₀ (2)
i ₂ = Zf / Ze (3)
i ₃ = i ₁ · i ₂ (4)
Za + Zb = Zc + Zd (5)
Za ≠ Zd (6)
Zb ≠ Zc (7)
Here, Za: the number of teeth of the fixed shaft gear 4, Zb: the number of teeth of the planetary gear 10, Zc: the number of teeth of the planetary gear 20, Zd: the number of teeth of the rudder shaft gear 2, Ze: the number of teeth of the drive gear 6c, Zf: number of teeth of carrier gear 5b, i ₁ : speed ratio (reduction ratio) of carrier 5 and rudder shaft 1, i ₂ : speed ratio (reduction ratio) of drive gear 6c and carrier 5, i ₃ : drive gear 6c This is the speed ratio (reduction ratio) of the rudder shaft 1.

As is clear from the above conditional expression, the reduction ratio between the drive gear 6c and the rudder shaft 1 is the number of teeth Za of the fixed shaft gear 4, the number of teeth Zb of the planetary gear 10, the number of teeth Zc of the planetary gear 20, the rudder shaft gear. 2 is determined by the number of teeth Zd, the number of teeth Ze of the drive gear 6c, and the number of teeth Zf of the carrier gear 5b.
Note that the number of teeth of the planetary gear 10 is the same, and Zb is the same number of teeth. The number of teeth of the planetary gear 20 is the same, and Zc is the same number of teeth.

  Conditional expression (5) indicates that the rudder shaft 1 and the fixed shaft 3 are provided with the same axis, and the planetary gear 10 and the planetary gear 20 are supported by the planetary shaft 30 (generic name of the planetary shafts 30a to 30d). This is a possible condition. By satisfying such a condition, the distance between the rudder shaft 1 and the planetary shaft 30 and the distance between the fixed shaft 3 and the planetary shaft 30 can be made equal.

  Conditional expressions (6) and (7) are conditions for rotating the rudder shaft 1 relative to the fixed shaft 3 as the carrier 5 rotates around the fixed shaft 3. When both conditional expressions (6) and (7) are not satisfied, the number of teeth Za of the fixed shaft gear 4 and the number of teeth Zd of the rudder shaft gear 2 are equal, and the number of teeth Zb of the planetary gear 10 and the number of teeth of the planetary gear 20 The numbers Zc are equal. In this case, the planetary gear 20 rotates in the circumferential direction around the rudder shaft gear 2, but the rudder shaft gear 2 does not rotate relative to the fixed shaft gear 4 and remains stationary. By satisfying conditional expressions (6) and (7), the rudder shaft 1 can be rotated relative to the fixed shaft 3 as the carrier 5 rotates about the fixed shaft 3.

  In the above description, the module of the fixed shaft gear 4 and the module of the planetary gear 10 when the fixed shaft gear 4 meshes with the planetary gear 10 have been described as being the same. In the above description, the rudder shaft gear 2 module and the planetary gear 20 module are the same when the rudder shaft gear 2 meshes with the planetary gear 20. However, the present embodiment is applicable even when these modules are different. The steering machine 100 in this case satisfies the following conditional expressions (8) to (10) instead of the conditional expressions (5) to (7) described above.

r ₁ + r ₂ = r ₄ + r ₅ (8)
r ₁ ≠ r ₃ (9)
r ₂ ≠ r ₄ (10)
Here, as shown in FIGS. 4 and 5, r ₁ : distance from the center O ₁ of the rudder shaft gear 2 to the meshing point P ₁ , r ₂ : meshing from the center O _{2 of the} planetary gear 20 (planetary gear 20 a). the distance between the point _{P 1, r 3:} center _{O 3} from the engagement point _{P 2} distance of the fixed shaft gear 4, _{r 4:} the distance from the center _{O 4} of the meshing point _{P 2} of the planetary gear 10 (planetary gear 10a).

2r ₁ is twice the distance of r ₁ is the pitch circle diameter engagement of the steering shaft gear 2, is 2r ₃ is twice the distance of r ₃ is a working pitch circle diameter of the fixed shaft gear 4. Also, a working pitch circle diameter of 2r ₂ planetary gear 20 is twice the distance of r _2, 2r ₄ is twice the distance of r ₄ is working pitch circle diameter of the planetary gear 10.

  Conditional expression (8) is a condition that allows the rudder shaft 1 and the fixed shaft 3 to be provided with the same axis and allow the planetary gear 10 and the planetary gear 20 to be supported by the planetary shaft 30. By satisfying such a condition, the distance between the rudder shaft 1 and the planetary shaft 30 and the distance between the fixed shaft 3 and the planetary shaft 30 can be made equal.

Condition (9), the pitch diameter 2r ₁ meshing rudder shaft gear 2 the planetary gear 20 is engaged, in conditional expression indicating that the pitch circle diameter 2r ₃ engagement of the fixed shaft gear 4 of the planetary gear 10 is engaged are different is there. The conditional expression (10) shows a pitch diameter 2r ₂ meshing planetary gear 20 which is the steering shaft gear 2 meshes, and a working pitch circle diameter 2r ₄ of the planetary gear 10 which is fixed shaft gear 4 meshing vary conditions It is a formula.

Conditional expressions (9) and (10) are conditions for rotating the rudder shaft 1 relative to the fixed shaft 3 as the carrier 5 rotates around the fixed shaft 3. If the conditional expression (9) and (10) are not both satisfied, the steering shaft gear 2 of the center _{O 1} distance from the engagement point _{P 1 r 1} and a distance _{r 3} of the center _{O 3} from engagement point _{P 2} of the fixed shaft gear 4 It is equal to the distance from the center _{O 2} of the engagement point _{P 1} of the planetary gear 20 _{r 2} and the planetary gears 10a distance _{r 4} from the center _{O 4} of the meshing point _{P 2} of the same. In this case, the planetary gear 20 rotates in the circumferential direction around the rudder shaft gear 2, but the rudder shaft gear 2 does not rotate relative to the fixed shaft gear 4 and remains stationary. By satisfying conditional expressions (9) and (10), the rudder shaft 1 can be rotated relative to the fixed shaft 3 as the carrier 5 rotates about the fixed shaft 3.

Thus, according to the steering gear 100 according to the present embodiment, the driving force from the driving source 6a is transmitted from the driving gear 6c to the carrier gear 5b, and the planetary gear 20 supported by the plurality of planetary shafts 30 of the carrier 5 is used. The driving force is further transmitted to the rudder shaft gear 2. Thus, by setting it as the structure which transmits the driving force of the drive source 6a to the rudder shaft 1 in two steps, each gear is reduced in size, As a result, the steering gear 100 is reduced in size. Further, since the meshing pitch circle diameter 2r _{1 of the} rudder shaft gear 2 meshed with the planetary gear 20 and the meshing pitch circle diameter 2r _{3 of the} fixed shaft gear 4 meshed with the planetary gear 10 are different, the carrier 5 rotates around the fixed shaft 3. Accordingly, the rudder shaft 1 rotates relative to the fixed shaft 3. In this way, the drive source 6a transmits the driving force to the rudder shaft 1 via the two-stage gears, and the rudder shaft 1 rotates relative to the fixed shaft 3, so the rudder is driven with a high reduction ratio. A steering machine 100 can be provided.

  Further, in the steering machine 100 of the present embodiment, the modules of the rudder shaft gear 2, the fixed shaft gear 4, the planetary gear 10, and the planetary gear 20 are equal, and the total number of teeth of the fixed shaft gear 4 and the planetary gear 10 is the same. It is equal to the total number of teeth of the rudder shaft gear 2 and the planetary gear 20. By doing so, the planetary gear 10 and the planetary gear 20 can be appropriately supported by the same planetary shaft 30 when using gears having the same module.

  The steering machine 100 according to the present embodiment includes a bearing pad 40 that is disposed between the rudder shaft gear 2 and the fixed shaft gear 4 and supports a load in the axial direction of the rudder shaft 1. In this way, the load in the axial direction of the rudder shaft 1 is appropriately supported, and the steering gear 100 is downsized as compared with the case where the load in the axial direction of the rudder shaft 1 is supported by another structure. can do.

  In the steering machine 100 of the present embodiment, the drive source 6a is installed on the seat 7 on which the fixed shaft 3 is installed. By doing in this way, the drive source 6a can be installed in the base 7 in which the fixed shaft 3 is installed, and the drive force of the drive source 6a can be appropriately transmitted to the carrier 5.

[Second Embodiment]
Next, the steering machine 200 of 2nd Embodiment is demonstrated using FIG. FIG. 6 is a partial longitudinal sectional view of the steering machine 200 according to the second embodiment.
In the first embodiment, the planetary gear 10 and the planetary gear 20 are independent gears. On the other hand, in the second embodiment, a single planetary gear integrally formed on the planetary shaft 30 is arranged, and the shift amount of the gear in the axial direction of the planetary gear is varied.
The second embodiment is a modification of the first embodiment. Except for the case specifically described below, the other configurations are the same as those of the first embodiment, and thus the description thereof will be omitted. Further, FIG. 6 does not show the rudder shaft support mechanism 18 of the first embodiment, but it is assumed that the same rudder shaft support mechanism 18 as that of the first embodiment is provided.

As shown in FIG. 6, the planetary gears 11a and 11b supported by the planetary shafts 30a and 30b are a single member formed integrally and a gear having a fixed number of teeth. On the other hand, the rudder shaft gear 2 and the fixed shaft gear 4 have different numbers of teeth as in the first embodiment.
Since the number of teeth of the rudder shaft gear 2 and the fixed shaft gear 4 having the same axis is different, the planet gears 11a, 11b arranged on the planet shafts 30a, 30b are the standard gears with which the gears mesh with each other. Will not be established. Therefore, in this embodiment, planetary gears 11a and 11b in which the shift amount at the position where the rudder shaft gear 2 meshes with the shift amount at the position where the rudder shaft gear 4 meshes are different when forming.

  Here, the amount of dislocation will be described with reference to FIG. Displacement refers to changing the tooth thickness and tooth profile of a gear rather than a standard gear. The minus shift shown in FIG. 7 (a) means that the tooth thickness of the gear is made thinner than that of the standard gear, and the tooth surface is retracted toward the center of the gear. Further, the plus shift shown in FIG. 7B means that the tooth thickness of the gear is made thicker than that of the standard gear, and the tooth surface is advanced in a direction away from the center direction of the gear.

  For example, when the number of teeth of the fixed shaft gear 4 is larger than the number of teeth of the rudder shaft gear 2, the planetary gears 11a and 11b in positions engaged with the rudder shaft gear 2 are positively shifted planetary gears (second planetary gears). The planetary gears 11a and 11b that are in mesh with the fixed shaft gear 4 are planetary gears (first planetary gears) that have been negatively shifted. In this case, the number of teeth of the planetary gears 11a and 11b at the minus-shifted position and the planetary gears 11a and 11b at the plus-shifted position are equal, and the planetary gears 11a and 11b at the minus-shifted position are the positions of the plus-shifted positions. The shift amounts of the planetary gears 11a and 11b with respect to the standard gears are different.

In this way, positive dislocations position of the planetary gear 11a, 11b (second planetary gear) meshing pitch circle rudder shaft gear 2 which is engaged in diameter 2r ₁ and the planetary gear 11a of the negative dislocation position, 11b (the since the first planetary gear) pitch circle diameter 2r ₃ engagement of the fixed shaft gear 4 meshing different, relatively rotating the steering shaft 1 with respect to the fixed shaft 3 in response to the carrier 5 is rotated about the fixed shaft 3 To do.

In the above description, the planetary gears 11a and 11b that are in mesh with the rudder shaft gear 2 are positively shifted planetary gears (second planetary gears), and the planetary gears 11a and 11b that are in mesh with the fixed shaft gear 4 are negatively shifted. Although the above-described planetary gear (first planetary gear) is used, other modes may be used.
For example, if the conditional expressions (8) to (10) of the first embodiment are satisfied, the planetary gears 11a and 11b having various shift amounts are adopted according to the shapes of the rudder shaft gear 2 and the fixed shaft gear 4. You may do it. The amount of dislocation is not limited to one in which one is a plus dislocation and the other is a minus dislocation, and both may be a plus or minus dislocation. When both are shifted to the positive shift or the negative shift, the shift amounts of the planetary gears 11a, 11b at the position engaging with the rudder shaft gear 2 and the planetary gears 11a, 11b at the position engaging with the fixed shaft gear 4 may be made different. .

Thus, according to the steering gear 200 according to the present embodiment, there are portions (first planetary gear and second planetary gear) having the same number of teeth of the planetary gear and different shift amounts in the planetary gear. By doing in this way, the number of teeth of a fixed shaft gear and a rudder shaft gear can be varied, equalizing the number of teeth of a planetary gear provided with a part from which the amount of shift is different.
Further, by using the planetary gear disposed on the planetary shaft 30 as a single member, the height in the axial direction can be kept low, and the steering machine 200 can be downsized. Further, in the second embodiment, unlike the first embodiment, the carrier gear 5b is provided on the outer peripheral surface of the carrier 5, so that the axial direction of the drive source is set lower than that in the first embodiment in which the drive source is installed below the carrier 5. The height of the steering machine 200 can be reduced while keeping the height low.

[Third Embodiment]
Next, the steering machine 300 of 3rd Embodiment is demonstrated using FIG. FIG. 8 is a partial longitudinal sectional view of the steering gear 300 of the third embodiment.
In the first embodiment, a single driving device is provided as a driving device that transmits a driving force to the carrier gear 5b. On the other hand, in the second embodiment, a plurality of drive devices are provided as drive devices that transmit drive force to the carrier gear 5b.
The third embodiment is a modification of the first embodiment. Except for the case specifically described below, the other configurations are the same as those of the first embodiment, and thus the description thereof will be omitted.

  As shown in FIG. 8, the carrier gear 5b is engaged with a drive gear 6c connected to the drive source 6a via the drive shaft 6b. The drive source 6a is composed of an electric motor and a speed reducer, and rotates the drive gear 6c via the drive shaft 6b. The driving gear 6 c transmits driving force to the carrier gear 5 b and rotates the carrier 5 around the fixed shaft 3. The driving source 6a drives the driving gear 6c to transmit the driving force to the carrier gear 5b. The drive source 6a is installed on a seat 7 on which the fixed shaft 3 is installed.

  Similarly, the carrier gear 5b is engaged with a drive gear 60c connected to the drive source 60a via the drive shaft 60b. The drive source 60a is composed of an electric motor and a speed reducer, and rotates the drive gear 60c via the drive shaft 60b. The driving gear 60c transmits driving force to the carrier gear 5b and rotates the carrier 5 around the fixed shaft 3. The driving source 60a drives the driving gear 60c to transmit the driving force to the carrier gear 5b. The drive source 60a is installed on the seat 7 on which the fixed shaft 3 is installed.

  Thus, the steering machine 300 according to the present embodiment includes a plurality of drive sources, and each of the plurality of drive sources 6a and 60a transmits the drive force to the carrier gear 5b via the drive gears 6c and 60c. By doing so, the driving force transmitted to the carrier 5 is enhanced, and even when a certain driving source fails, the driving force can be transmitted to the carrier 5 by another driving source.

[Fourth Embodiment]
Next, the steering machine 400 of 4th Embodiment is demonstrated using FIG. FIG. 9 is a partial longitudinal sectional view of the steering gear 400 of the fourth embodiment.
The steering machine 300 according to the third embodiment includes the rudder shaft support mechanism 18 that supports the weight of the rudder shaft 1. On the other hand, the steering machine 400 of 4th Embodiment is provided with the bearing pad 40 for supporting the dead weight of the rudder axle 1. FIG.
The fourth embodiment is a modification of the third embodiment. Except for the case specifically described below, the other configurations are the same as those of the third embodiment, and thus the description thereof will be omitted.

  The steering machine 400 of the fourth embodiment does not include the rudder shaft support mechanism 18 of the third embodiment for supporting the weight of the rudder shaft 1. Instead, a bearing pad 40 for supporting the weight of the rudder shaft 1 is provided. The bearing pad 40 supports the load in the axial direction of the rudder shaft 1 and is disposed between the rudder shaft gear 2 and the fixed shaft gear 4. The bearing pad 40 is fixed to the upper surface of the outer peripheral end portion of the fixed shaft gear 4 and is in contact with the lower surface of the outer peripheral end portion of the rudder shaft gear 2.

  Thus, the steering gear 400 of the fourth embodiment is provided with the rudder shaft support mechanism 18 as in the third embodiment by disposing the bearing pad 40 between the rudder shaft gear 2 and the fixed shaft gear 4. Even without it, the weight of the rudder shaft 1 can be supported appropriately.

[Fifth Embodiment]
Next, the steering machine 500 of 5th Embodiment is demonstrated using FIG. FIG. 10 is a partial longitudinal sectional view of a steering machine 500 according to the fifth embodiment.
The fifth embodiment is a modification of the fourth embodiment, and is different in that a journal bearing 50 that rotatably supports the rudder shaft 1 is provided between the rudder shaft 1 and the fixed shaft 3.
By providing the journal bearing 50, it is possible to appropriately support a load applied in a radial direction orthogonal to the axial direction of the rudder shaft 1.

[Sixth Embodiment]
Next, the steering machine 600 of 6th Embodiment is demonstrated using FIG. FIG. 11 is a partial longitudinal sectional view of a steering gear 600 according to the sixth embodiment.
In the third embodiment, a plurality of driving sources are installed on a seat and the carrier gear is driven. On the other hand, in the sixth embodiment, a protective cover for protecting the carrier 5 from the outside is provided, and a plurality of drive sources are installed on the upper portion of the protective cover.
The sixth embodiment is a modification of the third embodiment, and the other configurations are the same as those of the third embodiment and the first embodiment unless otherwise described below. Is omitted.

  As shown in FIG. 11, the steering gear 600 of the sixth embodiment includes a protective cover 70 that protects the carrier 5 from the outside. The drive device 6 including the drive source 6 a is installed on the upper portion of the protective cover 70, and a drive shaft 6 b that drives the drive gear 6 c protrudes downward from the upper portion of the protective cover 70. Similarly, the drive device 60 including the drive source 60a is installed on the upper part of the protective cover 70, and a drive shaft 60b for driving the drive gear 60c projects downward from the upper part of the protective cover 70. In the carrier 5 of the present embodiment, the carrier gear 5b is disposed on the top of the carrier 5 and meshes with the drive gears 6c and 60c driven by the drive shafts 6b and 60b.

  Thus, the steering gear 600 according to the present embodiment includes the protective cover 70 that protects the rudder shaft gear 2, the fixed shaft gear 4, and the carrier 5 from the outside, and the drive source is installed on the upper portion of the protective cover 70. At the same time, a drive shaft for driving the drive gear protrudes downward from the upper portion of the protective cover 70, the carrier gear 5b is disposed on the upper portion of the carrier 5, and the drive gear 6c driven by the drive shafts 6b and 60b. , 60c.

  In this way, since the drive sources 6a and 60a are installed on the protective cover 70 that protects the carrier 5 from the outside, the drive sources 6a and 60a are installed on the seat 7 on which the fixed shaft 3 is installed. As compared with the above, the length of the fixed shaft 3 can be shortened.

[Seventh Embodiment]
Next, the steering machine 700 of 7th Embodiment is demonstrated using FIG. FIG. 12 is a partial longitudinal sectional view of a steering machine 700 according to the seventh embodiment.
7th Embodiment is a modification of 6th Embodiment, the flange part 5c is provided in the upper part of the carrier 5, and the thrust bearing 80 is arrange | positioned between the rudder shaft gear 2 and the flange part 5c. Is different.
The seventh embodiment is a modification of the sixth embodiment. Except for the case specifically described below, the other configurations are the same as those of the sixth embodiment and the first embodiment. Is omitted.

  As shown in FIG. 12, in the steering machine 700 of the seventh embodiment, the flange portion 5 c included in the carrier 5 is disposed above the rudder shaft gear 2. The steering gear 700 includes a thrust bearing 80 that is disposed between the rudder shaft gear 2 and the flange portion 5 c and supports the load of the carrier 5. By doing in this way, the load of the carrier 5 can be appropriately supported by the thrust bearing 80 disposed between the rudder shaft gear 2 and the flange portion 5c.

[Eighth Embodiment]
Next, the steering shaft gear of the steering machine according to the eighth embodiment will be described with reference to FIG.
The eighth embodiment is a modification of the first embodiment, and is characterized in that the rudder shaft gear is provided with a safety mechanism when an external force is applied to the rudder.
As shown in FIG. 13, the rudder shaft gear 2 of the eighth embodiment includes a rudder shaft gear portion 2 a provided radially outward from the central axis C and a disc-shaped rudder shaft connection provided radially inward. It is comprised by the some connecting pin 2c which connects the part 2b, the rudder shaft gear part 2a, and the rudder shaft connection part 2b.

  The rudder shaft connecting portion 2b is a member connected to the rudder shaft 1, and when an external force is applied to the rudder connected to the rudder shaft 1, such as when it collides with the seabed or a reef, the external force is transmitted via the rudder shaft 1. Is a member to which is transmitted. When an external force is transmitted to the rudder shaft connecting portion 2b, a plurality of connecting pins 2c that connect the rudder shaft gear portion 2a and the rudder shaft connecting portion 2b remain connected if the external force is within a predetermined allowable range. It becomes. On the other hand, when an external force exceeding a predetermined allowable range is applied to the rudder, the plurality of connecting pins 2c are broken, and the connection between the rudder shaft gear portion 2a and the rudder shaft connecting portion 2b is broken. By doing in this way, when the external force exceeding a predetermined allowable range is applied to the rudder, the rudder shaft gear 2 is damaged, but the other parts of the steering gear are not damaged. it can. That is, when an external force exceeding a predetermined allowable range is applied to the rudder, it is possible to prevent the entire steering machine from being damaged by an impact caused by the external force.

  In addition, the radius of the rudder shaft connection part 2b shall be longer than the radius L of the inner periphery of the fixed shaft gear. By doing in this way, even if it is a case where connection with the rudder shaft gear part 2a and the rudder shaft connection part 2b is cut | disconnected, since the rudder shaft connection part 2b remains on the upper part of the fixed shaft gear 4, It is possible to prevent 1 from falling downward.

[Other Embodiments]
In the embodiment described above, the drive source may be an electric motor, and a sensor for detecting the rotation speed of the electric motor may be provided. In this case, a control unit to which the detection value of the sensor is input is further provided, and the steering angle is controlled based on the detection value of the sensor to which the control unit is input. By doing in this way, control of a steering angle can be performed accurately.
Further, as shown in the fifth and sixth embodiments, when a protective cover for protecting the carrier is provided on the steering machine, the protective cover may be filled with lubricating oil. In this case, as the lubricating oil, various methods such as a method of applying grease to the gear, a method of immersing the entire gear, a method of supplying oil directly from an oil pump or the like can be adopted.
In an embodiment in which no protective cover is provided, it is desirable to provide a lever outside the carrier 5 so that the operator can operate the rudder by his / her own operation in the event of a drive source failure or the like. By doing so, the rudder can be operated even if there is a failure of the drive source.
In addition, when an external force within a predetermined allowable range is applied to the rudder, the strength of those portions is set so that the drive shaft included in the drive device or the connection portion between the drive shaft and the drive gear is broken. Also good. By doing in this way, when the external force of the predetermined permissible range is added to the rudder, it can prevent appropriately that a drive source and the speed reducer with which a drive source is provided are damaged.

DESCRIPTION OF SYMBOLS 1 Rudder shaft 1a Flange part 2 Rudder shaft gear 3 Fixed shaft 4 Fixed shaft gear 5 Carrier 5b Carrier gears 6, 60 Drive device 6a, 60a Drive source 6b, 60b Drive shaft 6c, 60c Drive gear 7 Seat 10a, 10b, 10c , 10d Planetary gear (first planetary gear)
15 Rudder bearing 16 Support shaft 17 Seat 18 Rudder shaft support mechanisms 20a, 20b, 20c, 20d Planetary gear (second planetary gear)
30a, 30b, 30c, 30d Planetary shaft 40 Bearing pad 50 Journal bearing 70 Protective cover 80 Thrust bearing 100, 200, 300, 400, 500, 600, 700 Steering machine

Claims (11)

A steering machine for driving a rudder of a ship via a rudder shaft connected to the rudder,
A rudder axle gear fixed to the end of the rudder axle;
A fixed shaft gear fixed to the end of a fixed shaft provided with the same axis as the rudder shaft and fixed to the hull side;
A carrier rotatably installed around the fixed shaft and having a carrier gear on its outer periphery;
A driving gear for transmitting a driving force to the carrier gear and rotating the carrier around the fixed shaft;
A drive source for driving the drive gear,
The carrier has a plurality of planetary axes;
Each of the plurality of planetary shafts rotatably supports a first planetary gear meshing with the fixed shaft gear and a second planetary gear meshing with the rudder shaft gear,
A steering gear characterized in that the meshing pitch circle diameter of the rudder shaft gear meshed with the second planetary gear is different from the meshing pitch circle diameter of the fixed shaft gear meshed with the first planetary gear. The rudder shaft gear, the fixed shaft gear, the first planetary gear, and the second planetary gear module are equal,
The steering gear according to claim 1, wherein the total number of teeth of the fixed shaft gear and the first planetary gear is equal to the total number of teeth of the rudder shaft gear and the second planetary gear. The number of teeth of the first planetary gear and the second planetary gear are equal,
The steering gear according to claim 1 or 2, wherein a shift amount of the first planetary gear is different from that of the second planetary gear.   The steering gear according to claim 3, wherein the first planetary gear and the second planetary gear are integrally formed. A plurality of the drive sources;
The steering machine according to any one of claims 1 to 4, wherein each of the plurality of driving sources transmits a driving force to the carrier gear via the driving gear.   The steering according to any one of claims 1 to 5, further comprising a bearing pad that is disposed between the rudder shaft gear and the fixed shaft gear and supports an axial load of the rudder shaft. Machine.   The steering machine according to any one of claims 1 to 6, further comprising a journal bearing that is disposed between the rudder shaft and the fixed shaft and rotatably supports the rudder shaft.   The steering machine according to any one of claims 1 to 7, wherein the drive source is installed on a seat on which the fixed shaft is installed. The rudder shaft gear, the fixed shaft gear, and a protective cover for protecting the carrier from the outside,
The drive source is installed on the upper part of the protective cover, and a drive shaft for driving the drive gear protrudes downward from the upper part of the protective cover,
The steering gear according to any one of claims 1 to 7, wherein the carrier gear is disposed on an upper portion of the carrier and meshes with the drive gear driven by the drive shaft. The carrier has a flange portion disposed above the rudder axle gear;
The steering machine according to claim 9, further comprising a thrust bearing disposed between the rudder shaft gear and the flange portion and supporting a load of the carrier.   A ship comprising the steering machine according to any one of claims 1 to 10.

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