JP2018030458A - Outboard engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an outboard engine comprising a gear shifter that includes a mechanism for switching rotary output from propellers to forward and backward movement and nonetheless has a simple configuration and can be downsized.SOLUTION: The outboard engine is provided that comprises a gear shifter 13 arranged between an engine 11 and a lower gear mechanism 12. The gear shifter 13 comprises a forward movement shaft 23 and a backward movement shaft 24 which are vertically long and aligned in parallel to each other. Forward movement gears 28, 29, forward movement clutches 27, 30 for connecting/disconnecting power transmission to the forward movement gears 28, 29 and a backward movement relay gear 31 are arranged in the forward movement shaft 23. A backward movement gear 36 and a backward movement clutch 37 for connecting/disconnecting a power transmission to the backward movement gear 36 are arranged in the backward movement shaft 24. A power from the input shaft 14 through the forward movement shaft 23 is transmitted as a forward movement output to the output shaft 15 through the forward movement gears 28, 29. A power from the input shaft 14 through the backward movement shaft 24 is transmitted to the output shaft 15 through the backward movement gear 36 and a backward relay gear 31.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an outboard motor in which a transmission is disposed between an engine and a lower gear mechanism for driving a propeller.

  Conventionally, outboard motors are known in which a transmission is arranged between an engine and a lower gear mechanism for driving a propeller (see, for example, Patent Documents 1 to 3).

JP 2011-110968 A International Publication No. 2007/7707 JP 2009-185972 A

  However, in the outboard motor of Patent Document 1, a forward / reverse switching mechanism capable of switching the rotation output of the propeller between forward and reverse is provided in the lower gear mechanism separately from the transmission, so the outboard motor There was a problem of causing an increase in size. Further, in the outboard motors of Patent Documents 2 and 3, although the forward / reverse switching mechanism is provided in the transmission, the forward / backward switching mechanism using the planetary gear mechanism is adopted, so that the structure is complicated and the speed change is performed. In addition to incurring an increase in the size of the apparatus, there is a problem that the cost increases.

  An object of the present invention is to provide an outboard motor that has been improved by examining the current situation as described above.

  The present invention includes an engine, a lower gear mechanism for driving a propeller disposed below the engine, a transmission device disposed between the engine and the lower gear mechanism, and power transmission from the engine to the transmission device. In an outboard motor including an input shaft and an output shaft that transmits power from the transmission to the lower gear mechanism, the transmission includes a vertically long forward shaft and a reverse shaft, which are arranged in parallel. A forward gear, a forward clutch that interrupts power transmission to the forward gear, and a reverse relay gear are arranged, and a reverse gear that reverses power transmission to the reverse gear is provided on the reverse shaft. A power is transmitted from the input shaft via the forward shaft to the output shaft as a forward output via the forward gear, and the power via the reverse shaft is transmitted from the input shaft to the reverse shaft. With gear Via the serial reverse relay gear is that is configured to transmit to the output shaft.

  In the outboard motor of the present invention, the forward gear and the reverse relay gear are connected to form a forward / reverse relay gear, and the forward gear and the forward / reverse relay gear are arranged between the forward shaft and the forward / reverse relay gear. A one-way clutch configured to transmit a forward output from the shaft to the forward / reverse relay gear but not to transmit the forward output on the contrary may be arranged.

  Furthermore, in the outboard motor of the present invention, the forward gear is configured to be separated into a forward low-speed gear and a forward high-speed gear, and the forward clutch forwards the power transmission from the input shaft to the forward shaft. A low-speed clutch and a forward high-speed clutch that cuts off power transmission from the forward shaft to the forward high-speed gear are configured separately, and the forward low-speed gear and the reverse relay gear are connected to each other, and the forward and reverse relay gear You may make it.

  In the outboard motor of the present invention, a hydraulic pump may be connected to at least one of the input shaft and the reverse shaft.

  In the outboard motor of the present invention, the propeller may be configured as a counter-rotating propeller in which a front propeller and a rear propeller are arranged in series and are driven to rotate in directions opposite to each other.

  According to the present invention, an engine, a lower gear mechanism for driving a propeller disposed below the engine, a transmission disposed between the engine and the lower gear mechanism, and power transmission from the engine to the transmission And an output shaft that transmits power from the transmission to the lower gear mechanism.The transmission includes a vertically long forward shaft and a reverse shaft arranged in parallel. Includes a forward gear, a forward clutch that interrupts power transmission to the forward gear, and a reverse relay gear, and the reverse gear on the reverse shaft and power transmission to the reverse gear are interrupted. A reverse clutch is disposed, and the power passing through the forward shaft from the input shaft is transmitted as the forward output to the output shaft via the forward gear, and the power passing through the reverse shaft from the input shaft is Reverse Since the transmission is configured to transmit to the output shaft via the reverse relay gear, the transmission includes a mechanism for switching the rotation output of the propeller between forward and reverse. Can be made simple, small and inexpensive. As a result, it contributes to downsizing of outboard motors.

  In addition, when all the clutches are in the neutral state, the forward shaft and the reverse shaft are each rotated by the rotational power of the engine. According to the configuration of the present invention, the forward shaft is directed to the output shaft. Since the rotating rotation direction and the rotating rotation direction from the reverse shaft toward the output shaft are opposite to each other, the mutual rotation force is canceled out. Therefore, even if all the clutches are in a neutral state, there is no possibility that the output shaft is inadvertently rotated.

It is a schematic side view of the outboard motor in the embodiment. It is a skeleton figure which shows the power transmission system of an outboard motor. It is a side view which shows the internal structure of a transmission. It is a plane sectional view showing the internal structure of a transmission. FIG. 5 is a cross-sectional view taken along line AA in FIG. 4. It is a hydraulic circuit diagram of an outboard motor. It is sectional drawing explaining the operation | movement aspect of a one-way clutch, (a) is at the time of advance low speed, (b) is a figure at the time of forward high speed. FIG. 5 is a cross-sectional view taken along line B-B in FIG. 4.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments embodying the present invention will be described with reference to the drawings.

  First, an outline of the outboard motor 1 will be described with reference to FIG. As shown in FIG. 1, the outboard motor 1 includes an engine cover 2, an intermediate housing 3, and a lower unit case 4 in order from the upper side. These constitute the casing (exterior) of the outboard motor 1. A front propeller 5 and a rear propeller 6 are arranged in series on the rear side of the lower unit case 4 as propellers of the outboard motor 1. The front and rear propellers 5 and 6 are configured as counter-rotating propellers that are driven to rotate in opposite directions. A bracket device 7 for supporting the outboard motor 1 on the hull (not shown) is provided on the front side of the intermediate housing 3. The outboard motor 1 is attached to a stern board or the like of the hull via a bracket device 7. In general, the outboard motor 1 is connected to the bracket device 7 so as to be turnable in the left-right direction. The bracket device 7 is connected to a stern plate or the like of the hull so as to be rotatable up and down.

  The outboard motor 1 of the embodiment is disposed between an engine 11 as a drive source, a lower gear mechanism 12 for driving front and rear propellers 5 and 6 disposed below the engine 11, and the engine 11 and the lower gear mechanism 12. The transmission 13, the input shaft 14 that transmits power from the engine 11 to the transmission 13, and the output shaft 15 that transmits power from the transmission 13 to the lower gear mechanism 12 are provided.

  The engine 11 is mounted inside the engine cover 2. The engine 11 of the embodiment is a vertical water-cooled engine in which a crankshaft (not shown) that is an engine output shaft is vertically oriented. The lower gear mechanism 12 is accommodated in the lower unit case 4. A horizontally long propeller shaft 16 that rotatably drives the front and rear propellers 5 and 6 is rotatably supported on the lower unit case 4. The transmission 13 is accommodated in the intermediate housing 3. The transmission 13 according to the embodiment switches a function of shifting the rotational power of the engine to a plurality of stages (in this case, two stages of forward low speed and forward high speed) and the rotational output of the front and rear propellers 5 and 6 to forward and reverse. With functionality.

  The upper end side of the input shaft 14 is connected to the crankshaft of the engine 11. The lower end side of the input shaft 14 is pivotally supported by projecting into a transmission case 22 (see FIG. 2) that constitutes the transmission 13. The upper end side of the output shaft 15 protrudes into the transmission case 22 and is pivotally supported. The lower end side of the output shaft 15 is connected to the lower gear mechanism 12. The input shaft 14 and the output shaft 15 are vertically long and are coaxially positioned. The rotational power of the engine 11 is transmitted to the front and rear propellers 5 and 6 via the input shaft 14, the transmission 13, the output shaft 15, the lower gear mechanism 12 and the propeller shaft 16.

  As shown in FIG. 2, the lower gear mechanism 12 includes a drive bevel gear 17 fixed to the lower end side of the output shaft 15 and a pair of front and rear driven bevel gears 18 and 19 that always mesh with the drive bevel gear. On the other hand, the propeller shaft 16 has a horizontally long concentric double shaft structure with an inner shaft 20 and an outer cylinder shaft 21 that are rotatable in opposite directions (see FIG. 2). A first driven bevel gear 18 is fixed to the front end side of the inner shaft 20, and a second driven bevel gear 19 is fixed to the front end side of the outer cylinder shaft 21. The rear end sides of the inner shaft 20 and the outer cylinder shaft 21 protrude rearward from the lower unit case 4. The front propeller 5 is attached to the rear projecting end side of the outer cylindrical shaft 21, and the rear propeller 6 is attached to the rear projecting end side of the inner shaft 20.

  The rotational power of the output shaft 15 is transmitted from the drive bevel gear 17 to both the first driven bevel gear 18 and the second driven bevel gear 19. The first driven bevel gear 18 and the second driven bevel gear 19 rotate in opposite directions due to the meshing relationship with the drive bevel gear 17. Therefore, the inner shaft 20 and the outer cylinder shaft 21, and thus the front propeller 5 and the rear propeller 6 are rotationally driven in opposite directions.

  Next, the internal structure of the transmission 13 and the power transmission system will be described with reference to FIGS. In addition, in FIG. 3, illustration of the clutch pump 40 and the cooling water pump 41 which are mentioned later is abbreviate | omitted. On the upper plate portion of the transmission case 22, the lower end side of the input shaft 14 is rotatably supported, while the lid member 22 a that forms the lower plate portion of the transmission case 22 has an upper end side of the output shaft 15. It is pivotally supported. In a transmission case 22 of the transmission 13, a vertically long forward shaft 23 and a reverse shaft 24 are rotatably supported in parallel. Therefore, the input / output shafts 14, 15, the forward shaft 23, and the reverse shaft 24 that are coaxially extend in a longitudinal direction in parallel with each other. Further, the input / output shafts 14 and 15, the forward shaft 23, and the reverse shaft 24 are in a positional relationship so as to form a substantially triangular vertex in plan sectional view (see FIG. 4).

  In order from the upstream side, the forward shaft 23 is connected to a forward input gear 26 that is connected to a wet multi-plate forward low-speed clutch 27 so that the power can be disconnected, and a wet multi-plate forward high-speed clutch 30 is capable of power disconnection. The forward high-speed gear 29 to be connected and the forward / reverse relay gear 32 formed by connecting the forward low-speed gear 28 and the reverse relay gear 31 are loosely fitted. The forward input gear 26 is always meshed with an input branch gear 25 fixed to the lower end side of the input shaft 14. The forward low speed clutch 27 interrupts power transmission from the input shaft 14 to the forward shaft 23, and the forward high speed clutch 30 interrupts power transmission from the forward shaft 23 to the forward high speed gear 29. . The lower ends of the forward shaft 23 and the reverse shaft 24 penetrate the lid member 22a and are covered with an oil passage inheriting member 22b. Oil passage ports 22a, 30a, 37a are opened in the oil passage transfer member 22b and connected to a hydraulic circuit 100, which will be described later, and are connected to the clutches 27, 30, 37 through the oil passages in the forward shaft 23 and the reverse shaft 24. Refueling is possible. Further, the oil flowing through the oil supply port 51 a is discharged toward the friction plates of the clutches 27, 30 and 37 of the forward shaft 23 and the reverse shaft 24.

  The forward low-speed gear 28 that is a component of the forward / reverse relay gear 32 is always meshed with the forward / reverse output gear 38 fixed to the upper end side of the output shaft 15. Further, the forward high-speed gear 29 is always meshed with the forward high-speed output gear 39 fixed to the upper end side of the output shaft 15. The forward low speed clutch 27 and the forward high speed clutch 30 correspond to the forward clutch, and the forward low speed gear 28 and the forward high speed gear 29, which are components of the forward / reverse relay gear 32, correspond to the forward gear.

  Between the forward shaft 23 and the forward / reverse relay gear 32, a one-way clutch 33 configured to transmit forward output from the forward shaft 23 to the forward / reverse relay gear 32 but not to transmit the forward output on the contrary. doing. The one-way clutch 33 of the embodiment is a sprag type.

  In this case, when only the forward low-speed clutch 27 is connected from the neutral state and the forward shaft 23 is rotated in the forward output direction, the forward / reverse relay gear 32 side is not driven, so the forward shaft 23 and the forward / reverse relay gear 32 are driven. The sprag 34 group between the forward and reverse relay gears 32 and 32 is raised, and a large frictional force is generated between the raceway surfaces of the forward shaft 23 and the forward / reverse relay gear 32 and the sprag 34 group. (See FIG. 7A). As a result, the forward low speed output is transmitted from the forward shaft 23 to the forward / reverse output gear 38 via the forward low speed gear 28.

  When both the forward low speed clutch 27 and the forward high speed clutch 30 are connected, the forward / reverse output gear 38 changes to the forward / reverse relay gear 32 due to the gear ratio between the forward high speed output gear 39 and the forward / reverse output gear 38. The power with the same rotational direction is transmitted at a higher speed than the forward shaft 23. For this reason, the contact surface pressure between the raceway surface of each of the forward shaft 23 and the forward / reverse relay gear 32 and the sprag 34 group is reduced, the frictional force is reduced, and both the forward shaft 23 and the forward / reverse relay gear 32 are combined. In this state, the wheels are idled (see FIG. 7B).

  When a reverse clutch 37 (to be described later) is connected and the reverse shaft 24 is rotated in the reverse output direction, a reverse output is transmitted from the reverse gear 36 to the reverse relay gear 31, and the forward shaft 23 and the forward / reverse relay gear 32 are connected. The sprag 34 group in the meantime rises, and the forward / reverse relay gear 32 rotates integrally with the forward shaft 23. However, when the reverse clutch 37 is connected, both the forward low speed clutch 27 and the forward high speed clutch 30 are in the disconnected state, so that the forward input gear 26 and the forward high speed gear 29 are not affected.

  A reverse input gear 35 that always meshes with the input branch gear 25 and a reverse gear 36 that is connected by a wet multi-plate reverse clutch 37 so as to be capable of power transmission / disconnection are disposed on the reverse shaft 24 in order from the upstream side. The reverse input gear 35 is fixed to the reverse shaft 24, and the reverse gear 36 is loosely fitted to the reverse shaft 24. The reverse clutch 37 interrupts power transmission from the reverse shaft 24 to the reverse gear 36. The reverse gear 36 is always meshed with the reverse relay gear 31 that is a component of the forward / reverse relay gear 32 loosely fitted to the forward shaft 23.

  The forward low speed clutch 27, the forward high speed clutch 30 and the reverse clutch 37 are all wet multi-plate hydraulic friction clutches. By bringing the friction plates of the clutches 27, 30, and 37 into pressure contact with each other with the operating hydraulic pressure, the input shaft 14 and the output shaft 15 are coupled so as to be able to transmit power.

  That is, when only the forward low-speed clutch 27 is connected and the forward high-speed clutch 30 and the reverse clutch 37 are disconnected, the forward input gear 26 is coupled to the forward shaft 23 through the forward low-speed clutch 27 so as not to be relatively rotatable. Accordingly, the rotational power of the engine 11 is transmitted from the input branch gear 25 of the input shaft 14 to the forward shaft 23 via the forward input gear 26, and from the forward shaft 23 via the one-way clutch 33 and the forward / reverse relay gear 32. It is transmitted to the forward / reverse output gear 38 as a forward low speed output. As a result, the transmission 13 enters a forward low speed state in which the rotational power of the engine 11 is transmitted to the output shaft 15 as a forward low speed output.

  When the forward low-speed clutch 27 and the forward high-speed clutch 30 are simultaneously connected and the reverse clutch 37 is disconnected, the forward input gear 26 is connected to the forward shaft 23 via the forward low-speed clutch 27 so as not to be relatively rotatable, and the forward high-speed gear. 29 is also connected to the forward shaft 23 through the forward high-speed clutch 30 so as not to be relatively rotatable. Accordingly, the rotational power of the engine 11 is transmitted from the input branch gear 25 of the input shaft 14 to the forward shaft 23 via the forward input gear 26, and from the forward shaft 23 to the forward high-speed output gear 39 via the forward high-speed gear 29. Transmitted as forward high speed output. As a result, the transmission 13 enters a forward high speed state in which the rotational power of the engine 11 is transmitted to the output shaft 15 as a forward high speed output.

  Further, when the forward low speed clutch 27 and the forward high speed clutch 30 are disconnected and only the reverse clutch 37 is connected, the reverse gear 36 is connected to the reverse shaft 24 through the reverse clutch 37 so as not to be relatively rotatable. Therefore, the rotational power of the engine 11 is transmitted from the input branch gear 25 of the input shaft 14 to the reverse shaft 24 via the reverse input gear 35, and forward and backward from the reverse shaft 24 via the reverse gear 36 and the forward / reverse relay gear 32. It is transmitted to the reverse output gear 38 as a reverse output. As a result, the transmission 13 enters a reverse state in which the rotational power of the engine 11 is transmitted to the output shaft 15 as a reverse output.

  When all of the forward low speed clutch 27, the forward high speed clutch 30, and the reverse clutch 37 are disconnected, the output shaft 15 is in a neutral state in which the rotational power of the engine 11 is not transmitted.

  In summary, the rotational power from the input shaft 14 via the forward shaft 23 is transmitted as forward output (forward low-speed or forward high-speed output) to the output shaft 15 via the forward / reverse relay gear 32 or the forward high-speed gear 29. Rotational power from the input shaft 14 via the reverse shaft 24 is transmitted to the output shaft 15 via the reverse gear 36 and the forward / reverse relay gear 32.

  In addition, the rotational speed of the output shaft 15 is detected using the rotational speed detection sensor 42 (see FIG. 2), and the forward low speed clutch 27 and the forward high speed clutch 30 are disconnected from the relationship between the rotational speeds of the engine 11 and the output shaft 15. May be configured to be automatically controlled, or may be configured to be controlled by manual operation of a lever or the like. The disengagement control of the reverse clutch 37 is executed based on manual operation of a lever or the like.

  In the embodiment, the input shaft 14 and the reverse shaft 24 are configured to always rotate with the rotational power while the engine 11 is driven. For this reason, a clutch pump 40 that supplies hydraulic oil to the forward low-speed clutch 27, the forward high-speed clutch 30, and the reverse clutch 37 is connected to the lowermost end portion of the input shaft 14 that is positioned in the transmission case 22 as a hydraulic pump. ing. In this case, the transmission case 22 of the transmission 13 is also used as a hydraulic oil tank, and the hydraulic oil in the transmission case 22 is supplied to the clutch pump 40. Further, the lower end side of the reverse shaft 24 protrudes downward from the lower plate portion of the transmission case, and a cooling water pump 41 that circulates cooling water for cooling the engine 11 is connected to the protruding end portion.

  Therefore, the transmission 13 according to the embodiment also has a power take-out function of driving the auxiliary power such as the clutch pump 40 and the cooling water pump 41, which are auxiliary machines, using the rotational power of the engine 11. Moreover, the transmission 13, the clutch pump 40, and the cooling water pump 41 are integrally assembled into a unit.

  The auxiliary pump includes, for example, a steering hydraulic pump for steering the outboard motor, a tilt / trim hydraulic pump for rotating the outboard motor up and down, and the like. These may be attached to the input shaft 14 in a tandem manner or attached to the reverse shaft 24 in a tandem manner. Of course, it is possible to attach the clutch pump 40 and the cooling water pump 41 to the reverse shaft 24 in a tandem manner.

  Next, the structure of the hydraulic circuit 100 of the outboard motor 1 (transmission device 13) will be described with reference to FIG. The hydraulic circuit 100 of the outboard motor 1 includes a clutch pump 40 that is driven by the rotational power of the engine 11. As described above, the clutch pump 40 supplies hydraulic oil to the forward low speed clutch 27, the forward high speed clutch 30, and the reverse clutch 37. A clutch pump 40 is disposed in the middle of the hydraulic oil passage 44 connected to the speed change case 22 as a hydraulic oil tank. A strainer 43 is disposed on the suction side of the clutch pump 40 in the hydraulic oil passage 44.

  Of the hydraulic oil passage 44, the discharge side of the clutch pump 40 includes a forward low speed oil passage 45 toward the forward low speed clutch 27, a forward high speed oil passage 46 toward the forward high speed clutch 30, and a reverse oil passage 47 toward the reverse clutch 37. It is divided into three sides. In the middle of the forward low speed oil passage 45, a forward low speed solenoid valve 48 for connecting and disconnecting the forward low speed clutch 27 is provided. A forward high speed solenoid valve 49 for connecting and disconnecting the forward high speed clutch 30 is provided in the middle of the forward high speed oil passage 46. A reverse solenoid valve 50 for disengaging the reverse clutch 37 is provided in the middle of the reverse oil passage 47. Depending on the combination of switching operations of the solenoid valves 48 to 50, hydraulic oil is selectively supplied to either the forward low speed clutch 27, both the forward low speed clutch 27 and the forward high speed clutch 30, or the reverse clutch 37.

  From a midway portion of the hydraulic oil passage 44, a lubricating oil passage 51 for injecting hydraulic oil as lubricating oil to the forward low-speed clutch 27, the forward high-speed clutch 30 and the reverse clutch 37 is extended. The lubricating oil passage 51 is provided with, in order from the upstream side, an operating hydraulic pressure adjustment valve 52 that is a relief valve for setting the clutch operating pressure on the hydraulic oil passage 44 side, and a lubricating hydraulic pressure adjustment valve 53. The hydraulic oil that has passed through the hydraulic pressure adjustment valve 52 is cooled and lubricated to the friction plate by the forward low-speed clutch 27, the forward high-speed clutch 30, and the reverse clutch 37 in a state where the hydraulic pressure is reduced by the lubricating hydraulic pressure adjustment valve 53. The oil supply port 57 is supplied. Unnecessary hydraulic oil having a pressure equal to or higher than a predetermined pressure is returned from the lubricating oil pressure adjusting valve 53 to the transmission case 22.

  The working hydraulic pressure adjusting valve 52 is provided with a slow fitting valve 54 that gradually increases the hydraulic pressure in proportion to time up to a set pressure of the hydraulic pressure adjusting valve 52 so as to reduce a shock caused by clutch connection at the time of forward or reverse switching. The slow insertion valve 54 includes a forward low-speed back pressure oil passage 55 branched from the downstream side of the forward low-speed electromagnetic valve 48 in the forward low-speed oil passage 45 and a downstream side of the forward high-speed electromagnetic valve 49 in the forward high-speed oil passage 46. Are connected to a forward high-speed back pressure oil passage 56 branched from the reverse hydraulic passage 56 and a reverse back pressure oil passage 57 branched from the downstream side of the reverse solenoid valve 50 in the reverse oil passage 47 via a throttle. The slow fitting valve 54 gradually increases the operating hydraulic pressure to the forward low speed clutch 27, the forward high speed clutch 30 or the reverse clutch 37 by the back pressure introduced from each of the back pressure oil passages 55 to 57, at the time of forward or reverse switching. It is configured to reduce the shock caused by clutch connection.

  The hydraulic pressure adjusting valve 52 is opened according to the hydraulic pressure flowing through the lubricating oil passage 51 when all the solenoid valves 48 to 50 are neutral. When the forward low speed solenoid valve 48 is driven to switch to the forward position, both the forward low speed solenoid valve 48 and the forward high speed solenoid valve 49 are switched to the forward position, or the reverse solenoid valve 50 is driven to switch to the reverse position. Then, the hydraulic oil flows into the loosely fitted valve 54 via the corresponding back pressure oil passages 55 to 57, and the hydraulic pressure adjusting valve 52 is closed. A relief spring 58 is interposed between the hydraulic pressure adjusting valve 52 and the loosely fitted valve 54. The compression of the relief spring 58 causes the operating hydraulic pressure adjustment valve 52 to operate more slowly than the loose insertion valve 54 and gradually closes. For this reason, the operating hydraulic pressure to the forward low-speed clutch 27, the forward high-speed clutch 30, or the reverse clutch 37 gradually increases, and the forward low-speed clutch 27, the forward high-speed clutch 30 or the reverse clutch 37 is gradually connected (engaged state). To. As a result, the shock when the clutches 27, 30, and 37 are connected is alleviated. These valves are collected as a hydraulic unit HU and are arranged adjacent to the engine 11 in the engine cover 2 shown in FIG. Symbol C is a controller for driving and controlling various electromagnetic valves.

  Next, the shaft support structure of the input / output shafts 14 and 15 in the transmission case 22 will be described with reference to FIGS. 4, 5, and 8. In the transmission case 22, a first bearing holder 61 that supports the lower end side of the input shaft 14, a pump case 62 that houses the clutch pump 40 connected to the lowermost end portion of the input shaft 14, and an upper end side of the output shaft 15 The 2nd bearing holder 63 which supports is arrange | positioned. The first bearing holder 61 is formed with a plurality of holder boss portions 64 protruding upward. The holder boss portions 64 of the first bearing holder 61 are fastened together with bolts 65 together with the pump case 62 superimposed from below the first bearing holder 61 on the inner surface side of the upper plate portion of the transmission case 22.

  The input shaft 14 is rotatably supported by a bearing 66 attached to the upper plate portion of the transmission case 22 and a bearing 67 attached to the first bearing holder 61. The input branch gear 25 is positioned between the pair of upper and lower bearings 66 and 67 of the input shaft 14.

  In the embodiment, two of the holder boss portions 64 of the first bearing holder 61 are partly formed with hydraulic oil passages 44a and 44b communicating with the clutch pump 40 in the pump case 62 so as to open on the outer surface of the case. doing. One of the holder boss portions 64 is provided with a 44 a communicating with the suction side of the clutch pump 40 in the hydraulic oil passage 44. Another of the holder boss portions 64 is formed with 44 b communicating with the discharge side of the clutch pump 40 in the hydraulic oil passage 44. The hydraulic oil passage 44 is formed with a 44 a communicating with the suction side of the clutch pump 40. The open end of the hydraulic oil passage 44b is connected to the hydraulic oil passage 44 of the hydraulic unit HU installed on the upper side thereof through a pipe.

  The second bearing holder 63 that supports the upper end side of the output shaft 15 is formed with a plurality of holder boss portions 68 protruding downward. Each holder boss portion 68 of the second bearing holder 63 is fastened together with bolts 69 on the inner surface side of the lower plate portion of the transmission case 22. The output shaft 15 is rotatably supported by a bearing 70 attached to the second bearing holder 63 and a bearing 71 attached to the lower plate portion of the transmission case 22. A forward high-speed output gear 39 and a forward / reverse output gear 38 are positioned between a pair of upper and lower bearings 70, 71 of the output shaft 15.

  As apparent from the above description and FIGS. 2 to 5, according to the outboard motor 1 of the embodiment, the rotational power from the input shaft 14 via the forward shaft 23 is the forward / reverse relay gear 32 or the forward high-speed gear 29. Is transmitted as a forward output (forward low speed or forward high speed output) to the output shaft 15, and the rotational power from the input shaft 14 via the reverse shaft 24 is transmitted via the reverse gear 36 and the forward / reverse relay gear 32. Since the transmission 13 is transmitted to the output shaft 15, the transmission 13 includes a mechanism for switching the rotational output of the front and rear propellers 5 and 6 between forward and reverse, but can have a simple structure, a small size, and a low cost. As a result, the outboard motor 1 is also made compact.

  Further, when all the clutches 27, 30, and 37 are in a neutral state, the rotation of the gear 26 that is constantly driven from the gear 25 is transmitted from the gear 29 to the gear 39 under the influence of the drag torque generated by the clutches 27 and 30. Therefore, the gear 39 tries to follow in the forward direction. On the other hand, the rotation of the gear 35 that is always driven from the gear 25 is transmitted to the gear 38 from the gears 36, 31, 28 under the influence of the drag torque generated by the clutch 37, so that the gear 38 tries to rotate in the reverse direction. To do. Therefore, the accompanying rotational forces with different rotation directions are canceled on the output shaft 15. Therefore, drag torque is generated when all the clutches 27, 30, and 37 are in a neutral state, and there is no possibility that the output shaft 15 will rotate unintentionally.

  Further, the forward low-speed gear 28 and the reverse relay gear 31 are connected to form a forward / reverse relay gear 32, and the forward / reverse relay gear is connected from the forward shaft 23 to the forward / reverse relay gear 32. 32 is provided with a one-way clutch 33 configured to transmit the forward output but not to transmit the forward output, so the forward low-speed gear 28 and the reverse relay gear 31 are shared, and the output shaft 15 side is provided. One gear can be omitted, and the transmission 13 can be made more compact.

  Moreover, the outboard motor 1 of the embodiment includes the forward low-speed gear 28, the forward high-speed gear 29, the forward low-speed clutch 27 that interrupts power transmission from the input shaft 14 to the forward shaft 23, and the forward high-speed from the forward shaft 23. Since the forward high-speed clutch 30 that cuts off the power transmission to the gear 29 is provided and is configured in the forward two-speed type, the gears 28 and 29 having a gear ratio according to the situation and the like are appropriately selected to output an appropriate output. It can be demonstrated and it is possible to navigate accurately.

  In addition, the structure of each part in this invention is not limited to embodiment of illustration, It can change variously in the range which does not deviate from the meaning of this invention.

DESCRIPTION OF SYMBOLS 1 Outboard motor 5 Front propeller 6 Rear propeller 11 Engine 12 Lower gear mechanism 13 Transmission 14 Input shaft 15 Output shaft 16 Propeller shaft 22 Shift case 23 Forward shaft 24 Reverse shaft 27 Forward low speed clutch 28 Forward low speed gear 29 Forward high speed gear 30 Forward high-speed clutch 31 Reverse relay gear 32 Forward and reverse relay gear 33 One-way clutch 36 Reverse gear 37 Reverse clutch 40 Clutch pump 41 Cooling water pump

Claims (5)

An engine, a lower gear mechanism for driving a propeller disposed below the engine, a transmission disposed between the engine and the lower gear mechanism, and an input shaft for transmitting power from the engine to the transmission; In an outboard motor comprising an output shaft for transmitting power from the transmission to the lower gear mechanism,
The transmission includes a vertically long forward shaft and a reverse shaft arranged in parallel,
A forward gear, a forward clutch that interrupts power transmission to the forward gear, and a reverse relay gear are arranged on the forward shaft, and a reverse gear and power transmission to the reverse gear are arranged on the reverse shaft. With a reverse clutch that
Power from the input shaft via the forward shaft is transmitted as a forward output to the output shaft via the forward gear, and power from the input shaft via the reverse shaft is transmitted from the reverse gear and the reverse relay gear. And is configured to transmit to the output shaft via
Outboard motor. The forward gear and the reverse relay gear are connected to form a forward and reverse relay gear,
A one-way clutch is arranged between the forward shaft and the forward / reverse relay gear to transmit forward output from the forward shaft to the forward / reverse relay gear but vice versa. ing,
The outboard motor according to claim 1. The forward gear is configured to separate a forward low speed gear and a forward high speed gear,
The forward clutch is configured to be separated into a forward low speed clutch that interrupts power transmission from the input shaft to the forward shaft and a forward high speed clutch that interrupts power transmission from the forward shaft to the forward high speed gear.
The forward low speed gear and the reverse relay gear are connected to form the forward and reverse relay gear.
The outboard motor according to claim 2. A hydraulic pump is connected to at least one of the input shaft and the reverse shaft;
The outboard motor according to claim 3. The propeller is configured as a counter-rotating propeller that is arranged in series with a front propeller and a rear propeller and is driven to rotate in directions opposite to each other.
The outboard motor according to any one of claims 1 to 4.

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