Patent Application
20120094558
1. Field of the Invention
The present invention relates to a marine vessel propulsion apparatus.
2. Description of the Related Art
A conventional marine vessel propulsion apparatus is described in, for example, U.S. Pat. No. 6,402,577. This marine vessel propulsion apparatus includes a transom bracket, a steering shaft, an outboard motor, a tilt mechanism, and a steering mechanism.
The transom bracket attachable to the transom of a hull is joined to the steering shaft. The steering shaft is turnable around a steering axis extending in the up-down direction with respect to the transom bracket. The outboard motor joined to the steering shaft is turnable around a tilt axis extending in the horizontal direction with respect to the steering shaft. The outboard motor and the steering shaft are turnable around the steering axis with respect to the transom bracket.
The tilt mechanism turns the outboard motor around the tilt axis with respect to the steering shaft. The steering mechanism turns the outboard motor and the steering shaft around the steering axis with respect to the transom bracket. The steering mechanism described in U.S. Pat. No. 6,402,577 is a hydraulic steering mechanism including a hydraulic pump. By driving the hydraulic pump, a hydraulic pressure is generated and this hydraulic pressure turns the outboard motor around the steering axis.
The steering mechanism described in U.S. Pat. No. 6,402,577 includes a steering arm and a steering actuator. The steering actuator includes a housing (a first portion of the steering actuator) and a rod (a second portion of the steering actuator). The housing and the rod extend in the right-left direction. The rod is disposed inside the housing. The housing has two cavities (hollows) disposed on the lateral sides of the right end portion and the left end portion of the rod. Hydraulic oil is supplied to these two cavities. The cavities are filled with the hydraulic oil. When a difference in hydraulic pressure is caused between the two cavities, the rod moves in the right-left direction inside the housing.
The rod is attached to the steering arm. The steering arm is attached to the outboard motor. When a difference in hydraulic pressure is caused between the two cavities and the rod moves in the right-left direction, the steering arm turns around the steering axis at a turning angle corresponding to a movement distance of the rod. When the steering arm further turns around the steering axis, the outboard motor turns around the steering axis together with the steering arm. Therefore, when the rod moves in the right-left direction, the outboard motor turns around the steering axis at a turning angle corresponding to the movement distance of the rod.
The inventors of preferred embodiments of the present invention described and claimed in the present application conducted an extensive study and research regarding a marine vessel propulsion apparatus, such as the one described above, and in doing so, discovered and first recognized new unique challenges and previously unrecognized possibilities for improvements as described in greater detail below.
In a hydraulic steering mechanism, a hydraulic pump is driven in response to a steering command to turn the outboard motor around the steering axis. Therefore, in order to maintain excellent responsiveness, the hydraulic pump must be driven even when the outboard motor is not turned around the steering axis. However, when the hydraulic pump is driven even in the case where the steering mechanism is not used, energy loss increases. A power source (electric motor) to drive the hydraulic pump uses power generated by an engine, and as a result, this also influences fuel consumption.
Further, in the steering mechanism described in U.S. Pat. No. 6,402,577, two cavities are disposed on the left and right of the rod, so that the width (length in the right-left direction) of the steering mechanism is wide. Moreover, the outboard motor turns around the steering axis at a turning angle corresponding to the movement distance of the rod, so that in order to increase the maximum turning angle of the outboard motor around the steering axis, it is necessary to increase the maximum movement distance of the rod by increasing the width of the housing that houses the rod. Therefore, if the maximum turning angle of the outboard motor around the steering axis is increased, the width of the steering mechanism further increases.
In order to overcome the previously unrecognized and unsolved challenges described above, a preferred embodiment of the present invention provides a marine vessel propulsion apparatus including a transom bracket, a steering shaft, an outboard motor, a tilt mechanism, and a steering mechanism. The transom bracket is arranged to be attachable to a transom of a hull. The steering shaft is joined to the transom bracket, and arranged to turn around the steering axis extending in an up-down direction. The outboard motor is joined to the steering shaft. The outboard motor is arranged to turn around the tilt axis extending along a plane that is perpendicular or substantially perpendicular to the steering axis. Further, the outboard motor is arranged to turn around the steering axis together with the steering shaft. The tilt mechanism is joined to the steering shaft and the outboard motor, and arranged to turn the outboard motor around the tilt axis with respect to the steering shaft. The steering mechanism includes an electric motor and a power conversion mechanism. The power conversion mechanism is arranged to convert power of the electric motor turning of the steering shaft around the steering axis.
With this arrangement of the present preferred embodiment of the present invention, the steering mechanism includes an electric motor and a power conversion mechanism. Specifically, the steering mechanism is an electric steering mechanism including an electric motor. The electric motor is driven by electric power. Power of the electric motor is converted into turning of the steering shaft around the steering axis by the power conversion mechanism. The outboard motor and the steering shaft are turnable around the steering axis with respect to the transom bracket . Therefore, by converting the power of the electric motor into turning of the steering shaft around the steering axis, the outboard motor turns around the steering axis with respect to the transom bracket. Accordingly, the marine vessel is steered.
In the electric steering mechanism, the time lag between a steering command to turn the outboard motor around the steering axis and turning of the outboard motor is smaller than that in a hydraulic steering mechanism. Therefore, when the outboard motor is not turned around the steering axis, it is not necessary to drive the electric motor. Therefore, as compared with a marine vessel propulsion apparatus including a hydraulic steering mechanism, energy loss can be reduced. The electric steering mechanism can control the stop position of the outboard motor and the turning angle of the outboard motor with accuracy higher than that of the hydraulic steering mechanism. Further, the electric steering mechanism does not need a hydraulic pump and a tank, etc., so that as compared with a marine vessel propulsion apparatus including a hydraulic steering mechanism, the steering mechanism can be decreased in size.
The transom bracket includes a tubular housing portion extending along the steering axis, and at least a portion of the steering shaft may be housed in the housing portion. In this case, the steering shaft is reliably held by the transom bracket.
The steering mechanism may include a reduction gear mechanism arranged to decelerate rotation of the electric motor and transmit the decelerated rotation to the power conversion mechanism. In this case, by decelerating the rotation of the electric motor by the reduction gear mechanism, the power of the electric motor is amplified. Accordingly, the steering mechanism does not require a large-sized electric motor that outputs high power. Accordingly, the marine vessel propulsion apparatus can be decreased in size.
The electric motor may be arranged so as not to turn around the steering axis with respect to the transom bracket according to turning of the outboard motor around the steering axis, and the electric motor may be arranged so as not to turn around the tilt axis with respect to the transom bracket according to turning of the outboard motor around the tilt axis.
Further, the electric motor may be arranged to change a position of the electric motor with respect to the outboard motor according to turning of the outboard motor around the steering axis, and may be arranged to change the position of the electric motor with respect to the outboard motor according to turning of the outboard motor around the tilt axis.
The electric motor may be fixed to the transom bracket. In detail, the electric motor may be fixed to the transom bracket via an intermediate member, or may be directly fixed to the transom bracket.
The power conversion mechanism may include a first conversion mechanism arranged to convert rotation of the electric motor into linear motion, and a second conversion mechanism arranged to convert the linear motion into turning of the steering shaft around the steering axis with respect to the transom bracket.
The first conversion mechanism may include a first ball screw joined to the transom bracket and the electric motor, the first ball screw driven to rotate by the electric motor, and a first ball nut attached to the first ball screw. In this case, the second conversion mechanism may include a first rack joined to the first ball nut, and a first pinion engaged with the first rack, the first pinion joined to the steering shaft so as to turn around the steering axis together with the steering shaft. The rotation of the electric motor is converted into linear motion of the first ball nut with respect to the first ball screw by the first ball screw and the first ball nut, and the linear motion of the first ball nut is converted into turning of the steering shaft by the first rack and the first pinion.
The first conversion mechanism may include a first ball screw joined to the transom bracket and the electric motor the first ball screw driven to rotate by the electric motor, and a first ball nut attached to the first ball screw. In this case, the second conversion mechanism may include a first pin joined to the first ball nut and a first arm joined to the first pin and the steering shaft, and the first conversion mechanism may be arranged to convert linear motion of the first ball nut with respect to the first ball screw into turning of the steering shaft by the first pin and the first arm. The rotation of the electric motor is converted into linear motion of the first ball nut with respect to the first ball screw by the first ball screw and the first ball nut, and the linear motion of the first ball nut is converted into turning of the steering shaft by the first pin and the first arm.
The power conversion mechanism may include a first drive gear joined to the transom bracket and the electric motor, the first drive gear being driven to rotate by the electric motor, and a first driven gear engaged with the first drive gear, the first driven gear being joined to the steering shaft so as to turn around the steering axis together with the steering shaft.
The first drive gear may be arranged to be driven to rotate by the electric motor around a first non-crossing axis that is parallel or substantially parallel to the steering axis and does not cross the steering axis, and the first driven gear may have a first central axis positioned on the steering axis and may be arranged to turn around the first central axis.
The first drive gear may be arranged to be driven to rotate by the electric motor around a first crossing axis crossing the steering axis, and the first driven gear may have a first central axis positioned on the steering axis, and may be arranged to turn around the first central axis.
The electric motor may be arranged to turn around the steering axis with respect to the transom bracket according to turning of the outboard motor around the steering axis, and the electric motor may be arranged so as not to turn around the tilt axis with respect to the transom bracket according to turning of the outboard motor around the tilt axis.
The electric motor may be arranged so as not to change a position of the electric motor with respect to the outboard motor according to turning of the outboard motor around the steering axis, and arranged to change the position of the electric motor with respect to the outboard motor according to turning of the outboard motor around the tilt axis.
The electric motor may be fixed to the steering shaft. In detail, the electric motor may be fixed to the steering shaft via an intermediate member, or may be directly fixed to the steering shaft.
The first conversion mechanism may include a second ball screw joined to the steering shaft and the electric motor, the second ball screw driven to rotate by the electric motor, and a second ball nut attached to the second ball screw. In this case, the second conversion mechanism may include a second rack joined to the second ball nut, and a second pinion engaged with the second rack, the second pinion joined to the transom bracket, and the first conversion mechanism may be arranged to convert linear motion of the second ball screw with respect to the second ball nut into turning of the steering shaft by the second rack and the second pinion. The rotation of the electric motor is converted into linear motion of the second ball screw with respect to the second ball nut by the second ball screw and the second ball nut, and the linear motion of the second ball screw is converted into turning of the steering shaft by the second rack and the second pinion.
The first conversion mechanism may include a second ball screw joined to the steering shaft and the electric motor, the second ball screw being driven to rotate by the electric motor, and a second ball nut attached to the second ball screw. In this case, the second conversion mechanism may include a second pin joined to the second ball nut, and a second arm joined to the second pin and the transom bracket, and the first conversion mechanism may be arranged to convert linear motion of the second ball screw with respect to the second ball nut into turning of the steering shaft by the second pin and the second arm. The rotation of the electric motor is converted into linear motion of the second ball screw with respect to the second ball nut by the second ball screw and the second ball nut, and the linear motion of the second ball screw is converted into turning of the steering shaft by the second pin and the second arm.
The power conversion mechanism may include a second drive gear joined to the steering shaft and the electric motor, the second drive gear being driven to rotate by the electric motor, and a second driven gear engaged with the second drive gear, the second driven gear being joined to the transom bracket.
The second drive gear may be arranged to be driven to rotate by the electric motor around a second non-crossing axis that is parallel or substantially parallel to the steering axis and does not cross the steering axis, and the second driven gear may have a second central axis positioned on the steering axis. In this case, the rotation of the electric motor is converted into turning of the second drive gear around the second central axis by the second drive gear and the second driven gear.
The second drive gear may be arranged to be driven to rotate by the electric motor around a second crossing axis crossing the steering axis, and the second driven gear may have a second central axis positioned on the steering axis. In this case, the rotation of the electric motor is converted into turning of the second drive gear around the second central axis by the second drive gear and the second driven gear.
The above and other elements, features, steps, characteristics and advantages of the present invention will become more apparent from the following detailed description of the preferred embodiments with reference to the attached drawings.
Hereinafter, a first marine vessel propulsion apparatus including an electric motor fixed to the transom bracket and a second marine vessel propulsion apparatus including an electric motor fixed to the steering shaft will be described. The description given below is based on a state in which the outboard motor is in a reference posture.
The reference posture is a posture of the outboard motor when the tilting angle of the outboard motor is zero and the steering angle of the outboard motor is zero. The tilting angle of the outboard motor is an angle of the rotational axis (crank axis L1) of the crankshaft with respect to a vertical plane. The tilting angle of the outboard motor 2 when the crank axis L1 extends vertically is zero. The steering angle of the outboard motor is an angle of the rotational axis (rotational axis L2) of the propeller with respect to the center line of the hull. The steering angle of the outboard motor when the rotational axis L2 of the propeller extends in the front-rear direction is zero. A direction toward one side of the front-rear direction (forward direction) is a direction approaching the transom, and the other direction of the front-rear direction (rearward direction) is a direction extending away from the transom.
First Marine Vessel Propulsion Apparatus
First Preferred Embodiment
The first marine vessel propulsion apparatus 1 includes an outboard motor 2. The outboard motor 2 is attached to a transom T1 provided on the rear portion of the hull H1. The outboard motor 2 includes an engine 3, an engine cover 4, and a casing 5. The engine 3 is housed inside the engine cover 4. The engine 3 includes a crankshaft 6. The crankshaft 6 is rotatable around a crank axis L1. The crankshaft 6 is joined to a drive shaft (not shown). The drive shaft is joined to a propeller shaft (not shown). The drive shaft and the propeller shaft are housed in the casing 5. The casing 5 includes an upper case 7 and a lower case 8 disposed below the engine cover 4. The lower case 8 supports the propeller 9 rotatably around a rotational axis L2. Rotation of the crankshaft 6 is transmitted to the propeller 9 via the drive shaft and the propeller shaft. The propeller 9 is rotatable in a forward propelling direction and a backward propelling direction opposite to the forward propelling direction. The propeller 9 is driven to rotate in the forward propelling direction and the backward propelling direction by the engine 3.
The first marine vessel propulsion apparatus 1 includes a transom bracket 10, a steering shaft 11, and a tilt shaft 12. The outboard motor 2 includes a tilt bracket 13. The transom bracket 10 is attachable to the transom T1. The transom bracket 10 includes a plate-shaped attaching portion 14 to be attached to the transom T1 and a tubular housing portion 15 disposed at the rear of the attaching portion 14. The steering shaft 11 is joined to the transom bracket 10. The tilt bracket 13 is joined to the steering shaft 11 via the tilt shaft 12. The steering shaft 11 and the outboard motor 2 are turnable around a steering axis L3 extending in the up-down direction with respect to the transom bracket 10. The outboard motor 2 is turnable around a tilt axis L4 extending in the horizontal direction with respect to the transom bracket 10 and the steering shaft 11. The tilt axis L4 is a central axis of the tilt shaft 12.
As shown in
The first marine vessel propulsion apparatus 1 includes a tilt mechanism 19. The tilt mechanism 19 is joined to the steering shaft 11 and the outboard motor 2. The tilt mechanism 19 turns the outboard motor 2 around the tilt axis L4 with respect to the transom bracket 10 and the steering shaft 11. The outboard motor 2 turns around the tilt axis L4 with respect to the steering shaft 11, so that even if the tilting angle of the outboard motor 2 changes, the steering axis L3 does not move. Specifically, the steering axis L3 is an axis that does not move with respect to the transom bracket 10. A direction in which the outboard motor 2 tilts around the tilt axis L4 so that the upper end of the crank axis L1 is positioned forward relative to the lower end of the crank axis L1 is defined as a positive direction. A range in which the tilting angle of the outboard motor 2 is small is a trim range, and a range in which the tilting angle of the outboard motor 2 is larger than the upper limit of the trim range is a tilt range.
In
The first marine vessel propulsion apparatus 1 includes a steering mechanism 20. The steering mechanism 20 is joined to the transom bracket 10 and the steering shaft 11. The steering mechanism 20 turns the steering shaft 11 and the tilt shaft 12 around the steering axis L3 with respect to the transom bracket 10. The outboard motor 2 and the tilt mechanism 19 turn around the steering axis L3 together with the steering shaft 11 and the tilt shaft 12 according to turning of the steering shaft 11. The tilt shaft 12 turns around the steering axis L3 together with the outboard motor 2, so that the tilt axis L4 that is the central axis of the tilt shaft 12 turns around the steering axis L3 with respect to the transom bracket 10 according to turning of the outboard motor 2 around the steering axis L3. The position of the outboard motor 2 when the steering angle of the outboard motor 2 is zero is defined as a steering origin. As shown in
The tilt mechanism 19 includes two trim cylinders 21, a tilt cylinder 22, and a frame 23. Two trim cylinders 21 are disposed parallel or substantially parallel to each other at an interval in the right-left direction. Each trim cylinder 21 is disposed obliquely along the front-rear direction so that the upper end of the trim cylinder 21 is positioned rearward relative to the lower end of the trim cylinder 21. The tilt cylinder 22 extends in the up-down direction. The upper end of the tilt cylinder 22 (upper end portion of a tilt rod 27) is positioned higher than the trim cylinders 21. The tilt cylinder 22 is disposed so that the tilt cylinder 22 is positioned between the two trim cylinders 21 as viewed in the front-rear direction.
Each trim cylinder 21 includes a cylinder main body 24 and a trim rod 25 extending along the central axis of the trim cylinder 21. Each trim rod 25 projects upward from the upper end of the cylinder main body 24. Each cylinder main body 24 is fixed to the frame 23. On the other hand, the tilt cylinder 22 includes a cylinder main body 26 and a tilt rod 27 extending along the central axis of the tilt cylinder 22. The tilt rod 27 projects upward from the upper end of the cylinder main body 26. The lower end portion of the cylinder main body 26 is joined to the frame 23 via a lower pin 28 extending in the right-left direction. The tilt cylinder 22 is turnable around the lower pin 28 with respect to the frame 23.
The cylinders 21 and 22 preferably are, for example, hydraulic cylinders. The tilt mechanism 19 includes a pump 30 that supplies hydraulic oil, a tank 31 storing the hydraulic oil, a motor 32 that drives the pump 30, and a plurality of pipes 33 connected to the pump 30 and the tank 31. The pump 30, the tank 31, the motor 32, and the pipes 33 are held by the frame 23. The pump 30 and the tank 31 are disposed at an interval in the right-left direction. The motor 32 is disposed above the pump 30. The pump 30 and the motor 32 are disposed above one trim cylinder 21, and the tank 31 is disposed above the other trim cylinder 21. The tilt cylinder 22 is disposed so that the tilt cylinder 22 is positioned between the pump 30 and motor 32 and the tank 31 as viewed in the front-rear direction.
The frame 23 includes a seat portion 23a disposed along a horizontal plane, a pair of projections 23b projecting downward from the seat portion 23a, and a support portion 23c disposed along a horizontal plane above the seat portion 23a. The pair of projections 23b are disposed at an interval in the right-left direction below the seat portion 23a. The cylinder main body 24 of the trim cylinder 21 is fixed to the frame 23. In the first preferred embodiment, for example, the cylinder main body 24 of the trim cylinder 21 and the frame 23 preferably are an integral casting. The cylinder main body 26 of the tilt cylinder 22 is inserted in a through-hole 23d (refer to
The pump 30, the tank 31, and the motor 32 are disposed rearward relative to the tilt cylinder 22. The lateral side of the pump 30, the tank 31, and the motor 32 is opened (for example, refer to
As shown in
The upper end portion of the tilt rod 27 projects upward from the through-hole 34 of the joint portion 17. The upper end portion of the tilt rod 27 is joined to the tilt bracket 13 via an upper pin 35 extending in the right-left direction. Therefore, the outboard motor 2 is supported by the tilt cylinder 22. The tilt rod 27 is turnable around the upper pin 35 with respect to the tilt bracket 13. On the other hand, as shown in
When the projecting amount of the tilt rod 27 increases, the tilt bracket 13 is pushed up by the tilt rod 27 and the outboard motor 2 turns up around the tilt axis L4. When the projecting amounts of the trim rods 25 increase in the state in which the outboard motor 2 is positioned in the trim range, the tilt bracket 13 is pushed up by the trim rods 25 and the outboard motor 2 turns up around the tilt axis L4. The tilt cylinder 22 can hold the outboard motor 2 at an arbitrary position between a full trim-in angle (see the outboard motor 2 shown by the alternate long and short dashed lines in
The steering mechanism 20 includes an electric motor 37, a power conversion mechanism 38, a reduction gear mechanism 39, and a steering case 40. The reduction gear mechanism 39 decelerates the rotation of the electric motor 37 and transmits the decelerated rotation to the power conversion mechanism 38. The power conversion mechanism 38 converts the power of the electric motor 37 transmitted by the reduction gear mechanism 39 into turning of the steering shaft 11 around the steering axis L3. The outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10 according to turning of the steering shaft 11 around the steering axis L3. The power conversion mechanism 38 includes a first conversion mechanism 41 that converts the rotation of the electric motor 37 into linear motion, and a second conversion mechanism 42 that converts the linear motion into turning of the steering shaft 11 around the steering axis L3 with respect to the transom bracket 10.
The electric motor 37 includes a motor main body 43 and a rotary shaft 44. The rotary shaft 44 is rotatable in the forward direction and the reverse direction opposite to the forward direction. The rotation of the rotary shaft 44 is transmitted to the first conversion mechanism 41 of the power conversion mechanism 38 via the reduction gear mechanism 39. The electric motor 37 is housed in a steering case 40. The electric motor 37 is disposed so that, for example, the rotary shaft 44 extends in the right-left direction. The motor main body 43 is fixed to the steering case 40. The steering case 40 is fixed to the transom bracket 10. Therefore, the electric motor 37 is fixed to the transom bracket 10 via the steering case 40. The electric motor 37 may be fixed to the transom bracket 10 via an intermediate member such as the steering case 40, or may be directly fixed to the transom bracket 10.
The first conversion mechanism 41 includes a first ball screw 45, and a tubular first ball nut 46 attached to the first ball screw 45 via a plurality of balls. The second conversion mechanism 42 includes a first rack 47 joined to the first ball nut 46, and a first pinion 48 engaged with the first rack 47. The first ball screw 45, the first ball nut 46, and the first rack 47 are housed in the steering case 40, and are held by the steering case 40. On the other hand, most of the first pinion 48 is disposed outside the steering case 40. The first pinion 48 is joined to the intermediate portion 18. Therefore, the first pinion 48 is joined to the tubular portion 16 and the joint portion 17 via the intermediate portion 18. The first pinion 48 turns around the steering axis L3 together with the steering shaft 11.
The first ball screw 45 extends in the right-left direction inside the steering case 40. The rotational axis of the first ball screw 45 and the rotational axis of the electric motor 37 are parallel or substantially parallel to each other. The first ball screw 45 is disposed rearward relative to the electric motor 37. Both end portions of the first ball screw 45 are supported on the steering case 40 via bearings 49. The first ball screw 45 is joined to the transom bracket 10 via the steering case 40, and joined to the electric motor 37 via the reduction gear mechanism 39. The rotation of the electric motor 37 is transmitted to the first ball screw 45 via the reduction gear mechanism 39. Accordingly, the first ball screw 45 is driven so as to be rotated by the electric motor 37. When the first ball screw 45 rotates around the central axis of the first ball screw 45, the first ball nut 46 moves along the first ball screw 45, and the rotation of the first ball screw 45 is converted into linear motion of the first ball nut 46 with respect to the first ball screw 45.
The first rack 47 is provided on the outer peripheral portion of the first ball nut 46. The first rack 47 is, for example, integral with the first ball nut 46. The first rack 47 and the first ball nut 46 may constitute an integral member, or may constitute a member including a plurality of divided bodies joined integrally. The first rack 47 includes a plurality of teeth aligned in the axial direction of the first ball screw 45. The first rack 47 is opposed to the steering opening 50 provided in the steering case 40. The inside of the steering case 40 is connected to the inside of the housing portion 15 via a transom opening 51 provided in the housing portion 15 of the transom bracket 10. When the first ball screw 45 rotates, the first rack 47 moves along the first ball screw 45 together with the first ball nut 46.
The first pinion 48 projects from the outer peripheral portion of the intermediate portion 18. The first pinion 48 has, for example, a fan shape having a central axis positioned on the steering axis L3. The first pinion 48 is, for example, integral with the intermediate portion 18. The first pinion 48 and the intermediate portion 18 may constitute an integral member, or may constitute a member including a plurality of divided bodies joined integrally. The first pinion 48 enters the inside of the steering case 40 through the steering opening 50 and the transom opening 51. When the first rack 47 moves in the axial direction of the first ball crew 45, the position of engagement between the first rack 47 and the first pinion 48 moves and the first pinion 48 turns around the steering axis L3. Accordingly, the linear motion of the first ball nut 46 is converted into turning of the steering shaft 11 around the steering axis L3.
The reduction gear mechanism 39 includes a plurality of reduction gears (a first reduction gear 52, a second reduction gear 53, a third reduction gear 54, and a fourth reduction gear 55). The reduction gears 52 to 55 are, for example, external gears. The first reduction gear 52 is joined to the rotary shaft 44 of the electric motor 37. The first reduction gear 52 and the rotary shaft 44 are disposed coaxially with each other. The first reduction gear 52 rotates together with the rotary shaft 44. The first reduction gear 52 engages with the second reduction gear 53, and the second reduction gear 53 engages with the third reduction gear 54. The third reduction gear 54 engages with the fourth reduction gear 55. The second reduction gear 53 and the third reduction gear 54 are held rotatably by the steering case 40. The fourth reduction gear 55 is joined to the first ball screw 45. The fourth reduction gear 55 and the first ball screw 45 are disposed coaxially with each other. The first ball screw 45 rotates together with the fourth reduction gear 55.
The rotation of the electric motor 37 is transmitted to the first ball screw 45 by the reduction gear mechanism 39. The power of the electric motor 37 is amplified by deceleration of the rotation of the electric motor 37 by the reduction gear mechanism 39. The rotation of the first ball screw 45 is converted into linear motion of the first ball nut 46 with respect to the first ball screw 45 by the first ball screw 45 and the first ball nut 46. Then, the linear motion of the first ball nut 46 is converted into turning of the steering shaft 11 around the steering axis L3 by the first rack 47 and the first pinion 48. Accordingly, as shown in
As described above, the electric motor 37 is fixed to the transom bracket 10 via the steering case 40. Therefore, when the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10, the electric motor 37 does not turn around the steering axis L3 with respect to the transom bracket 10 together with the outboard motor 2 (refer to
As described above, in the first preferred embodiment, the steering mechanism 20 includes the electric motor 37 and the power conversion mechanism 38. Specifically, the steering mechanism 20 is an electric steering mechanism that includes an electric motor. The electric motor 37 is driven by supply of electric power. The power of the electric motor 37 is converted into turning of the steering shaft 11 around the steering axis L3. The outboard motor 2 and the steering shaft 11 are turnable around the steering axis L3 with respect to the transom bracket 10. Therefore, by converting the power of the electric motor 37 into turning of the steering shaft 11 around the steering axis L3, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10. Accordingly, the marine vessel is steered.
In the electric steering mechanism, a time lag between a steering command to turn the outboard motor 2 around the steering axis L3 and turning of the outboard motor 2 is smaller than that of a hydraulic steering mechanism. Therefore, the electric motor 37 does not need to be driven when the outboard motor 2 is not turned around the steering axis L3, and energy loss can be reduced as compared with a marine vessel propulsion apparatus that includes a hydraulic steering mechanism. In addition, the steering mechanism 20 can control the stop position of the outboard motor 2 and the turning angle of the outboard motor 2 with high accuracy as compared with a hydraulic steering mechanism. Further, the steering mechanism 20 does not need a hydraulic pump and a tank, etc., so that the steering mechanism can be decreased in size as compared with a marine vessel propulsion apparatus including a hydraulic steering mechanism.
Second Preferred Embodiment
A major difference between the second preferred embodiment and the above-described first preferred embodiment is that the steering mechanism 220 is provided instead of the steering mechanism 20. The steering mechanism 220 includes the electric motor 37, a power conversion mechanism 238, the reduction gear mechanism 39 and the steering case 40. The power conversion mechanism 238 includes the first conversion mechanism 41 and a second conversion mechanism 242. The linear motion of the first rack 47 is converted into turning of the steering shaft 11 around the steering axis L3 by an intermediate gear 256.
In detail, the second conversion mechanism 242 includes an intermediate gear 256 that transmits power from the first rack 47 to the second pinion 248. The intermediate gear 256 has a columnar shape. The intermediate gear 256 extends in the up-down direction. The intermediate gear 256 includes a first supported portion 257, a second supported portion 258, a first gear portion 259, and a second gear portion 260 aligned along the central axis of the intermediate gear 256. The first supported portion 257, the second supported portion 258, the first gear portion 259, and the second gear portion 260 are disposed coaxially. The first gear portion 259 is disposed between the first supported portion 257 and the second supported portion 258, and the second supported portion 258 is disposed between the first gear portion 259 and the second gear portion 260. The first supported portion 257 and the second supported portion 258 are supported rotatably by the steering case 40. The gap between the first supported portion 257 and the steering case 40 is sealed by a seal member 261, and the gap between the second supported portion 258 and the steering case 40 is sealed by a seal member 261.
The first gear portion 259 is disposed inside the steering case 40. The first gear portion 259 engages with the first rack 47. On the other hand, the second gear portion 260 is disposed outside the steering case 40. The second gear portion 260 engages with the second pinion 248. The second pinion 248 has, for example, a fan shape having a central axis positioned on the steering axis L3. The second pinion 248 is joined to the joint portion 17. The second pinion 248 turns around the steering axis L3 together with the joint portion 17. The linear motion of the first rack 47 is converted into rotation of the intermediate gear 256 by the first rack 47 and the first gear portion 259. Then, the rotation of the intermediate gear 256 is converted into turning of the joint portion 17 around the steering axis L3 by the second pinion 248 and the second gear portion 260. Accordingly, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10.
Third Preferred Embodiment
A major difference between this third preferred embodiment and the above-described first preferred embodiment is that the steering mechanism 320 is provided instead of the steering mechanism 20. The steering mechanism 320 includes the electric motor 37, a power conversion mechanism 338, the reduction gear mechanism 39, and the steering case 40. The power conversion mechanism 338 includes the first conversion mechanism 41 and a second conversion mechanism 342. The linear motion of the first ball nut 46 is converted into turning of the steering shaft 11 around the steering axis L3 by a first pin 362 and a first arm 363.
In detail, the second conversion mechanism 342 includes the first pin 362 joined to the first ball nut 46, and the first arm 363 joined to the first pin 362 and the steering shaft 11. For example, the first pin 362 projects upward from the first ball nut 46. The first pin 362 is housed in the steering case 40. When the first ball screw 45 rotates, the first pin 362 moves along the first ball screw 45 together with the first ball nut 46. The first arm 363 projects from the outer peripheral portion of the intermediate portion 18. The first arm 363 is, for example, integral with the intermediate portion 18. The first arm 363 and the intermediate portion 18 may constitute an integral member, or may constitute a member including a plurality of divided bodies joined integrally. The first arm 363 enters the inside of the steering case 40 through the steering opening 50 and the transom opening 51. The first arm 363 includes a forked engagement portion 364. The first pin 362 is disposed inside the engagement portion 364.
The rotation of the electric motor 37 is transmitted to the first ball screw 45 by the reduction gear mechanism 39. The rotation of the first ball screw 45 is converted into linear motion of the first ball nut 46 with respect to the first ball screw 45 by the first ball screw 45 and the first ball nut 46. The first pin 362 moves along the first ball screw 45 together with the first ball nut 46. When the first pin 362 moves along the first ball screw 45, the first pin 362 and the first arm 363 turn relative to each other around the central axis of the first pin 362, and the intermediate portion 18 of the steering shaft 11 turns around the steering axis L3. Therefore, the linear motion of the first ball nut 46 is converted into turning of the steering shaft 11 by the first pin 362 and the first arm 363. Accordingly, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10.
Fourth Preferred Embodiment
A major difference between the fourth preferred embodiment and the above-described first preferred embodiment is that the steering mechanism 420 is provided instead of the steering mechanism 20. The steering mechanism 420 includes the electric motor 37, a power conversion mechanism 438, the reduction gear mechanism 39, and the steering case 40. The rotation of the electric motor 37 is converted into turning of the steering shaft 11 around the steering axis L3 by a first drive gear 465 and a first driven gear 466.
In detail, the power conversion mechanism 438 includes the first drive gear 465 that is driven to rotate by the electric motor 37, and the first driven gear 466 engaged with the first drive gear 465. The first drive gear 465 is, for example, a worm, and the first driven gear 466 is, for example, a worm wheel.
The first drive gear 465 extends in the right-left direction inside the steering case 40. The rotational axis of the first drive gear 465 and the rotational axis of the electric motor 37 are parallel or substantially parallel to each other. The first drive gear 465 is disposed rearward relative to the electric motor 37. Both end portions of the first drive gear 465 are supported on the steering case 40 via the bearings 49. The first drive gear 465 is rotatable around the central axis of the first drive gear 465 with respect to the steering case 40. The central axis (rotational axis) of the first drive gear 465 is a first non-crossing axis L405 that is not parallel to and does not cross the steering axis L3. The first drive gear 465 is joined to the transom bracket 10 via the steering case 40, and joined to the electric motor 37 via the reduction gear mechanism 39. The rotation of the electric motor 37 is transmitted to the first drive gear 465 via the reduction gear mechanism 39. Accordingly, the first drive gear 465 is driven to rotate around the first non-crossing axis L405 by the electric motor 37.
The first driven gear 466 projects from the outer peripheral portion of the intermediate portion 18. The first driven gear 466 has, for example, a fan shape having a first central axis L406 positioned on the steering axis L3. The first driven gear 466 is, for example, integral with the intermediate portion 18. The first driven gear 466 and the intermediate portion 18 may constitute an integral member, or a member including a plurality of divided bodies joined integrally. The first driven gear 466 enters the inside of the steering case 40 through the steering opening 50 and the transom opening 51. The first driven gear 466 turns around the steering axis L3 together with the steering shaft 11.
The rotation of the electric motor 37 is transmitted to the first drive gear 465 by the reduction gear mechanism 39. When the first drive gear 465 rotates around the first non-crossing axis L405, the first driven gear 466 turns around the steering axis L3, and the position of engagement between the first drive gear 465 and the first driven gear 466 moves. Accordingly, the rotation of the electric motor 37 is converted into turning of the steering shaft 11 around the steering axis L3 by the first drive gear 465 and the first driven gear 466. Therefore, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10.
Fifth Preferred Embodiment
A major difference between the fifth preferred embodiment and the above-described first preferred embodiment is that the steering mechanism 520 is provided instead of the steering mechanism 20. The steering mechanism 520 includes the electric motor 37, a power conversion mechanism 538, and the steering case 40. The rotation of the electric motor 37 is converted into turning of the steering shaft 11 around the steering axis L3 by a first drive gear 565 and a first driven gear 566.
In detail, the power conversion mechanism 538 includes the first drive gear 565 that is driven to rotate by the electric motor 37, and the first driven gear 566 engaged with the first drive gear 565. The first drive gear 565 and the first driven gear 566 are, for example, bevel gears.
The first drive gear 565 is joined to the rotary shaft 44 of the electric motor 37. The first drive gear 565 is disposed coaxially with the rotary shaft 44. The first reduction gear 52 rotates together with the rotary shaft 44. By the electric motor 37, the first drive gear 565 is driven to rotate around a first crossing axis L507 that crosses the steering axis L3. Specifically, the electric motor 37 is disposed so that the rotary shaft 44 extends in the front-rear direction. The motor main body 43 of the electric motor 37 is fixed to the steering case 40. The electric motor 37 is fixed to the transom bracket 10 via the steering case 40. Therefore, the first drive gear 565 is joined to the transom bracket 10 via the electric motor 37 and the steering case 40.
The first driven gear 566 is joined to the joint portion 17 of the steering shaft 11. The first driven gear 566 has, for example, a fan shape having a first central axis L406 positioned on the steering axis L3. The first driven gear 566 turns around the steering axis L3 together with the steering shaft 11. The rotation of the electric motor 37 is transmitted to the first driven gear 566 via the first drive gear 565. When the first drive gear 565 rotates around the first crossing axis L507, the first driven gear 566 turns around the steering axis L3, and the position of engagement between the first drive gear 565 and the first driven gear 566 moves. Accordingly, the rotation of the electric motor 37 is converted into turning of the steering shaft 11 around the steering axis L3 by the first drive gear 565 and the first driven gear 566. Therefore, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10.
Second Marine Vessel Propulsion Apparatus
Next, a second marine vessel propulsion apparatus including an electric motor fixed to the steering shaft will be described. In the description given below, components equivalent to those shown in
Sixth Preferred Embodiment
The second marine vessel propulsion apparatus 601 includes the outboard motor 2, the transom bracket 10, a steering shaft 611, and the tilt shaft 12. The second marine vessel propulsion apparatus 601 further includes the tilt mechanism 19 and a steering mechanism 620. The steering shaft 611 includes the tubular portion 16 and the joint portion 17. The joint portion 17 is joined to the upper end portion of the tubular portion 16. The joint portion 17 is, for example, integral with the tubular portion 16 . The tubular portion 16 and the joint portion 17 may constitute an integral member, or may constitute a member including a plurality of divided bodies joined integrally. Specifically, the steering shaft 611 may be a member including a plurality of divided bodies, or may be an integral member. The inside of the tubular portion 16 is connected to the through-hole 34 of the joint portion 17. The cylinder main body 26 of the tilt cylinder 22 is disposed inside the tubular portion 16. The lower end portion of the tubular portion 16 is joined to the frame 23. The upper end portion of the tilt rod 27 projects upward from the through-hole 34 of the joint portion 17. The upper end portion of the tilt rod 27 is joined to the tilt bracket 13 via the upper pin 35.
The steering shaft 611 further includes a fixing portion 667 provided on the joint portion 17. The steering case 40 is fixed to the fixing portion 667. Therefore, the electric motor 37 is fixed to the steering shaft 611 via the steering case 40. The outboard motor 2 turns around the tilt axis L4 with respect to the steering shaft 611. Therefore, as shown in
On the other hand, the electric motor 37 is fixed to the steering shaft 611, so that when the steering shaft 611 turns around the steering axis L3, the electric motor 37 turns around the steering axis L3 together with the steering shaft 611 and the outboard motor 2. Therefore, as shown in
The steering mechanism 620 includes the electric motor 37, a power conversion mechanism 638, the reduction gear mechanism 39, and the steering case 40. As shown in
As shown in
As shown in
As shown in
As shown in
As shown in
In detail, the rotation of the electric motor 37 is transmitted to the second ball screw 645 by the reduction gear mechanism 39. When the second ball screw 645 rotates, a force of relative movement in the axial direction of the second ball screw 645 is applied to the second ball screw 645 and the second ball nut 646. According to movement of the position of engagement between the second rack 647 and the second pinion 648, the force is converted into a force that turns the second ball screw 645 and the second ball nut 646 around the steering axis L3. Accordingly, as shown in
The second ball screw 645 is joined to the steering shaft 611 via the steering case 40. Therefore, the second ball screw 645 turns around the steering axis L3, and accordingly, the steering shaft 611 turns around the steering axis L3 with respect to the transom bracket 10. Specifically, the rotation of the electric motor 37 is converted into linear motion of the second ball nut 646 with respect to the second ball screw 645 by the second ball screw 645 and the second ball nut 646. Concurrently, the linear motion of the second ball nut 646 is converted into turning of the steering shaft 611 around the steering axis L3 by the second rack 647 and the second pinion 648. Accordingly, as shown in
Seventh Preferred Embodiment
A major difference between the seventh preferred embodiment and the above-described sixth preferred embodiment is that the steering mechanism 720 is provided instead of the steering mechanism 620. The steering mechanism 720 includes the electric motor 37, a power conversion mechanism 738, the reduction gear mechanism 39, and the steering case 40. The power conversion mechanism 738 includes the first conversion mechanism 641 and a second conversion mechanism 742. Linear motion of the second ball nut 646 is converted into turning of the steering shaft 611 around the steering axis L3 by a second pin 762 and a second arm 763.
In detail, the second conversion mechanism 742 includes the second pin 762 joined to the second ball nut 646, and the second arm 763 joined to the second pin 762 and the transom bracket 10. For example, the second pin 762 projects downward from the second ball nut 646. The second pin 762 is housed in the steering case 40. When the second ball screw 645 rotates, the second pin 762 moves along the second ball screw 645 together with the second ball nut 646. The second arm 763 projects from the housing portion 15 of the transom bracket 10. The second arm 763 is, for example, integral with the housing portion 15. The second arm 763 and the housing portion 15 may constitute an integral member, or may constitute a member including a plurality of divided bodies joined integrally. The second arm 763 enters the inside of the steering case 40 through the steering opening 50 and the gear opening 670. The second arm 763 includes a forked engagement portion 764. The second pin 762 is disposed inside the engagement portion 764.
The rotation of the electric motor 37 is transmitted to the second ball screw 645 by the reduction gear mechanism 39. When the second ball screw 645 rotates, a force of relative movement in the axial direction of the second ball screw 645 is applied to the second ball screw 645 and the second ball nut 646. By relative turning of the second pin 762 and the second arm 763 around the central axis of the second pin 762, the force is converted into a force that turns the second ball screw 645 and the second ball nut 646 around the steering axis L3. Specifically, the rotation of the electric motor 37 is converted into linear motion of the second ball nut 646 with respect to the second ball screw 645 by the second ball screw 645 and the second ball nut 646. Concurrently, the linear motion of the second ball nut 646 is converted into turning of the steering shaft 611 around the steering axis L3 by the second pin 762 and the second arm 763. Accordingly, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10.
Eighth Preferred Embodiment
A major difference between the eighth preferred embodiment and the above-described sixth preferred embodiment is that the steering mechanism 820 is provided instead of the steering mechanism 620. The steering mechanism 820 includes the electric motor 37, a power conversion mechanism 838, the reduction gear mechanism 39, and the steering case 40. The rotation of the electric motor 37 is converted into turning of the steering shaft 611 around the steering axis L3 by a second drive gear 865 and a second driven gear 866.
In detail, the power conversion mechanism 838 includes the second drive gear 865 that is driven to rotate by the electric motor 37, and the second driven gear 866 engaged with the second driven gear 865. The second drive gear 865 is, for example, a worm, and the second driven gear 866 is, for example, a worm wheel.
The second drive gear 865 extends in the right-left direction inside the steering case 40. The rotational axis of the second drive gear 865 and the rotational axis of the electric motor 37 are parallel or substantially parallel to each other. The second drive gear 865 is disposed rearward relative to the electric motor 37. Both end portions of the second drive gear 865 are supported on the steering case 40 via bearings 49. The second drive gear 865 is rotatable around the central axis of the second drive gear 865 with respect to the steering case 40. The central axis (rotational axis) of the second drive gear 865 is a second non-crossing axis L805 that is not parallel to and does not cross the steering axis L3. The second drive gear 865 is joined to the steering shaft 611 via the steering case 40, and joined to the electric motor 37 via the reduction gear mechanism 39. The rotation of the electric motor 37 is transmitted to the second drive gear 865 via the reduction gear mechanism 39. Accordingly, the second drive gear 865 is driven to rotate around the second non-crossing axis L805 by the electric motor 37.
The second driven gear 866 includes the cylindrical portion 671 and a gear portion 872. The second driven gear 866 is fixed to the transom bracket 10 via the stay 669. The second driven gear 866 is covered by the gear case 668. The gear case 668 is disposed around the second driven gear 866. The gear portion 872 of the second driven gear 866 projects from the outer peripheral portion of the cylindrical portion 671. The gear portion 872 has, for example, a fan shape having a second central axis L806 positioned on the steering axis L3. The gear portion 872 enters the inside of the steering case 40 through the steering opening 50 and the gear opening 670. The gear portion 872 engages with the second rack 647 inside the steering case 40. The rotation of the electric motor 37 is converted into turning of the steering shaft 611 around the steering axis L3 by the second drive gear 865 and the second driven gear 866.
In detail, the rotation of the electric motor 37 is transmitted to the second drive gear 865 by the reduction gear mechanism 39. The second driven gear 866 is fixed to the transom bracket 10, so that when the second drive gear 865 rotates around the second non-crossing axis L805, a force that moves the second drive gear 865 in the axial direction of the second drive gear 865 is applied. This force is converted into a force that turns the second drive gear 865 around the steering axis L3 by movement of the position of engagement between the second drive gear 865 and the second driven gear 866. The second drive gear 865 is joined to the steering shaft 611 by the electric motor 37 and the steering case 40. Therefore, according to turning of the second drive gear 865 around the steering axis L3, the steering shaft 611 turns around the steering axis L3 with respect to the transom bracket 10. Accordingly, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10.
Ninth Preferred Embodiment
A major difference between the ninth preferred embodiment and the above-described sixth preferred embodiment is that the steering mechanism 920 is provided instead of the steering mechanism 620. The steering mechanism 920 includes the electric motor 37, a power conversion mechanism 938, and the steering case 40. The rotation of the electric motor 37 is converted into turning of the steering shaft 611 around the steering axis L3 by a second drive gear 965 and a second driven gear 966.
In detail, the power conversion mechanism 938 includes the second drive gear 965 that is driven to rotate by the electric motor 37, and the second driven gear 966 engaged with the second drive gear 965. The second drive gear 965 and the second driven gear 966 are, for example, bevel gears.
The second drive gear 965 is joined to the rotary shaft 44 of the electric motor 37. The second drive gear 965 and the rotary shaft 44 are disposed coaxially with each other. The second reduction gear 53 rotates together with the rotary shaft 44. The second drive gear 965 is driven to rotate around a second crossing axis L907 crossing the steering axis L3 by the electric motor 37. Specifically, the electric motor 37 is disposed so that, for example, the rotary shaft 44 extends in the front-rear direction. The motor main body 43 of the electric motor 37 is fixed to the steering case 40. The electric motor 37 is fixed to the steering shaft 611 via the steering case 40. Therefore, the second drive gear 965 is joined to the steering shaft 611 via the electric motor 37 and the steering case 40.
The second driven gear 966 includes the cylindrical portion 671 and a gear portion 972. The second driven gear 966 is fixed to the transom bracket 10 via the stay 669. The second driven gear 966 is covered by the gear case 668. The gear case 668 is disposed around the second driven gear 966. The gear portion 972 of the second driven gear 966 projects from the outer peripheral portion of the cylindrical portion 671. The gear portion 972 has, for example, a fan shape having the central axis L806 positioned on the steering axis L3. The gear portion 972 engages with the second rack 647. The rotation of the electric motor 37 is converted into turning of the steering shaft 611 around the steering axis L3 by the second drive gear 965 and the second driven gear 966.
In detail, the rotation of the electric motor 37 is transmitted to the second drive gear 965. The second driven gear 966 is fixed to the transom bracket 10, so that when the second drive gear 965 rotates around the second crossing axis L907, the position of engagement between the second drive gear 965 and the second driven gear 966 moves, and accordingly, the second drive gear 965 turns around the steering axis L3. The second drive gear 965 is joined to the steering shaft 611 via the electric motor 37 and the steering case 40. Therefore, according to turning of the second drive gear 965 around the steering axis L3, the steering shaft 611 turns around the steering axis L3 with respect to the transom bracket 10. Accordingly, the outboard motor 2 turns around the steering axis L3 with respect to the transom bracket 10.
Other Preferred Embodiments
Preferred embodiments of the present invention are as described above, however, the present invention is not limited to the contents of the first to ninth preferred embodiments described above, and can be variously changed or combined.
For example, the first to fourth and sixth to eighth preferred embodiments described above describe a case where preferably a reduction gear mechanism is provided in the steering mechanism, and the rotation of the electric motor is transmitted to a ball screw or a drive gear via the reduction gear mechanism. However, in the first to fourth and sixth to eighth preferred embodiments described above, it is also possible that the reduction gear mechanism is not provided in the steering mechanism, and the rotation of the electric motor is transmitted to a ball screw or a drive gear without the reduction gear mechanism.
The fifth and ninth preferred embodiments described above describe a case where preferably a reduction gear mechanism is not provided in the steering mechanism, and the rotation of the electric motor is transmitted to the drive gear without the reduction gear mechanism. However, in the fifth and ninth preferred embodiments, it is also possible that a reduction gear mechanism is provided in the steering mechanism, and the rotation of the electric motor is transmitted to the drive gear via the reduction gear mechanism.
A non-limiting example of the correspondence between the components mentioned in the “SUMMARY OF THE INVENTION” and the components of the above-described preferred embodiments are as follows.
Hull: Hull H1
Transom: Transom T1
Transom bracket: Transom bracket 10
Steering axis: Steering axis L3
Steering shaft: Steering shaft 11, 611
Tilt axis: Tilt axis L4
Outboard motor: Outboard motor 2
Tilt mechanism: Tilt mechanism 19
Electric motor: Electric motor 37
Power conversion mechanism: Power conversion mechanism 38, 238, 338, 438, 538, 638, 738, 838, 938
Steering mechanism: Steering mechanism 20, 220, 320, 420, 520, 620, 720, 820, 920
Marine vessel propulsion apparatus: First marine vessel propulsion apparatus 1, 201, 301, 401, 501, second marine vessel propulsion apparatus 601, 701, 801, 901
Housing portion: Housing portion 15
Reduction gear mechanism: Reduction gear mechanism 39
First conversion mechanism: First conversion mechanism 41, 641
Second conversion mechanism: Second conversion mechanism 42, 242, 342, 642, 742
First ball screw: First ball screw 45
First ball nut: First ball nut 46
First rack: First rack 47
First pinion: First pinion 48
First pin: First pin 362
First arm: First arm 363
First drive gear: First drive gear 465, 565
First driven gear: First driven gear 466, 566
First non-crossing axis: First non-crossing axis L405
First central axis: First central axis L406
First crossing axis: First crossing axis L507
Second ball screw: Second ball screw 645
Second ball nut: Second ball nut 646
Second rack: Second rack 647
Second pinion: Second pinion 648
Second pin: Second pin 762
Second arm: Second arm 763
Second drive gear: Second drive gear 865, 965
Second driven gear: Second driven gear 866, 966
Second non-crossing axis: Second non-crossing axis L805
Second central axis: Second central axis L806
Second crossing axis: Second crossing axis L907
The present application corresponds to Japanese Patent Application No. 2010-230851 filed in the Japan Patent Office on Oct. 13, 2010,and the entire disclosure of this application is incorporated herein by reference.
While preferred embodiments of the present invention have been described above, it is to be understood that variations and modifications will be apparent to those skilled in the art without departing from the scope and spirit of the present invention. The scope of the present invention, therefore, is to be determined solely by the following claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2010-230851 | Oct 2010 | JP | national |
