JP2005014722A - Shift operation device of outboard engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve a shift operation feeling; and to reduce the size of a transmission mechanism, in a shift operation device of an outboard engine. <P>SOLUTION: This shift operation device of the outboard engine has an operation cable C for transmitting operation force applied to an operation handle, a shift rod for switching a shift position of a forward-backward switching device, a driving arm 72 integrally rotatably connected to the shift rod, and the transmission mechanism 60 connected to the operation cable C, and transmitting the operation force to the driving arm 72. The transmission mechanism 60 is composed of arm mechanisms 61, 62 and 63 pivoted on a pivot part arranged in an outboard engine body, and integrally rotating around the immovable rotational center line L4. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a shift operation device including a shift rod that switches a shift position of a forward / reverse switching device provided in a propulsion unit of an outboard motor.
[0002]
[Prior art]
In a marine vessel propulsion apparatus including a propulsion unit having a propeller driven by an engine, the propulsion unit is provided with a forward / reverse switching device that switches forward and reverse of the marine vessel. The neutral position, forward position and reverse position of the forward / reverse switching device are switched by a shift rod driven by remote operation using an operation cable.
[0003]
For example, in an outboard motor disclosed in Patent Document 1, in order to drive a shift rod by remote control, a shift input arm fixed to a shift input shaft rotatably supported by a bracket fixed to a crankcase; A shift output arm fixed to the upper end of the shift output shaft rotatably supported by the crankcase, a shift link connecting the shift input arm and the shift output arm, and a drive provided at the lower end of the shift output shaft A sector gear and a driven sector gear provided at the upper end of the shift rod and meshing with the drive sector gear are provided. Then, the operating force applied by the operator to the operation lever to switch the shift position is transmitted to the shift input arm to which the Bowden wire connected to the operation lever is connected, and further shifted from the shift input arm via the shift link. Sequentially transmitted to the output arm, the drive sector gear and the driven sector gear, the driven sector gear drives the shift rod.
[0004]
In the outboard motor disclosed in Patent Document 2, a shift link connected to the remote control cable via a pin that slides along a guide groove of a guide fixed to the exhaust guide, and a pin connected to the shift link via the pin And a shift arm connected to the shift rod. The operating force for switching the shift position is transmitted from the remote control cable extending from the remote control device to the shift ring through the pin, and further transmitted to the shift arm, and the shift arm drives the shift rod.
[0005]
[Patent Document 1]
JP-A-8-91296
[Patent Document 2]
JP-A-9-123996
[0006]
[Problems to be solved by the invention]
By the way, all the said prior art is provided with the link mechanism which has a shift link in order to drive a shift rod with an operating force. Therefore, in the outboard motor disclosed in Patent Document 1, the shift link that connects the shift input arm and the shift output arm needs to rotate relative to both arms. There is a certain gap in the connecting portion. Due to the presence of this gap, a shift occurs between the movement of the shift input arm rotated by the cable and the movement of the shift output arm rotated via the shift link. The operation position and the shift position of the shift position of the shift rod do not always correspond in a fixed relationship, and a good shift operation feeling cannot be obtained.
[0007]
Further, in the outboard motors disclosed in Patent Documents 1 and 2, since the entire shift link is translated and rotated, it is necessary to secure a relatively wide space in which the shift link can move. Is difficult to place in a narrow space, and the layout of the peripheral parts of the shift link is restricted, making it difficult to arrange the peripheral parts in a compact manner.
[0008]
Furthermore, in the outboard motor disclosed in Patent Document 1, since the Bowden wire is fixed to the shift input arm, the Bowden wire is bent by the rotation of the shift input arm, and the sliding resistance of the Bowden wire is increased. As a result of the increased operating resistance, the lightness of the shifting operation is reduced.
[0009]
The present invention has been made in view of such circumstances, and the invention according to claims 1 to 3 can improve the shift operation feeling and make the transmission mechanism compact in the outboard motor shift operation device. With the goal. Further, the invention described in claim 2 further aims to increase the degree of freedom of arrangement of the transmission mechanism, and the invention described in claim 3 further aims to improve the lightness of the shifting operation. .
[0010]
[Means for Solving the Problems and Effects of the Invention]
The invention according to claim 1 is a shift operation device for an outboard motor, wherein an operation cable for transmitting an operation force applied to an operation member provided outside the outboard motor main body and forward / reverse switching of the propulsion unit are provided. A shift rod for switching a shift position of the device; a drive member engaged with or coupled to the shift rod to drive the shift rod; and an operation cable coupled to the operation cable. And a transmission mechanism for transmitting force to the drive member, wherein the transmission mechanism is pivotally supported by a pivotal support portion provided in the outboard motor main body, and is integrally formed around a stationary rotation center line. It is a shift operation device which is a rotating arm mechanism.
[0011]
According to this, since the arm mechanism rotates integrally around the rotation center line, in the transmission path of the operation force in the transmission mechanism that transmits the operation force transmitted from the operation cable to the drive member that drives the shift rod. Therefore, in the transmission mechanism, it is possible to prevent the movement of the rotating members from being shifted. Further, since the arm mechanism rotates around the stationary rotation center line, the arm mechanism does not perform translational movement, and the movement range of the transmission mechanism becomes small.
[0012]
As a result, according to the first aspect of the present invention, the following effects can be obtained. That is, in the transmission mechanism, a shift in movement between the rotating members is prevented, so that the shift operation feeling is improved. Further, since the movement range of the transmission mechanism is reduced, the transmission mechanism is made compact and the transmission mechanism can be arranged in a narrow space.
[0013]
According to a second aspect of the present invention, in the shift operation device according to the first aspect, the arm mechanism includes only an input arm and an output arm that are connected to each other so as to be integrally rotatable, and the input arm is connected to the operation cable. The output arm is connected to the driving member.
[0014]
According to this, the input arm and the output arm or a part of the arms are arranged at different positions in the vertical direction, for example, or the relative arrangement of both arms in the circumferential direction around the rotation center line is set. Since it can be easily changed, a flexible transmission mechanism that can be adapted to various forms of spaces can be obtained.
[0015]
As a result, according to the invention described in claim 2, in addition to the effect of the invention described in claim 1, the following effect is exhibited. That is, since it can be set as the flexible transmission mechanism which can be matched with the space of various forms, the freedom degree of arrangement | positioning of a transmission mechanism becomes large.
[0016]
According to a third aspect of the present invention, in the shift operation device according to the second aspect, the input arm and the operation cable are located inside the outboard motor main body, and the operation cable is within the entire rotation range of the input arm. Are connected by a connecting structure having a long hole that can move in a substantially straight line.
[0017]
According to this, since the operation cable moves in a substantially straight line over the entire rotation range of the input arm inside the outboard motor main body, when the operation cable is pushed and pulled according to the operation force, Since the operation cable is prevented from being bent, an increase in the operation resistance of the operation cable due to such bending is avoided.
[0018]
As a result, according to the invention described in claim 3, in addition to the effect of the invention described in claim 2, the following effect is exhibited. That is, since an increase in operation resistance due to bending of the operation cable is avoided, the lightness of the shift operation is improved.
[0019]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to FIGS.
Referring to FIG. 1, which is a schematic right side view of an outboard motor to which the shift operation device according to the present invention is applied, the outboard motor 1 is driven by the internal combustion engine E and the internal combustion engine E to generate thrust. The outboard motor main body 2 including the propulsion unit P having the above and the support device 3 that supports the outboard motor main body 2 to the hull S are provided.
[0020]
An internal combustion engine E, which is a water-cooled overhead camshaft (OHC) type in-line four-cylinder four-stroke internal combustion engine, has an engine body 4 having a cylinder block 4a and a crankcase 4b coupled to the front end of the cylinder block 4a. A crankshaft 5 having a rotation center line L1 oriented in the vertical direction is rotatably supported between the cylinder block 4a and the crankcase 4b.
[0021]
In this embodiment, the upper, lower, front and rear, and left and right are based on the hull S on which the outboard motor 1 is mounted, and the outboard motor main body 2 shown in FIG. A turning center line L3 that is a turning center line when turning in the direction is parallel to the vertical direction.
[0022]
The engine body 4 is coupled to the upper end portion of the mount case 6, and an oil case 7 having an oil pan portion 7 a and a peripheral wall 7 b is coupled to the lower end portion of the mount case 6, and the lower portion of the engine body 4, the mount case 6 and the oil case 7 Are covered with a cylindrical under cover 8 surrounding them, and the under cover 8 is coupled to the oil case 7 or the extension case 11. An engine cover 9 that covers the upper portion of the engine body 4 is coupled to the upper end portion of the under cover 8, and the engine cover 9 cooperates with the under cover 8 that engages with a flange portion provided around the mount case 6. The internal space above the mount case 6 is formed as an engine room 10 in which the engine body 4 is accommodated. An extension case 11 is coupled to the lower end portion of the oil case 7, and a gear case 12 is coupled to the lower end portion of the extension case 11. An exhaust chamber defined by the lower wall of the mount case 6, the peripheral wall 7 b of the oil case 7 and the extension case 11 communicates with an exhaust passage formed in the gear case 12.
[0023]
A flywheel 13 and a drive shaft 14 are coupled to the lower end portion 5 a of the crankshaft 5 so as to be integrally rotatable with the crankshaft 5. The drive shaft 14 connected to the crankshaft 5 at the upper end portion 14a extends in the vertical direction coaxially with the crankshaft 5, extends downward from the lower end portion 5a, passes through the mount case 6, and then extends into the extension case 11. Is extended downward to reach into the gear case 12, and is coupled to the propeller shaft 18 via the forward / reverse switching device 15 including the gear mechanism 16 and the clutch mechanism 17 in the gear case 12.
[0024]
The power of the internal combustion engine E is transmitted from the crankshaft 5 to the propeller 19 via the drive shaft 14, the forward / reverse switching device 15 and the propeller shaft 18, and the propeller 19 is rotationally driven.
[0025]
Here, the drive shaft 14, the forward / reverse switching device 15, the propeller shaft 18, the propeller 19, the under cover 8, the extension case 11 and the gear case 12 constitute a propulsion unit P, and the internal combustion engine E, the propulsion unit P and the engine cover 9. Constitutes the outboard motor body 2. The under cover 8 and the engine cover 9 constitute a chamber wall of the engine room 10 and an upper cover of the outboard motor main body 2 above the tilt shaft 21 described later.
[0026]
The support device 3 is supported by a pair of left and right stern brackets 20 that are detachably fixed to the hull S, and a tilt shaft 21 that is attached to the left and right stern brackets 20 so as to be rotatable in the vertical direction. And a mount frame 23 that supports the outboard motor body 2 and is supported by the bearing portion 22a of the swivel case 22 so as to be rotatable in the left-right direction.
[0027]
The mount frame 23 includes a swivel shaft 23a that is rotatably fitted to the inner periphery of the bearing portion 22a, a pair of left and right upper mount portions 23b provided at the upper end portion of the swivel shaft 23a, and a lower end portion of the swivel shaft 23a. The lower mount part 23c provided so that attachment or detachment is possible, and the steering arm part 23d provided in the upper end part of the swivel shaft 23a and extending ahead are included.
[0028]
In the upper part of the outboard motor body 2, the mount case 6 is coupled to the upper mount portion 23 b via the upper mount rubber 24 with bolts, and the extension case 11 is connected to the lower case via a pair of left and right lower mount rubbers 25. Then, it is supported by the mount frame 23 by being coupled to the lower mount portion 23c with bolts.
[0029]
Then, the outboard motor main body 2 performs a tilt motion that rotates in the vertical direction with the rotation center line of the swivel case 22 as the tilt center line L2 (see also FIG. 2) by the operation of a hydraulic cylinder mechanism (not shown). Do. Further, the outboard motor main body 2 has a central axis of the swivel shaft 23a when a steering handle (not shown) coupled to the steering arm portion 23d is operated or when the steering arm portion 23d is remotely operated. Is turned in the left-right direction with the turning center line L3 being turned.
[0030]
The gear mechanism 16 includes a drive gear 16a that is coupled to the lower end portion 14b of the drive shaft 14 so as to rotate integrally with the drive shaft 14, and a drive gear 16a that is rotatably supported by the front portion of the propeller shaft 18. This is a bevel gear mechanism composed of a forward gear 16b and a reverse gear 16c that are always meshed.
[0031]
The clutch mechanism 17 includes a shifter 17a that moves in the axial direction of the propeller shaft 18 in response to an operation of a shift rod 30, which will be described later, and a clutch element 17b that is integrally coupled to the shifter 17a. The shifter 17 a is formed with an engaging portion 17 a 1 with which the shift rod 30 is engaged, and the shifter 30 is moved in the axial direction of the propeller shaft 18 by the rotation of the shift rod 30. The clutch element 17b can be rotated integrally with the propeller shaft 18 by being engaged with a spline formed on the outer peripheral surface of the propeller shaft 18, and is selectively engaged with the forward gear 16b and the reverse gear 16c. It can slide in the axial direction.
[0032]
With this structure of the forward / reverse switching device 15, when the clutch mechanism 17 occupies the neutral position according to the operation of the shift rod 30, the clutch element 17b is not engaged with either the forward gear 16b or the reverse gear 16c, and the forward gear Although 16b and reverse gear 16c are rotated by drive gear 16a, the rotation of drive shaft 14 is not transmitted to propeller shaft 18. When the clutch mechanism 17 occupies the forward position, the clutch element 17b engages with the forward gear 16b, so that the rotation of the drive shaft 14 is transmitted to the propeller shaft 18 via the forward gear 16b and the clutch element 17b. A ship advances by the shaft 18 and the propeller 19 rotating forward. Further, when the clutch mechanism 17 occupies the reverse position, the clutch element 17b is engaged with the reverse gear 16c, so that the rotation of the drive shaft 14 is transmitted to the propeller shaft 18 via the reverse gear 16c and the clutch element 17b. The ship moves backward by the reverse rotation of the shaft 18 and the propeller 19. Therefore, the shift rod 30 operates the clutch mechanism 17 to switch the shift position of the forward / reverse switching device 15, that is, the neutral position, the forward position, and the reverse position.
[0033]
Referring to FIGS. 1 and 2, the shift operating device operated by a remote operation using an operation cable C, which will be described later, to activate the clutch mechanism 17 is a remote controller to which an operating force is applied by a driver to switch the shift position. An operation handle 32 of the device 31, a Bowden cable 33 for transmitting an operation force applied to the operation handle 32, and an operation that is arranged in the engine room 10 inside the outboard motor body 2, here the inside of the upper cover in this case. A transmission mechanism 60 that transmits an operating force transmitted through the cable C to a drive arm 72 as a drive member, which will be described later, and a forward mechanism that is disposed in front of the drive shaft 14 and extends substantially parallel to the drive shaft 14. The shift rod 30 is coupled to the shift rod 30 so as to be integrally rotatable, and is driven by an operation force transmitted through the transmission mechanism 60. It includes a drive arm 72 which is also the sector gear to drive the shift rod 30, a neutral switch 80 for detecting the neutral position of the forward-reverse switching device 15, and an actuating mechanism for actuating the neutral switch 80 Te.
[0034]
The shift rod 30 penetrates the inside of the cylindrical swivel shaft 23a in a substantially coaxial state, then extends further downward, penetrates through the extension case 11 and extends into the gear case 12, and within the gear case 12, the shifter 17a Engage with the engaging portion 17a1.
[0035]
The remote control device 31 is disposed in a cockpit outside the outboard motor 1, and an operation handle 32 as an operation member is not only a shift position switching operation but also an opening degree of a throttle valve that controls the intake air amount of the internal combustion engine E. It has a structure that can be operated.
[0036]
The Bowden cable 33 includes a flexible inner cable 34 that transmits an operation force applied to the operation handle 32, and an outer pipe 35 that is a flexible outer cable through which the inner cable 34 is inserted into a hollow portion. Composed.
[0037]
In the outer pipe 35 arranged outside the outboard motor body 2, one end thereof is fixed to the remote control device 31, and the other end together with the outer pipe 26a of the Bowden cable 26 for operating the throttle valve is an undercover. 8 is inserted into a grommet 27 mounted on the right side of the head. At the other end, a tubular locking tool 36 for fixing the outer pipe 35 to the bracket 28 fixed to the under cover 8 with the bolt B1 in the engine room 10 is coupled. By engaging, the outer pipe 35 is fixed to the under cover 8. The bracket 28 constitutes a fixed portion of the outer pipe 35 in the outboard motor main body 2.
[0038]
The bracket 28 is arranged on one side in the left-right direction, which is a direction orthogonal to the reference plane H, here on the right side with respect to a reference plane H that is a plane that includes the turning center line L3 and is orthogonal to the tilt center line L2. The operation cable C passes through the right side of the under cover 8 and extends into the engine room 10 from the outside in front of the outboard motor main body 2. The bracket 28 is disposed above the tilt shaft 21 and slightly ahead of the tilt shaft 21.
[0039]
In the engine room 10, the inner cable 34 extending rearward from the bracket 28 is inserted into a metal guide tube 37 that prevents the inner cable 34 from bending. A connecting rod 38 that is movably inserted into the guide tube 37 and extends rearward beyond the distal end portion 37a of the guide tube 37 is coupled to the end 34a of the inner cable 34 that is positioned in the guide tube 37. The Further, cylindrical and flexible seal members 39a and 39b made of an elastic material such as rubber straddle the connecting rod 38 and the locking tool 36 at the distal end portion 37a and the proximal end portion 37b of the guide tube 37, respectively. Installed. And the guide pipe | tube 37 comprises a universal joint structure inside the seal member 39b, and is connected with the latching tool 36. FIG.
[0040]
2 to 5, the slider 40 is slidably fitted in a guide groove 42 formed in a bracket 41 as a guide portion for guiding the slider 40. The bracket 41 is a member fixed to the crankcase 4b by a bolt B2 inserted through the pair of mounting bosses 41a (see FIGS. 3 and 5). The slider 40 is provided with a first pin 43 that constitutes a connecting portion between the slider 40 and the operation cable C, and further a second pin 44 that constitutes a connecting portion between the slider 40 and an input arm 61 described later of the transmission mechanism 60. Is provided. Then, both pins 43 and 44 are inserted so that there is no backlash in the through hole of the slider 40, the flange 40 a of the slider 40 is in contact with the lower surface of the bracket 41, and the fitting portion 40 b is fitted in the guide groove 42. Thus, the retaining plate 45 is fitted to the pins 43 and 44, and the retaining ring 46 is attached to the pins 43 and 44, so that the slider 40 is slidably held on the bracket 41.
[0041]
Above the guide groove 42, the connecting rod 38 is screwed into the end of the first pin 43, and the member 47 a that engages with the first pin 43 when the inner cable 34 is pushed, and the inner cable 34 are pulled. Sometimes a locking member 47 comprising a member 47b that engages with the first pin 43 is fixed by a lock nut 48 and attached.
[0042]
The slider 40 slides substantially parallel to the operation cable C over the entire sliding range in the guide groove 42 by the inner cable 34 pushed and pulled according to the operation force applied to the operation handle 32. This sliding range is equal to the stroke length of the operation cable C set corresponding to the rotation range of the input arm 61 necessary for switching the shift position. Further, since the length of the guide tube 37 is set based on the stroke length so that the end portion of the inner cable 34 does not come out of the guide tube 37, the minimum distance between the first pin 43 and the bracket 28 is set. Is roughly determined by the length of the guide tube 37 and the stroke length.
[0043]
Therefore, the inner cable 34 passes through the under cover 8 and is connected to the input arm 61 in the engine room 10 via the connecting rod 38 and the slider 40 as a connecting member. The inner cable 34 may be directly connected to the slider 40. Therefore, in this specification, the operation cable C is constituted by the inner cable 34 alone, and an accessory such as the connecting rod 38 is coupled to the inner cable 34 as in this embodiment. In terms of the function to be transmitted, it means that which is equivalent to that constituted by the inner cable 34 alone.
[0044]
The second pin 44 positioned in front of the first pin 43 is positioned closer to the bracket 28 than the first pin 43 in the front-rear direction, and is disposed slightly below the bracket 41 below the guide groove 42. The input arm 61 is slidably fitted into the long hole 64.
[0045]
Referring to FIG. 3, the bracket 41 is provided with a boss 41b that pivotally supports a throttle arm 49 to which an operation cable 50 having the same structure as the operation cable C for operating the throttle valve is coupled. Then, at the end of the pin 51 provided on the throttle arm 49, a locking tool 47 fixed to the end of the operation cable C by the lock nut 48 is locked. The throttle arm 49 is connected to one end of a bell crank 53 pivotally supported by the bracket 41 via a link 52, and further connected to an arm connected to the other end of the bell crank 53 to the valve shaft of the throttle valve. The rod 54 is connected.
[0046]
A transmission mechanism 60 (see also FIG. 1) disposed in the engine room 10 includes an input arm 61 as an input member connected to the operation cable C, and an output arm 62 as an output member connected to the drive arm 72. Is an arm mechanism configured to be integrally rotatable with each other.
[0047]
The input arm 61 disposed on the holder 55, which is a member fixed to the crankcase 4b with the bolt B3, can be integrally rotated with the arm portion 61a to which the operation cable C is connected via the slider 40 and the arm portion 61a. And a pivot shaft 63 to be described later as a pivoted support portion. In the arm portion 61a, the operation cable C pushed and pulled over the entire rotation range of the input arm 61 moves between the bracket 28 in the engine room 10 and the first pin 43 in a substantially straight line. A connecting structure having a long hole 64 is made possible. This connecting structure is fitted in the long hole 64 and the distal end portion 61a1 of the arm portion 61a in which a long hole 64 is formed in the radial direction (or the radial direction of the pivot shaft 63) centering on a rotation center line L4 described later. And the second pin 44 of the slider 40 that moves along the long hole 64 while being in sliding contact with the peripheral wall surface of the long hole 64 in the entire rotation range of the input arm 61.
[0048]
The base end portion 61a2 of the arm portion 61a placed on the upper surface of the boss 55a of the holder 55 has a shape that aligns with the upper portion of the pivot shaft 63 in which a notch rotation portion 63a (see FIG. 3) is formed. A through hole 66 is formed. Then, after the pivot shaft 63 is inserted into the through hole 66, a washer 67 is fitted into the protruding portion, and a retaining pin 68 is further inserted, so that the arm portion 61a is prevented from being detached from the pivot shaft 63. . Further, a cam 81 described later is integrally formed with the base end portion 61a2.
[0049]
The output arm 62, which is also a sector gear, has an arm portion 62 a in which a tooth portion 62 c that meshes with a tooth portion 72 c of the driving arm 72 is formed at the tip end portion 62 a 1, and the arm portion 62 a so that it can rotate integrally with the arm portion 62 a. And a pivot shaft 63 as a welded pivot. The pivot shaft 63 is provided on the holder 55 and has a fixed pivot portion 69 formed of a boss 55 a formed with a through hole 55 a 1 into which an intermediate portion of the pivot shaft 63 is inserted. The lower end portion is pivotally supported by an immovable pivotal support portion 70 formed of a portion that forms a recess into which the lower end portion is rotatably inserted.
[0050]
The arm portion 62 a is accommodated together with the drive arm 72 in a space formed by the mount case 6 and the pump body 56 of the oil pump below the holder 55. The pivot shaft 63 fixed to the base end portion 62a2 of the arm portion 62a is pivotally supported by the pivotal support portion 70 at the lower end portion, and is formed between the pump body 56, the crankcase 4b, and the cylinder block 4a upward. The boss 55 a extends outside the flywheel chamber 57 in which the flywheel 13 is accommodated and is kept oil-tight by the oil seal 71, and is connected to the input arm 61.
[0051]
As described above, the input arm 61 and the output arm 62 are rotatable about the stationary rotation center line L4 that is also the central axis of the pivot shaft 63 that is pivotally supported by the pivot support portions 69 and 70. is there. Therefore, the arm mechanism composed only of the input arm 61 and the output arm 62 having the pivot shaft 63 as a common supported portion is pivotally supported by both the pivot portions 69 and 70 and around the rotation center line L4. Rotate together. The arm portion 61 a of the input arm 61 is connected to the upper portion of the pivot shaft 63, and the arm portion 62 a of the output arm 62 is connected to the lower portion of the pivot shaft 63.
[0052]
Referring to FIG. 2, the rotation center line L4 is radially outward of the flywheel 13 and ahead of the shift rod center axis L5 (here, coincides with the turning center line L3). Thus, it is located closer to the first pin 43 than the reference plane H. Further, the position of the rotation center line L4 is, in plan view, with respect to the first half line L6 extending from the rotation center line L4 toward the center axis L5 of the shift rod 30, and from the rotation center line L4 to the second pin 44. The angle α formed with the second half line L7 extending toward the rotation center line L8 (see FIG. 5) of the input arm 61 is set to be a minor angle greater than 90 ° or 180 °.
[0053]
Depending on the position of the pivot shaft 63, the angle α is determined so that the input arm 61 in a state corresponding to the neutral position of the forward / reverse switching device 15 has the second half-line L7 and the operation cable C orthogonal or almost perpendicular to each other in plan view. It is set so as to occupy a position that is orthogonal to each other. As a result, the magnitude of the operation load when the operation cable C is pushed forward and the operation load when the operation cable C is pulled and retracted is substantially equal.
[0054]
Referring to FIGS. 2, 3, and 5, the drive arm 72 rotates via a bearing 73 to an arm portion 72 a having a tooth portion 72 c formed at a tip end portion 72 a 1 and a support portion 6 a provided on the mount case 6. And a shaft portion 72b that is movably supported. The shift rod 30 and the drive arm 72 are connected to the lower portion of the shaft portion 72b so that the upper end portion of the shift rod 30 is spline-fitted so as to be integrally rotatable.
[0055]
Referring to FIGS. 2 to 4, in addition to the input arm 61 being pivotally supported on the holder 55, a neutral switch 80 for detecting the neutral position of the forward / reverse switching device 15 and an operating mechanism for operating the neutral switch 80 are provided. It is attached.
[0056]
The neutral switch 80 is a limit switch that is turned on / off when the projecting operating piece 80a is linearly moved back and forth by an operating arm 82 described later. The neutral switch 80 is attached to a stay 74 that is positioned by the insertion of a pin 55c formed on the holder 55 and fixed to the holder 55 by a bolt B4.
[0057]
The operating mechanism includes a cam 81 formed on the input arm 61, an operating arm 82 that is pivotally supported by the holder 55 and driven by the cam 81, and operates so that the operating arm 82 contacts the cam 81. And a spring 83 for urging the arm 82. Referring also to FIG. 6, since the cam 81 rotates integrally with the input arm 61, the cam 81 rotates about the rotation center line L9 in synchronization with the rotation of the shift rod 30, and the rotation center. The operating arm 82 that rotates about the line L9 is rotated. The cam 81 is provided with a neutral switch 80 at the forward position in the rotational direction of the cam 81 in order to create a click feeling so that the driver can recognize that the forward position or the reverse position has changed to the neutral position. A recess 81c is formed between the cam crest 81a for opening and the cam crest 81b for opening the neutral switch 80 in the reverse drive position.
[0058]
The actuating arm 82 is provided with a roller 82a that serves as a contact part with the convex part and the cam 81 for creating a click feeling in cooperation with the cam 81 at one end, and the neutral switch 80 is actuated at the other end. A pressing portion 82b that presses the piece 80a is provided, and a cylindrical portion 82c that is a shaft-like supported portion that is pivotally supported by being fitted to the boss 55b of the holder 55 via the bush 84 is provided in the intermediate portion. The operating arm 82 is secured by a washer 85 fixed by a bolt B5 screwed into the boss 55b.
[0059]
Referring also to FIG. 7, the spring 83 surrounds the cylindrical portion 82 c and is externally fitted to the cylindrical portion 82 c so as to be substantially coaxial with the rotation center line L <b> 9, and its one end 83 a is in the hole of the holder 55. The other end 83 b is locked to the operating arm 82, and the torsion spring force biases the operating arm 82 so that the roller 82 a comes into contact with the cam 81.
[0060]
Referring to FIG. 7, the rotation center line L9 of the operation arm 82 is viewed from the direction in which the rotation center line L9 extends within the movement range of the operation piece 80a in the advance / retreat direction A1 (here, it is a plan view). .), And the amount of displacement of the pressing portion 82b in the forward / backward direction A1 is larger than the amount of displacement in the orthogonal direction A2 orthogonal to the forward / backward direction A1. Therefore, in a state where the operating arm 82 occupies a position corresponding to the neutral position, in a plan view, a half extending in parallel with the advancing / retreating direction A1 from the contact point 86 between the operating piece 80a and the pressing portion 82b on the side where the pressing portion 82b is positioned. The positions of the neutral switch 80 and the rotation center line L9 are set so that an angle β formed between the straight line L10 and the half line L11 extending from the contact point 86 through the rotation center line L9 is, for example, 45 ° to 135 °. Is set.
[0061]
Next, operations and effects of the embodiment configured as described above will be described.
Referring to FIG. 2 showing a state in which the shift operation device is at a position corresponding to the neutral position of the forward / reverse switching device 15, the operator operates the operation handle 32 (see FIG. 2) to switch the shift position from the illustrated state to the forward position. 1), the operation force applied to the operation handle 32 acts so as to pull the operation cable C (inner cable 34) passing through the outer pipe 35 outside the outboard motor body 2, and the slider 40 Is guided by the guide groove 42 and moves forward. At the same time, the input arm 61 connected to the operation cable C by the second pin 44 of the slider 40 rotates counterclockwise, and the output arm 62 that rotates integrally with the input arm 61 rotates counterclockwise in the same manner. Move. By this rotation of the output arm 62, the drive arm 72 meshing with the output arm 62 is rotated clockwise, and the shift rod 30 is rotated together with the drive arm 72 in the clockwise direction, and the shifter 17a (see FIG. 1). ) Moves forward, the clutch element 17b engages with the forward gear 16b, and the forward / reverse switching device 15 occupies the forward position.
[0062]
In the process of changing the shift position from the neutral position to the forward position, the cam 81 rotates counterclockwise integrally with the input arm 61, and the roller 82a of the operating arm 82 comes off the recess 81c and contacts the cam crest 81a. Touch. At this time, the operating arm 82 rotates counterclockwise around the rotation center line L9 against the spring force of the spring 83, and the pressing portion 82b rotates away from the neutral switch 80. Correspondingly, as shown by a two-dot chain line in FIG. 7, the operating piece 80a moves so as to advance, and the neutral switch 80 is turned off.
[0063]
In order to switch from the forward position to the neutral position, the operating force applied by the operator to the operating handle 32 acts so as to push the operating cable C, the slider 40 moves backward, and the input arm 61 and the output arm 62 are turned to the clock. Rotate in the direction. By this rotation of the output arm 62, the drive arm 72 and the shift rod 30 are rotated counterclockwise, the shifter 17a is moved rearward, and the forward / reverse switching device 15 occupies the neutral position.
[0064]
At the time of changing from the forward position to the neutral position, the cam 81 rotates clockwise, and the roller 82a moves the cam mountain 81a toward the recess 81c. Then, at a position corresponding to the neutral position, the roller 82a that has moved from the cam crest 81a engages with the recess 81c. At this time, the operating arm 82 is urged by the spring force of the spring 83 and rotates clockwise about the rotation center line L9, so that a click feeling is given to the driver when the roller 82a and the recess 81c are engaged. At the same time, the pressing portion 82b pushes the operating piece 80a backward to turn on the neutral switch 80.
[0065]
Further, when the shift position is switched to the reverse position from the state shown in FIG. 2, the operating force applied to the operation handle 32 by the operator acts to push the operation cable C, and the slider 40 is moved. It is guided by the guide groove 42 and moves backward. At the same time, the input arm 61 and the output arm 62 rotate integrally in the clockwise direction. By this rotation of the output arm 62, the drive arm 72 and the shift rod 30 are rotated together in the counterclockwise direction, the shifter 17a (see FIG. 1) is moved backward, and the clutch element 17b is moved to the forward gear 16b. The forward / reverse switching device 15 occupies the reverse position.
[0066]
In the process of changing the shift position from the neutral position to the reverse position, the cam 81 rotates clockwise, and the roller 82a comes out of the recess 81c and comes into contact with the cam crest 81b. At this time, the operating arm 82 rotates counterclockwise around the rotation center line L9 against the spring force of the spring 83, and the pressing portion 82b rotates away from the neutral switch 80. As indicated by a two-dot chain line in FIG. 7, the operating piece 80a moves so as to advance, and the neutral switch 80 is turned off.
[0067]
Further, when changing from the reverse position to the neutral position, as in the case of changing from the forward position to the neutral position, when the roller 82a is engaged with the recess 81c, the driver is given a click feeling, and at the same time, the neutral switch 80 is Turn on.
[0068]
As described above, the transmission mechanism 60 is the arm mechanism that is pivotally supported by both pivotal support portions and integrally rotates about the rotation center line L4, and thus the operation force transmitted from the operation cable C is obtained. Since the play in the transmission path of the operating force in the transmission mechanism 60 that transmits to the drive arm 72 that drives the shift rod 30 can be eliminated, the transmission mechanism 60 can be prevented from being displaced between the rotating members. Thus, the shift operation feeling is improved. In addition, the arm mechanism rotates around the stationary rotation center line L4, so that the translation mechanism does not move and the movement range of the transmission mechanism 60 is reduced. Therefore, the transmission mechanism 60 is made compact, It becomes possible to arrange the transmission mechanism 60 in a narrow space.
[0069]
The arm mechanism includes only an input arm 61 and an output arm 62 that are connected to each other via a pivot shaft 63 so as to be integrally rotatable. The input arm 61 is connected to an operation cable C, and the output arm 62 is a drive arm 72. Are connected to each other so that the arm portion 61a of the input arm 61 and the arm portion 62a of the output arm 62 are arranged at different positions in the vertical direction, or both arms in the circumferential direction centered on the rotation center line L4. Since the relative arrangement of the arm portions 61a and 62a can be easily changed, a flexible transmission mechanism 60 that can be adapted to various types of spaces can be obtained. The degree of freedom increases.
[0070]
The input arm 61 and the operation cable C have a long hole 64 that allows the operation cable C to move in a substantially straight line over the entire rotation range of the input arm 61 in the engine room 10. With respect to the operation cable C that extends in the engine room 10, the operation cable C does not rotate about the first pin 43, and substantially extends over the entire rotation range of the input arm 61. Since it moves on a straight line, it is prevented that the operation cable C is bent when the operation cable C is pushed and pulled according to the operation force, and an increase in the operation resistance of the operation cable C due to such bending is avoided. Therefore, the lightness of the shift operation is improved.
[0071]
The transmission mechanism 60 includes an input arm 61 and an output arm 62, and the output arm 62 is rotatable about a stationary rotation center line L 4. The rotation center line L 4 is first than the reference plane H. By being positioned closer to the pin 43, the distance between the rotation center line L4 and the first pin 43 becomes smaller than the distance between the reference plane H and the first pin 43, and the transmission mechanism 60 is Since it becomes compact, it becomes possible to arrange | position the transmission mechanism 60 in a narrow space, and also enlargement of the outboard motor main body 2 is prevented.
[0072]
In plan view, the angle α formed by the first half-line L6 and the second half-line L7 is an inferior angle greater than 90 ° or 180 °, and the operation cable C is connected to the first pin 43 in the outboard motor body 2. Further, the outer cover 8 passes through the outer pipe 35 fixed to the bracket 28 provided in front of and above the tilt center line L2 and passes through the under cover 8 from the front of the under cover 8 to the engine room 10 which is the inside thereof. By extending, the distance in the front-rear direction between the rotation center line L4 and the shift rod 30 is reduced, and the rotation center line L4 is positioned closer to the shift rod 30 in the front-rear direction. Without moving the pipe 37 forward, it is possible to secure a distance between the first pin 43 and the bracket for securing the required stroke length of the operation cable C to be pushed and pulled. Kill. Therefore, even when the tilt angle is increased, the outer pipe 35 and the inner cable 34 are not greatly bent in front of the outboard motor main body 2, and the operation cable due to the increase in sliding resistance of the inner cable 34 due to the bending. Since an increase in the operation resistance of C is avoided, the lightness of the shift operation is improved.
[0073]
The operation cable C is connected to the input arm 61 of the transmission mechanism 60 via the slider 40, and the second pin 44 is positioned closer to the bracket than the first pin 43, so that the first pin 43 and the bracket 28 are connected. Since the required stroke length to be pushed and pulled is ensured without moving the position of the bracket 28 forward, the outboard motor main body can be increased even when the tilt angle increases. Since the inner cable 34 is not greatly bent in front of 2 and the operation resistance of the operation cable C is prevented from increasing, the lightness of the shift operation is improved. In addition, the second pin 44 is not uniquely determined by the position of the first pin 43, and the interval between the two pins can be changed. Therefore, the second pin 44 can be adapted to various types of spaces including a narrow space. Therefore, the degree of freedom of arrangement of the transmission mechanism 60 is increased.
[0074]
The slider 40 is guided in a guide groove 42 of the bracket 41 fixed to the crankcase 4b by sliding substantially parallel to the operation cable C, so that the slider 40 follows the operation force transmitted from the operation cable C. Therefore, the sliding resistance between the bracket and the slider 40 is reduced, and the operation load of the operation cable C is reduced. Therefore, the lightness of the shift operation is further improved.
[0075]
The input arm 61 includes the pivot shaft 63 having the stationary rotation center line L4, so that the second pin 44 is connected to the input arm 61 having the stationary rotation center line L4 regardless of the position of the first pin 43. Can be set according to the position of the rotation center line L4, so that the position of the input arm 61 can be set to the optimum position from the viewpoint of the length of the arm portion of the input arm 61 and the operation load when the operation cable C is pushed and pulled. Two pins 44 can be arranged.
[0076]
The input arm 61 in a state corresponding to the neutral position of the forward / reverse switching device 15 is set so as to occupy a position where the second half line L7 and the operation cable C are orthogonal or almost orthogonal in plan view. As a result, the magnitude of the operating load when the operating cable C is pushed forward and the magnitude of the operating load when the operating cable C is pulled back is almost equal. Will improve.
[0077]
The rotation center line L9 of the actuating arm 82 has a displacement amount in the advancing / retreating direction A1 of the pressing portion 82b in a moving range in the advancing / retreating direction A1 of the actuating piece 80a larger than the displacement amount in the orthogonal direction A2 in plan view. The increased position reduces the amount of rotation of the operating arm 82 for operating the neutral switch 80, and the position of the rotation center line L9 of the operating arm 82 is not constrained by the forward / backward direction A1 of the operating piece 80a. Since the degree of freedom of arrangement of the neutral switch 80 is increased, the shift operation device can be made compact, and the neutral switch 80 can be arranged in a narrow space in the engine room 10.
[0078]
The operating mechanism includes a cam 81 that rotates the operating arm 82 in synchronization with the shift rod 30, an operating arm 82, and a spring 83 that biases the operating arm 82 to contact the cam 81, and is in a neutral position. The spring 83 for creating a click feeling is obtained by simply engaging the concave portion 81 c provided in the cam 81 with the roller 82 a that is the convex portion of the operating arm 82 so that the operating arm 82 contacts the cam 81. Since the position of the neutral switch 80 can be increased, the shift operation device can be made compact, so that the neutral switch can be installed in a narrow space in the engine room 10. 80 can be arranged. Further, since the click feeling is created by the engagement of the roller 82a of the operation arm 82 and the recess 81c of the cam 81, the operation arm 82, which is a single member, operates the neutral switch 80 and the click feeling. Since creation is performed, the occurrence of deviation between the neutral position detection timing of the neutral switch 80 and the click feeling at the neutral position is prevented.
[0079]
When the spring 83 is externally fitted to the shaft-like pivoted support portion of the operating arm 82, the spring 83 is disposed so as to surround the cylindrical portion 82c of the operating arm 82 and is compactly disposed around the rotation center line L9. Therefore, the shift operation device becomes compact.
[0080]
When the operation arm 82 moves from the neutral position to the forward movement position and the reverse movement position, the operation arm 82 rotates in the same direction from the neutral position, so that the operation arm 82 rotates in both rotation directions from the neutral position. Since the rotation range can be reduced, the shift operation device can be made compact.
[0081]
Hereinafter, an example in which a part of the configuration of the above-described embodiment is changed will be described with respect to the changed configuration.
The transmission mechanism 60 may be composed of a plurality of arm mechanisms, and the arm mechanisms may be connected via an arm having teeth that mesh with each other. Further, the input arm 61 and the output arm 62 that can rotate integrally may be pivotally supported by a shaft portion provided in the outboard motor main body 2.
[0082]
Although the output arm 62 and the drive arm 72 are constituted by sector gears that mesh with each other, the arms 62 and 72 may be connected by pins. The shift rod 30 may be of a type in which the shift position is switched by being driven in the axial direction or the vertical direction by a drive member engaged with the shift rod 30.
[0083]
In order to create a click feeling, the operating arm 82 has a convex portion and the cam 81 has a concave portion 81c. However, the operating arm 82 has a concave portion and the cam 81 has a convex portion that engages with the concave portion. It may be formed.
[0084]
The connection structure may include a slider in which a long hole is formed and a pin that is provided on the input arm and fits in the long hole.
[Brief description of the drawings]
FIG. 1 is a schematic right side view of an outboard motor to which a shift operation device is applied according to an embodiment of the present invention.
2 is a plan view and a partial cross-sectional view of a main part of a shift operating device in an engine room of the outboard motor of FIG. 1. FIG.
FIG. 3 is an exploded perspective view of the shift operation device of FIG. 2;
4 is a cross-sectional view taken along the arrow IVa-IVa in FIG. 2, and a part thereof is a cross-sectional view taken along the arrow IVb-IVb.
5 is a cross-sectional view taken along the line Va-Va in FIG. 2, and a part of the bracket is a cross-sectional view taken along the line Vb-Vb.
6 is a perspective view from below of the arm portion of the input arm of the shift operating device of FIG. 2; FIG.
FIG. 7 is an enlarged view of a main part of FIG.
[Explanation of symbols]
DESCRIPTION OF SYMBOLS 1 ... Outboard motor, 2 ... Outboard motor main body, 3 ... Support apparatus, 4 ... Engine main body, 5 ... Crankshaft, 6 ... Mount case, 7 ... Oil case, 8 ... Under cover, 9 ... Engine cover, 10 ... Engine room, 11 ... extension case, 12 ... gear case, 13 ... flywheel, 14 ... drive shaft, 15 ... forward / reverse switching device, 16 ... gear mechanism, 17 ... clutch mechanism, 18 ... propeller shaft, 19 ... propeller, 20 ... Stern bracket, 21 ... tilt shaft, 22 ... swivel case, 23 ... mount frame, 24, 25 ... mount rubber, 26 ... Bowden cable, 27 ... grommet, 28 ... bracket, 30 ... shift rod, 31 ... remote control device, 32 ... Operation handle, 33 ... Bowden cable, 34 ... Inner cable, 35 ... Outer pipe, 36 ... Locking tool, 37 ... Plan Pipe, 38 ... Connecting rod, 39a, 39b ... Seal member, 40 ... Slider, 41 ... Bracket, 42 ... Guide groove, 43, 44 ... Pin, 45 ... Retaining plate, 46 ... Retaining ring, 47 ... Locking tool, 48 ... Lock nut, 49 ... Throttle arm, 50 ... Operation cable, 51 ... Pin, 52 ... Link, 53 ... Bell crank, 54 ... Rod, 55 ... Holder, 56 ... Pump body, 57 ... Flywheel chamber, 60 ... Transmission Mechanism: 61 ... Input arm, 62 ... Output arm, 63 ... Pivot shaft, 64 ... Elongated hole, 66 ... Through hole, 67 ... Washer, 68 ... Retaining pin, 69,70 ... Pivot, 71 ... Oil seal, 72 ... Drive arm, 73 ... Bearing, 74 ... Stay, 80 ... Neutral switch, 81 ... Cam, 82 ... Operating arm, 83 ... Spring, 84 ... Bush, 85 ... Washer 86 ... the contact point,
E ... Internal combustion engine, P ... Propulsion unit, S ... Hull, L1 ... Rotation center line, L2 ... Tilt center line, L3 ... Steering center line, L4, L9 ... Rotation center line, L5 ... Center axis, L6, L7 , L10, L11 ... half straight line, L8 ... center line, B1 to B5 ... bolt, H ... reference plane, C ... operation cable, α, β ... angle, A1 ... forward / backward direction, A2 ... orthogonal direction.

Claims (3)

A shift operation device for an outboard motor, an operation cable for transmitting an operation force applied to an operation member provided outside the outboard motor main body, and a shift rod for switching the shift position of the forward / reverse switching device of the propulsion unit A drive member that engages the shift rod to drive the shift rod or is connected to the shift rod so as to be integrally rotatable, and is connected to the operation cable to transmit the operation force to the drive member. In a shift operation device comprising a transmission mechanism,
The shift operation device according to claim 1, wherein the transmission mechanism is an arm mechanism that is pivotally supported by a pivotal support portion provided in the outboard motor main body and integrally rotates about a stationary rotation center line. The arm mechanism includes only an input arm and an output arm that are connected to each other so as to be integrally rotatable, the input arm is connected to the operation cable, and the output arm is connected to the driving member. The shift operation device according to claim 1. The input arm and the operation cable have a long hole that allows the operation cable to move in a substantially straight line over the entire rotation range of the input arm inside the outboard motor main body. The shift operation device according to claim 2, wherein the shift operation device is connected by a connection structure.

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