JP2022140003A - Outboard motor - Google Patents

Abstract

To provide an outboard engine capable of preventing insufficient cooling due to the breakage and coming-off of cooling pipes.SOLUTION: An outboard engine 10 comprises an outboard engine body 20, a stern bracket 40, and a cooler 60 placed in the water and in a supported state by a left bracket 50A and right bracket 50B, where the stern bracket has the left bracket 50A and the right bracket 50B fixed to a hull S, and has a swivel case 41 fixed to the outboard engine body 20 and pivotably connected to the left bracket 50A and to the right bracket 50B. A shaft part 42 is provided in the swivel case 41. A bearing part 52 to rotatably support the shaft part 42 is provided in the left bracket 50A and the right bracket 50B. A cooling passage passing through the shaft part 42 and the bearing part 52 is provided between the outboard engine body 20 and the cooler 60.SELECTED DRAWING: Figure 3

Description

The present invention relates to an outboard motor.

In general, outboard motors, in a standard position during use, transmit the rotational output of an engine or an electric motor, which is the driving source, to a drive shaft arranged in a vertical direction. Converts it to rotation and transmits it to the propeller shaft. Rotation of the propeller shaft causes the propeller attached to the propeller shaft to rotate about a horizontal axis to propel the hull.

Since the drive source generates heat as it operates, it requires an appropriate cooling structure. As this type of cooling structure, an air cooling structure using a radiator is known, but the heat exchange efficiency is low and the size is large. Moreover, since it is necessary to install it in a place on the hull that is exposed to the wind, there is also the problem that it looks unattractive.
In contrast to such an air-cooled structure, a water-cooled structure that cools by taking in water from outside the hull has many advantages such as high heat exchange efficiency, small size, and good appearance. An example of a conventional outboard motor (inboard/outboard motor) having this type of water cooling structure is shown in Patent Document 1 below. In the configuration disclosed in Patent Document 1, outboard water is taken into the hull through water supply hoses, cooling pipes, and the like to cool the engine.

JP-A-1-175592

By the way, when the hull is moored and anchored in shallow water, the outboard motors are tilted up and raised above the water surface. The same applies to the inboard/outboard motor of Patent Document 1, in which a bracket (gimbal housing) fixed to the hull supports the propulsion unit in a swingable manner.
However, when the propulsion unit is vertically swung, the cooling hose is subject to bending and twisting along with this swinging. If the water supply hose is detached or damaged due to such bending or twisting, there is a concern that sufficient cooling cannot be obtained and the engine may malfunction.

SUMMARY OF THE INVENTION It is an object of the present invention to provide an outboard motor that can prevent insufficient cooling due to disconnection or breakage of cooling pipes.

In order to solve the above problems, an outboard motor according to one aspect of the present invention employs the following configuration.
(1) An outboard motor (for example, the outboard motor 10 of the embodiment) provided on a hull (for example, the hull S of the embodiment) to propel the hull, and the outboard motor main body (for example, the outboard motor main body 20), brackets (for example, left bracket 50A and right bracket 50B in the embodiment) fixed to the hull, and fixed to the outboard motor main body and swingable with respect to the brackets. A swivel mechanism (for example, the stern bracket 40 of the embodiment) having a connected swivel case (for example, the swivel case 41 of the embodiment), and a swinging mechanism (for example, the stern bracket 40 of the embodiment), supported by at least one of the bracket and the hull, underwater and a cooler (e.g., the cooler 60 of the embodiment) disposed in the bracket and the swivel case, and a shaft (e.g., the shaft portion 42 of the embodiment) is provided on one of the bracket and the swivel case, and the other is provided with a bearing (for example, the bearing portion 52 in the embodiment) that rotatably supports the shaft, and a cooling flow path (for example, the in-shaft flow path 42a in the embodiment and an inner A flow path 53a) is provided between the outboard motor body and the cooler.

According to this configuration, the cooling liquid heated in the outboard motor main body flows to the cooler via the swivel case and the bracket. The heated liquid then flows to the cooler via cooling channels through the shaft and bearings. The heated liquid is cooled by water surrounding the cooler as it passes through the cooler. The liquid cooled by the cooler is returned to the outboard motor body via the bracket and swivel case. At this time, the cooled liquid flows to the main body of the outboard motor through the cooling passage through the shaft and bearings.
By circulating the liquid between the outboard motor body and the cooler in this way, the devices in the outboard motor body can be cooled with high cooling efficiency. Moreover, since the structure uses the shaft and the bearing as part of the cooling flow path, the cooling pipes required in the conventional structure are not required. Therefore, even if the outboard motor main body is tilted up together with the swivel case, problems associated with disconnection or breakage of the cooling pipes do not occur, so that insufficient cooling of the equipment inside the outboard motor main body can be reliably prevented.

(2) The outboard motor described in (1) above may be configured as follows. That is, the rocking mechanism includes a pair of connecting portions (for example, the connecting portion J in the embodiment) each having the shaft body and the bearing and spaced apart from each other, and the cooling passage includes the pair of and a return path passing through the other.

According to this configuration, the cooling liquid cooled by the cooler is supplied to the outboard motor main body through the outward path of the cooling flow path. On the other hand, the cooling liquid heated in the outboard motor main body is returned to the cooler through the return path of the cooling flow path.
When the cooling liquid circulates between the outboard motor main body and the cooler in this way, the pair of connecting portions are separated from each other, so that the cooling liquid cooled by the cooler can be cooled from there. It is possible to more reliably prevent the risk of heating due to the cooling liquid on the way to the container.

(3) The outboard motor described in (1) or (2) above may be configured as follows. That is, the shaft has an in-shaft flow path (for example, the in-shaft flow path 42a in the embodiment) formed inside the shaft, and the connecting portion is formed between the inner surface of the bearing and the shaft. and an inner bearing channel (for example, the gap C2 in the embodiment) formed between the outer surface and communicating with the inner shaft channel, and the inner shaft channel and the inner bearing channel are connected to the cooling channel. include.

According to this configuration, the cooling liquid that has flowed into the shaft passes through the in-shaft channel and then flows into the in-bearing channel of the bearing. Conversely, the cooling liquid that has flowed into the bearing internal flow path flows through the bearing internal flow path and then into the shaft internal flow path of the shaft body.
Since the cooling liquid can be smoothly flowed through the bearing and the shaft in this way, there is no shortage of flow. Therefore, the cooling capacity of the cooler can be fully exhibited.

(4) In the outboard motor described in (3) above, the in-shaft flow path extends in the radial direction of the shaft body and each of which communicates with the in-bearing flow path (for example, a plurality of radial flow paths). , the radial flow channel 42a2) of the embodiment.

According to this configuration, the cooling liquid that has flowed into the shaft is divided into a plurality of flows in the radial direction through the radial flow passages. Any liquid flowing through each radial channel is directed to the same intra-bearing channel and then to the cooler.
In this way, by providing a plurality of branched radial flow paths, the flow path area can be increased, so the pressure loss when the liquid passes through the pair of connecting portions can be reduced.

(5) The outboard motor described in any one of (1) to (4) above may be configured as follows. That is, the swivel case has a first connection port (for example, the large-diameter portion 43b2 of the embodiment) through which the cooling passage passes and is connected to the outboard motor main body, and the outboard motor main body The first connection port has a second connection port (for example, the large diameter portion 21g1 of the embodiment) to which the first connection port is coaxially connected. a pipe member (for example, the pipe 45 of the embodiment) that is coaxially inserted through the joint, and a sealing member that seals between the pipe member and both the first connection port and the second connection port, A center line passing through each of the first connection port, the tubular member, and the second connection port is parallel to the direction in which the swivel case is assembled to the outboard motor main body.

According to this configuration, after arranging the sealing member, the swivel case is assembled to the outboard motor main body in a state in which the center lines passing through the first connection port, the pipe member, and the second connection port are aligned. , the cooling channel can be formed at the same time as the assembly.
Therefore, since the cooling flow path can be formed by a simple assembly procedure, the manufacturing cost can be reduced.

According to the above aspect of the present invention, the cooling liquid can be circulated and supplied to the drive source without using conventional cooling pipes. Therefore, when the outboard motor is tilted up, there is no need for cooling pipes that are elastically deformed to follow the tilting up, so that cooling deficiencies due to detachment or breakage of the cooling pipes can be reliably prevented.

1 is a side view of an outboard motor according to an embodiment of the invention; FIG. 2 is a plan view of the outboard motor; FIG. FIG. 2 is an exploded perspective view for explaining the arrangement of equipment of the outboard motor and the circulation route of cooling oil; FIG. 3 is a cross-sectional view taken along the line AA in FIG. 2, showing the essential parts of the outboard motor. FIG. 5 is a cross-sectional view taken along the line BB in FIG. 4, showing the essential parts of the outboard motor. FIG. 5 is an enlarged view of a portion C in FIG. 4, showing a main part of the outboard motor. FIG. 6 is an enlarged view of part D in FIG. 5, showing a main part of the outboard motor. FIG. 8 is a cross-sectional view taken along the line EE in FIG. 7, showing the essential parts of the outboard motor. FIG. 9 is an enlarged view of the F portion of FIG. 8, showing the essential parts of the outboard motor.

An embodiment of an outboard motor of the present invention will be described below with reference to the drawings.
In addition, the code|symbol FW shown in drawing shows the front with respect to the advancing direction, and the code|symbol RW shows the rear with respect to the advancing direction. Hereinafter, "forward with respect to the direction of travel" may be simply referred to as "forward", and "rear with respect to the direction of travel" may simply be referred to as "rear". Also, both the "forward direction with respect to the direction of travel" and the "rearward direction with respect to the direction of travel" may be collectively referred to simply as the "front-back direction." Also, the left with respect to the front is sometimes called "left direction", and the right with respect to the front is sometimes called "right direction". Both the "leftward direction" and the "rightward direction" may be collectively referred to simply as the "horizontal direction."

As shown in FIGS. 1 and 2, the outboard motor 10 of the present embodiment is a propulsion device provided at the stern St of the hull S to propel the hull S. As shown in FIGS.
The outboard motor 10 includes an outboard motor body 20 , a stern bracket (swing mechanism) 40 and a cooler 60 .
The outboard motor main body 20 includes a case 21, an oil pan 22, a drive shaft case 23, a gear case 24, a power unit 25, a steering mechanism 26, a drive shaft 27, a bevel gear unit 28, a propeller shaft 29, A propeller holder 30 and a propeller 31 are provided.

Case 21 is fixed to the upper portion of oil pan 22 . A power unit 25 and a steering mechanism 26 are housed within the case 21 . The case 21 is attached to the stern St of the hull S via a stern bracket 40 . More specifically, the case 21 is attached to the stern bracket 40 so as to be swingably supported in the vertical direction along the arrow T about the tilt axis Tc. A connection structure and the like between the case 21 and the stern bracket 40 will be described later.
The oil pan 22 stores, for example, an electric motor and a deceleration unit (both not shown) of the power unit 25, oil (cooling liquid, hereinafter referred to as “cooling oil”) for cooling and lubricating the steering mechanism 26, and the like. there is

The power unit 25 includes the electric motor and the reduction unit. The electric motor is a drive source that rotates the propeller 31 .
Although not shown, the drive motor has a configuration in which its rotating shaft is arranged in a vertical direction and a rotor is rotatably supported inside a stator. This rotor is supported by the rotating shaft. The reduction unit is connected to this rotating shaft. This deceleration unit decelerates the rotation speed of the electric motor and transmits it to the drive shaft 27 .

The drive shaft 27 is connected to the electric motor via the deceleration unit, and is generally arranged along the vertical direction.
The drive shaft 27 is housed within the drive shaft case 23 and rotatably supported within the drive shaft case 23 via bearings (not shown). The drive shaft case 23 is rotatably supported around a vertical axis, for example, via other bearings (not shown) arranged inside the case 21 .
The bevel gear unit 28 is housed inside the gear case 24 . The gear case 24 is fixed integrally with the drive shaft case 23 .

The propeller shaft 29 extends rearward from the bevel gear unit 28 in a direction crossing the drive shaft 27 . That is, the propeller shaft 29 is connected to the drive shaft 27 via the bevel gear unit 28 so as to intersect. The propeller shaft 29 has a base end fixed to the bevel gear unit 28 and housed in the gear case 24 .

The propeller shaft 29 protrudes rearward from the position of the bevel gear unit 28 via the propeller holder 30 . Propeller holder 30 is fixed to gear case 24 . For example, a propeller shaft 29 is rotatably supported by the propeller holder 30 via a bearing (not shown). A propeller 31 for propelling is fixed to a portion of the propeller shaft 29 that protrudes rearward from the propeller holder 30 .
Propeller 31 has a plurality of blades 31a that rotate about a horizontal axis together with propeller shaft 29 .
The drive shaft case 23, the gear case 24, and the propeller holder 30 are integrally fixed in a state of being arranged to form a substantially L shape when viewed from the side.

By driving the electric motor of the power unit 25 , the rotation of its rotary shaft is transmitted to the propeller 31 through the reduction unit, drive shaft 27 , bevel gear unit 28 and propeller shaft 29 . The hull S is propelled by the rotation of the propeller 31 .
The outboard motor 10 is steered by rotating the propeller 31 around the drive shaft 27 by the steering mechanism 26 .

As shown in FIG. 3 , the cooler 60 is supported by the stern bracket 40 below the stern bracket 40 . The cooler 60 is of a water-cooled type, and is placed underwater during normal operation of the outboard motor 10 . The cooler 60 has a cooler main body 61 , an outward piping 62 , and a return piping 63 .

Inside the cooler main body 61, a meandering flow path 61a is formed. By streamlining the cross-sectional shape of the cooler 61, the heat transfer area of the flow path 61a is increased and the heat exchange efficiency is improved, but a large fluid resistance is not generated when the hull S is propelled.

One end of the flow path 61a of the cooler body 61 is located near the left end in the left-right direction of the cooler body 61, and communicates with a return pipe 63 fixedly arranged directly above this position. The other end of the flow path 61a is located near the right end in the left-right direction of the cooler main body 61, and communicates with an outward pipe 62 fixedly arranged directly above this position.
The outgoing pipe 62 has its lower end vertically and integrally connected to the upper surface of the cooler main body 61, while its upper end faces vertically upward. The return pipe 63 also has its lower end vertically and integrally connected to the upper surface of the cooler main body 61, while its upper end faces vertically upward. Both the outgoing line pipe 62 and the return line pipe 63 are straight pipe members, and are arranged so as to be parallel to each other. The outbound pipe 62 and the return pipe 63 are a pair of metal pipes that do not elastically deform. Therefore, the relative position of the cooler body 61 with respect to the stern bracket 40 is always fixed.

These outward piping 62 and return piping 63 are fixed to the lower part of the bracket 50 of the stern bracket 40, as shown in FIG. However, the arrangement of the cooler main body 61 is not limited to this position, and it may be fixed to either the stern bracket 40 or the hull S.
That is, for example, the cooler body 61 may be arranged at a position indicated by reference numeral 60A indicated by a phantom line in FIG. In this case, the cooler body 61 can be fixed along the surface of the stern St. It is conceivable that the cooler main body 61 and the stern bracket 40 are communicated with each other by an outward piping 62 and a return piping 63 . Even when the cooler body 61 is arranged at the position 60A in this way, the relative position between the stern bracket 40 and the cooler body 61 can be fixed regardless of the rocking motion of the outboard motor body 20. FIG.
For that matter, the cooler body 61 may be fixed relative to both the stern bracket 40 and the stern S. In this case, the cooler main body 61 can be supported more firmly.

Next, the stern bracket 40 that supports the outboard motor main body 20 and the cooler 60 configured as described above will be described. Before that, the case 21 to which the stern bracket 40 is attached will be described in detail.
As shown in FIGS. 4 and 5, the case 21 has a substantially cylindrical side wall portion 21a and an upper wall portion 21b covering the upper portion of the side wall portion 21a. 4 and 5, illustration of each device in the case 21 is omitted for explanation. The lower portion of the side wall portion 21 a is open and communicates with the internal space of the oil pan 22 .

A part of the outer peripheral surface of the side wall portion 21a serves as a mounting surface 21c for fixing the stern bracket 40 with, for example, four bolts 40a. The mounting surface 21c is a substantially quadrilateral flat surface, and projections 21e having female screw holes are formed at the four corners thereof. These four protrusions 21 e have female screw holes whose center lines are parallel to each other, and open toward the stern bracket 40 . In this embodiment, four bolts 40a and four protrusions 21e are provided, but the number is not limited to four, and may be one, two, or five or more. Moreover, you may fix using fixing tools other than a bolt.

A pair of protrusions 21f are formed on the outer peripheral surface of the side wall portion 21a above the mounting surface 21c. These protrusions 21f are formed with through holes (reference numeral 21g in FIG. 6) that are parallel to each other and open toward the stern bracket 40. As shown in FIG. The height positions of these through holes 21g are the same. As shown in FIG. 6, each of the pair of through holes 21g has a large diameter portion 21g1 that opens toward the stern bracket 40 and a small diameter portion 21g2 that is smaller in diameter than the large diameter portion 21g1.

The large-diameter portion 21g1 is a columnar space having a constant inner diameter, and is fitted with a pipe 45 with an O-ring 46 fitted therein. In addition, the open end of the large diameter portion 21g1 widens toward the stern bracket 40. As shown in FIG. Since the large-diameter portion 21g1 and the small-diameter portion 21g2 have different inner diameters, a step is formed between them.
The small-diameter portion 21g2 is a columnar space having a constant inner diameter smaller than that of the large-diameter portion 21g1, and the back side thereof is bent vertically downward in an L shape. The small diameter portion 21g2 is connected to a lubricating circuit (not shown) leading to the oil pan 22. As shown in FIG. This lubricating circuit has an outward path and a return path. In the forward trip, after lubricating and cooling the equipment in the outboard motor main body 20 and sucking up the heated cooling oil, as shown in FIG. and send it out. On the return path, the cooling liquid cooled by the cooler 60 and returned via the stern bracket 40 is taken into the outboard motor main body 20 via the other of the pair of through holes 21g.

A stern bracket 40 fixed to the case 21 includes a swivel case 41 and a bracket 50, as shown in FIGS.

The swivel case 41 has a shaft portion (shaft body) 42 , a horizontal portion 43 , a mounting portion 44 , a pipe (tubing member) 45 and an O-ring (sealing member) 46 .
As shown in FIG. 5, the shaft portion 42 has a substantially cylindrical shape and is rotatable around a central axis CL extending in the left-right direction. A pair of in-shaft flow passages 42a extending coaxially with the center axis CL are formed inside the shaft portion 42 . As shown in FIG. 7, these axial flow passages 42a are respectively divided into an axial flow passage 42a1 formed coaxially with the shaft portion 42 and branched from the axial flow passage 42a1 in the radial direction of the shaft portion 42. and a radial flow path 42a2. Each axial flow path 42a1 is formed from a position near the center in the longitudinal direction of the shaft portion 42 toward an end position. Each axial flow path 42 a 1 is open at the end position of the shaft portion 42 . On the other hand, the two axial flow paths 42a1 are separated from each other at the central position in the longitudinal direction of the shaft portion 42 as viewed in plan in cross section as shown in FIG. On the other hand, adjacent ends of both axial flow paths 42 a 1 are bent in an L shape toward the mounting surface 21 c of the case 21 .

As shown in FIGS. 7 to 9, each of the radial flow passages 42a2 forms two flow passages that are perpendicular to the axial flow passages 42a1 and open on the outer peripheral surface of the shaft portion 42. As shown in FIG. Therefore, at each end of the shaft portion 42, there are a total of three axial flow paths 42a including one flow path along the central axis CL and two flow paths orthogonal to the central axis CL. Divided into books. In this embodiment, the number of the radial flow passages 42a2 is two, but the number is not limited to two, and may be one or three or more.

As shown in FIG. 7, a pair of O-ring grooves are formed at each end of the shaft portion 42 . The radial flow passages 42a2 are arranged at positions sandwiched between the O-ring grooves. In other words, when viewed along the central axis CL, O-ring grooves are formed on both sides of each of the radial flow paths 42a2. An O-ring 42b is fitted in each of these O-ring grooves.
A portion of the shaft portion 42 where the radial flow passages 42a2 are formed has a smaller diameter than the portions on both sides thereof. That is, when the shaft portion 42 is viewed from the outer end position toward the central position along the center axis CL, the outermost portion of the shaft portion 42 where the O-ring 42b is arranged has a relatively large outer diameter. It has a large diameter. A portion adjacent to the large-diameter portion where the radial flow passages 42a2 are arranged is a small-diameter portion having an outer diameter smaller than that of the large-diameter portion. Further, the portion adjacent to this small diameter portion where the O-ring 42b is arranged is a large diameter portion having an outer diameter larger than that of the small diameter portion. The pair of large-diameter portions sandwiching the small-diameter portion have the same outer diameter.

As shown in FIG. 5, the horizontal portion 43 has a left support wall portion 43a, a central pipe portion 43b, and a right support wall portion 43c.
The central pipe portion 43b is formed integrally with the central position of the shaft portion 42 in the left-right direction, and extends rearward from the shaft portion 42. As shown in FIG. A pair of connection flow paths 43b1 are formed in the central pipe portion 43b with a space therebetween. The front ends of the connection channels 43b1 communicate with the ends of the axial channels 42a1 located in the center of the shaft 42 in the longitudinal direction. That is, the front end portion of the connection channel 43b1 on the left side is connected to the axial direction channel 42a1 on the left side. The front end of the connection channel 43b1 on the right side is connected to the axial direction channel 42a1 on the right side.
A space S is provided between the pair of connection channels 43b1 as shown in FIG. The space S blocks the heat transfer between the cooling oil flowing in the outward connection flow path 43b1 and the cooling oil flowing in the homeward connection flow path 43b1. As a result, the temperature of the cooling oil that has been cooled and flows on the outward path is not raised by the heated cooling oil that flows on the return path.

As shown in FIG. 6, a large diameter portion 43b2 is formed at each rear end of the pair of connection flow paths 43b1. Since this large-diameter portion 43b2 is a portion whose diameter is partially enlarged, it has a step with other portions. These large diameter portions 43b2 have the same inner diameter as the large diameter portion 21g1. A pipe 45 in which an O-ring 46 is fitted is fitted in these large diameter portions 43b2.

As shown in FIG. 6, when the stern bracket 40 is assembled to the case 21, the large diameter portion 21g1 and the large diameter portion 43b2 are arranged coaxially with each other, and the pipe 45 is fitted therebetween. A deep O-ring groove is formed in the outer peripheral surface of the pipe 45 at a position corresponding to the O-ring groove in the large diameter portion 21g1. Further, a deep O-ring groove is also formed on the outer peripheral surface of the pipe 45 at a position corresponding to the O-ring groove in the large diameter portion 43b2. Therefore, the outer peripheral surface of the pipe 45 and the inner peripheral surface of the large diameter portion 21g1 are liquid-tightly sealed by the O-ring 46 disposed therebetween. Similarly, the outer peripheral surface of the pipe 45 and the inner peripheral surface of the large diameter portion 43b2 are liquid-tightly sealed by an O-ring 46 disposed therebetween. Therefore, the cooling oil flows only inside the pipe 45 without leaking to the outside from between the large diameter portion 21g1 and the large diameter portion 43b2.

Moreover, even if the pipe 45 tries to deviate from the specified installation position due to the flow of the cooling oil or the like, it is blocked by the step formed in the connection flow path 43b1. Similarly, even if the pipe 45 were to come off from the installation position in the opposite direction, it would be blocked by the step between the large-diameter portion 21g1 and the small-diameter portion 21g2. Therefore, although the structure is simple, the pipe 45 is prevented from being dislodged from the specified installation position, and the cooling oil is prevented from leaking.

When assembling the stern bracket 40 to the case 21 , first, the O-rings 46 are fitted in two O-ring grooves formed around the pipe 45 . Then, this pipe 45 is first inserted into the large diameter portion 43b2. At that time, the pipe 45 is pushed in until the fingertip feels the O-ring 46 entering the O-ring groove in the large-diameter portion 43b2. Subsequently, the stern bracket 40 with the pipe 45 inserted therein is assembled to the case 21 . At this time, the pipe 45 is inserted into the large-diameter portion 21g1, and the large-diameter portion 21g1 can be easily inserted because its opening end is widened. Subsequently, by fixing the position of the stern bracket 40 with respect to the case 21 with four bolts 40a, the large-diameter portion 21g1 and the large-diameter portion 43b2 are connected in a liquid-tight manner.
In this manner, simply by assembling the stern bracket 40 to the case 21, the large diameter portion 21g1 and the large diameter portion 43b2 are sealed, and at the same time, a cooling flow path communicating between them can be formed. there is

As shown in FIG. 5, the left support wall portion 43a and the right support wall portion 43c are arranged with the central pipe portion 43b interposed therebetween. Specifically, the left support wall portion 43 a extends rearward from a position near the left end of the shaft portion 42 . Similarly, the right support wall portion 43 c extends rearward from a position near the right end of the shaft portion 42 .

As shown in FIG. 3, the mounting portion 44 is a substantially plate-like portion arranged along the vertical direction, and has the left support wall portion 43a, the central pipe portion 43b, and the right support wall portion 43c above it. are connected together. The mounting portion 44 is formed with four through holes 44a at positions corresponding to the four protrusions 21e formed on the mounting surface 21c of the case 21. As shown in FIG.
The stern bracket 40 is fixed to the mounting surface 21c of the case 21 at each mounting portion 44 of the swivel case 41 by four bolts 40a. As a result, the attachment of the stern bracket 40 to the outboard motor main body 20 and the connection of the cooling flow path therebetween can be performed simultaneously.

The bracket 50 has a left bracket 50A and a right bracket 50B, as shown in FIG. The left bracket 50A and the right bracket 50B have the same configuration except that they are left-right asymmetrical. Therefore, the detailed structure of the left bracket 50A will be described below, and the description of the right bracket 50B will be omitted as the same applies.
As shown in FIG. 8, the left bracket 50A has a substantially L shape when viewed in vertical cross section. That is, the left bracket 50A includes a bearing portion 52 that rotatably supports the shaft portion 42, a bracket upper portion 53 that extends rearward from the bearing portion 52, and a rear end of the bracket upper portion 53 that extends vertically downward. It has a bracket middle portion 54 extending toward and a bracket lower portion 55 extending vertically downward from the lower end of the bracket middle portion 54 .

As shown in FIGS. 7 and 9, inside the bearing portion 52, a recess portion 52a, which is a substantially cylindrical space, is formed. The shaft portion 42 is coaxially fitted into the recess 52a. That is, the recessed portion 52a and the shaft portion 42 share the central axis CL, and the shaft portion 42 is rotatable about the central axis CL with respect to the recessed portion 52a. A pair of connecting portions J is formed by the bearing portion 52 and the shaft portion 42 pivotally supported in the bearing portion 52 . As shown in FIG. 5, the stern bracket 40 of this embodiment includes two sets (pairs) of connecting portions J. As shown in FIG. These connecting portions J are spaced apart from each other along the left-right direction. The swivel case 41 is axially supported by the pair of connecting portions J so as to be vertically swingable with respect to the bracket 50 .

As shown in FIG. 7, a gap C1 is formed between the end surface of the shaft portion 42 and the inner surface of the recess 52a. An annular gap C2 is formed between the outer peripheral surface of the small diameter portion of the shaft portion 42 and the inner peripheral surface of the recess 52a.
By providing the gap C1, the outer end surface of the shaft portion 42 can be kept out of contact with the inner surface of the recess 52a. In addition, part of the cooling oil can be stored in the gap C1. Therefore, when swiveling the swivel case 41 with respect to the bracket 50, the swivel case 41 can be moved smoothly.

The gap C2 communicates with an internal flow path 53a, which will be described later. Therefore, in the left bracket 50A through which the return path of the cooling oil passes, the cooling oil that has flowed into the gap C2 from each radial flow path 42a2 can further flow to the internal flow path 53a. Conversely, in the right bracket 50B through which the forward path of the cooling oil passes, the cooling oil that has flowed into the gap C2 from the internal flow path 53a can further flow to each radial flow path 42a2.
Since the gap C2 is annular, regardless of the swinging position of the swivel case 41 with respect to the stern bracket 40, the in-shaft flow path 42a and the internal flow path 53a are always in communication, and the cooling oil flows between them. flow is always maintained. In addition, since the clearance C2 is sealed by the pair of O-rings 42b, it is possible to always prevent leakage of cooling oil from the connecting portion J regardless of the swinging position of the swivel case 41 with respect to the bracket 50.

As shown in FIGS. 8 and 9, the bracket upper portion 53 is a plate elongated in the front-rear direction, and its front end is integrally connected to the shaft portion 42 . Inside the bracket upper portion 53, an internal flow passage 53a is formed that communicates with the clearance C2 and extends straight obliquely downward to the rear. In the case of the left bracket 50A through which the return path of the cooling oil passes, the internal flow path 53a causes the cooling oil that has flowed through the gap C2 to flow rearward. On the other hand, in the case of the right bracket 50B through which the forward path of the cooling oil passes, the internal flow path 53a causes the cooling oil to flow forward and into the gap C2.

As shown in FIG. 8 , the bracket middle portion 54 is a vertically elongated plate, and its upper end is integrally connected to the rear end of the bracket upper portion 53 . Inside the bracket middle portion 54, an internal channel 54a is formed that communicates with the internal channel 53a and extends straight downward in the vertical direction. In the case of the left bracket 50A through which the return path of the cooling oil passes, the internal flow path 54a causes the cooling oil flowing from the internal flow path 53a to flow vertically downward. On the other hand, in the case of the right bracket 50B through which the forward path of the cooling oil passes, the internal flow path 54a causes the cooling oil to flow vertically upward and into the internal flow path 53a.

As shown in FIG. 8, the bracket lower portion 55 is a cylindrical body elongated in the vertical direction, and its upper end is integrally connected to the lower end of the bracket middle portion 54 . Inside the bracket lower portion 55, an internal flow path 55a is formed that communicates with the internal flow path 54a and extends straight downward in the vertical direction. In the case of the left bracket 50A through which the return path of the cooling oil passes, the internal flow path 55a causes the cooling oil flowing from the internal flow path 54a to flow vertically downward. On the other hand, in the case of the right bracket 50B through which the forward path of the cooling oil passes, the internal flow path 55a causes the cooling oil to flow vertically upward and into the internal flow path 54a.

The lower end of the bracket lower portion 55 is configured to form a cooling flow path with the connection partner via the pipe 56, as in the configuration described in FIG.
That is, as shown in FIG. 8, the inner diameter of the lower end of the internal flow path 55a is partially increased. Similarly, the inner diameter of the upper end of the return pipe 63 is partially increased. A pipe 56 is coaxially arranged inside the lower end of the internal flow path 55a and the upper end of the return pipe 63 in a state in which they are coaxially in contact with each other. The outer peripheral surface of the pipe 56 and the inner peripheral surface of the lower end of the internal flow path 55a are liquid-tightly sealed by an O-ring. Similarly, the outer peripheral surface of the pipe 56 and the inner peripheral surface of the upper end of the return pipe 63 are liquid-tightly sealed by an O-ring.

A step is formed on the inner peripheral surface of the lower end of the internal flow path 55a. Similarly, a step is also formed on the inner peripheral surface of the upper end of the return pipe 63 . By arranging the pipe 56 between these two steps, it is possible to dam the pipe 45 so that it does not move out of the specified position due to the flow of the cooling liquid or the like. Therefore, although the structure is simple, the pipe 56 is prevented from being displaced from the specified position and the cooling oil is not leaked.

The bracket lower portion 55 is fixed to the cooler body 61 via bolts (not shown). The tightening direction of this bolt is along the vertical direction, which is the same as the mounting direction of the bracket lower portion 55 with respect to the return pipe 63 . Therefore, insert the lower end of the pipe 56 with two O-rings fitted in advance into the upper end of the return pipe 63, then insert the upper end of the pipe 56 into the lower end of the lower bracket 55, and finally tighten the lower end of the bracket 55 with bolts. can be assembled by simply fixing to the cooler main body 61. - 特許庁Therefore, complicated piping work is not required.
The outbound pipe 62 also has the same connection configuration as the inbound pipe 63 described above.

The outboard motor 10 of this embodiment has the device configuration described above. As a result, cooling oil is circulated through the cooling flow path shown in FIG.
That is, on the return path of the cooling passage, the cooling oil heated by lubricating and cooling each device in the outboard motor main body 20 is sent to the cooler 60 . Specifically, the cooling oil sent out from the lubricating circuit of the outboard motor body 20 first flows into the connection flow path 43b1. The cooling oil that has flowed through the connection flow path 43 b 1 flows into the in-shaft flow path 42 a of the shaft portion 42 . In the axial flow passage 42a, the cooling oil separated into two flows passing through the pair of radial flow passages 42a2 respectively flows into the gap C2 in the bearing portion 52 and gathers again into one flow. The cooling oil that has flowed out from the gap C2 flows through the internal flow path 53a, the internal flow path 54a, and the internal flow path 55a in this order within the left bracket 50A. The cooling oil that has flowed out of the internal flow path 55 a flows through the flow path 61 a inside the cooler body 61 via the return pipe 63 . At this time, the heat of the cooling oil is radiated to the surrounding water through the wall of the cooler body 61 . As a result, the cooling oil is cooled and its temperature is lowered. The cooled cooling oil goes to the outboard motor main body 20 through the outgoing path of the cooling flow path.

That is, the cooling oil that has flowed from the flow path 61a of the cooler main body 61 to the forward pipe 62 flows into the right bracket 50B. Inside the right bracket 50B, the cooling oil flows through the internal flow path 55a, the internal flow path 54a, and the internal flow path 53a in this order. The cooling oil flowing out from the internal flow path 53 a flows into the clearance C<b>2 inside the bearing portion 52 . The cooling oil in the gap C2 is separated into two flows passing through the pair of radial flow passages 42a2. Then, the cooling oil flows through the axial flow path 42a1 and is gathered into one flow again. The cooling oil flowing through the axial flow path 42a1 flows into the connection flow path 43b1. The cooling oil flowing through the connection flow path 43b1 finally flows into the lubrication circuit of the outboard motor main body 20. As shown in FIG. The cooling oil cools and lubricates each device in the outboard motor main body 20 while circulating through this lubrication circuit. As a result, the cooling oil whose temperature rises again is directed to the cooler main body 61 again through the return path.

The outline of the outboard motor 10 having the configuration described above is summarized below.
(1) The outboard motor 10 of the present embodiment is provided on the hull S to propel the hull S. The outboard motor 10 includes an outboard motor main body 20, a left bracket (bracket) 50A and a right bracket (bracket) 50B fixed to the hull S, and a left bracket (bracket) 50B fixed to the outboard motor main body 20. 50A and a swivel case 41 swingably connected to the right bracket (bracket) 50B, and supported by the left bracket (bracket) 50A and the right bracket (bracket) 50B. and a cooler 60 placed in the water in a closed state. A shaft (shaft) 42 is provided on the swivel case 41, and the shaft (shaft) 42 is rotatably supported by the left bracket (bracket) 50A and the right bracket (bracket) 50B. A bearing portion (bearing) 52 is provided. In addition, an in-shaft channel 42 a and an internal channel 53 a are provided between the outboard motor main body 20 and the cooler 60 as cooling channels passing through the shaft portion (shaft body) 42 and the bearing portion (bearing) 52 . there is

According to this configuration, the cooling oil (cooling liquid) heated in the outboard motor main body 20 flows to the cooler 60 via the swivel case 41 and the left bracket (bracket) 50A. At that time, the heated cooling oil flows to the cooler 60 through the shaft internal flow path 42 a and the internal flow path 53 a which are cooling flow paths passing through the shaft portion (shaft body) 42 and the bearing portion (bearing) 52 . As the heated coolant passes through cooler 60 , it is cooled by the water surrounding cooler 60 . The cooling oil (liquid) cooled by the cooler 60 is returned to the outboard motor main body 20 via the right bracket (bracket) 50B and swivel case 41 . At this time, the cooled cooling oil (liquid) passes through the shaft internal flow path 42a and internal flow path 53a, which are cooling flow paths passing through the shaft portion (shaft body) 42 and the bearing portion (bearing) 52, to the outboard motor. flows into the body 20;
By circulating the cooling oil (liquid) between the outboard motor main body 20 and the cooler 60 in this manner, the equipment in the outboard motor main body 20 can be cooled with high cooling efficiency. Moreover, since the structure uses the shaft portion (shaft body) 42 and the bearing portion (bearing) 52 as a part of the cooling flow path, cooling pipes unlike the conventional structure are not required. Therefore, even if the outboard motor main body 20 is tilted up together with the swivel case 41, problems associated with disconnection or breakage of the cooling pipes do not occur, and insufficient cooling of the equipment inside the outboard motor main body 20 can be reliably prevented.

In the above-described embodiment, the left bracket (bracket) 50A and the right bracket (bracket) 50B are provided with the bearing portions (bearings) 52, and the swivel case 41 is provided with the shaft portion (shaft body) 42. It is not limited only to the configuration. Conversely, the left bracket (bracket) 50A and the right bracket (bracket) 50B may have the shaft portion (shaft body) 42 and the swivel case 41 may have the bearing portion (bearing) 52 .
Further, although the cooler 60 is configured to be supported underwater by the left bracket (bracket) 50A and the right bracket (bracket) 50B, the configuration is not limited to this. As described above, the cooler 60 may be fixed to the hull S and supported underwater.

(2) The outboard motor described in (1) above may be configured as follows. That is, the stern bracket (swing mechanism) 40 includes a pair of connecting portions J each having a shaft portion (shaft body) 42 and a bearing portion (bearing) 52 and arranged apart from each other. It has an outward path passing through one of the pair of connecting portions J and a return path passing through the other.

According to this configuration, the cooling oil (cooling liquid) cooled by the cooler 60 is supplied to the outboard motor main body 20 through the outgoing path of the cooling flow path. On the other hand, the cooling oil (cooling liquid) heated in the outboard motor main body 20 is returned to the cooler 60 through the return path of the cooling flow path.
When the cooling oil (liquid for cooling) circulates between the outboard motor main body 20 and the cooler 60 in this manner, the pair of connecting portions J are spaced apart from each other, so the oil is cooled by the cooler 60. It is possible to more reliably prevent the cooling oil (cooling liquid) from being heated by the cooling oil (cooling liquid) on the way to the cooler 60 .

(3) The outboard motor described in (1) or (2) above may be configured as follows. That is, the shaft portion (shaft) 42 has a shaft inner flow path 42a formed inside the shaft portion (shaft) 42, and the connecting portion J is formed between the inner surface of the bearing portion (bearing) 52 and the shaft portion ( A gap (bearing inner channel) C2 is formed between the outer surface of the shaft body) 42 and communicates with the shaft inner channel 42a, and the shaft inner channel 42a and the gap (bearing inner channel) C2 are used for cooling Included in the flow path.

According to this configuration, the cooling oil (cooling liquid) that has flowed into the shaft portion (shaft body) 42 passes through the shaft inner flow path 42a, and then passes through the gap (bearing inner flow path) C2 of the bearing portion (bearing) 52. flow into. Conversely, the cooling oil (cooling liquid) that has flowed into the gap (bearing inner flow path) C2 passes through the gap (bearing inner flow path) C2 and then flows into the shaft inner flow path 42a of the shaft portion (shaft body) 42. and flow in.
Since the cooling oil (cooling liquid) can flow smoothly through the shaft portion (shaft body) 42 and the bearing portion (bearing) 52 in this way, there is no shortage of flow rate. Therefore, the cooling capacity of the cooler 60 can be fully exhibited.

(4) In the outboard motor described in (3) above, the two in-shaft flow paths 42a extend in the radial direction of the shaft portion (shaft body) 42 and each communicates with the gap (bearing flow path) C2. may be branched into the radial flow path 42a2.

According to this configuration, the cooling oil (cooling liquid) that has flowed into the shaft portion (shaft) 42 is divided into two flows in the radial direction through the radial flow passages 42a2. All of the cooling oil (liquid) flowing through each radial flow path 42 a 2 is directed to the cooler 60 after being guided to the same gap (bearing inner flow path) C 2 .
By providing the radial flow path 42a2 branching into two in this way, the flow path area can be increased, so the pressure loss when the cooling oil (liquid) passes through the pair of connecting portions J can be reduced.
In addition, the number of the radial flow passages 42a2 is not limited to two, and may be one or three or more.

(5) The outboard motor described in any one of (1) to (4) above may be configured as follows. That is, the swivel case 41 has a large-diameter portion (first connection port) 43b2 through which the cooling passage passes and is connected to the outboard motor body 20, and the outboard motor body 20 has a large-diameter portion (first connection port) 43b2. Port) 43b2 has a large diameter portion (second connection port) 21g1 coaxially connected thereto, and a stern bracket (swing mechanism) 40 is provided inside the large diameter portion (first connection port) 43b2 and inside the large diameter portion (second connection port) 43b2. 2 connection port) 21g1, a pipe (pipe member) 45 coaxially inserted into both of them, a pipe (pipe member) 45, a large diameter portion (first connection port) 43b2, and a large diameter portion (second connection port) 21g1. and an O-ring (sealing member) 46 for sealing between both of the large-diameter portion (first connection port) 43b2, the pipe (tubing member) 45, and the large-diameter portion (second connection port) 21g1, respectively. is parallel to the mounting direction of the swivel case 41 to the outboard motor main body 20 .

According to this configuration, after arranging the O-ring (sealing member) 46, the central By assembling the swivel case 41 to the outboard motor main body 20 with the lines aligned, the cooling flow path can be formed at the same time as the assembly.
Therefore, since the cooling flow path can be formed by a simple assembly procedure, the manufacturing cost can be reduced.

The technical scope of the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.
In addition, it is possible to appropriately replace the constituent elements in the above-described embodiment with well-known constituent elements without departing from the spirit of the present invention, and the modifications described above may be combined as appropriate.

10 outboard motor 20 outboard motor body 21g1 large diameter portion (second connection port)
40 stern bracket (swing mechanism)
41 swivel case 42 shaft (shaft)
42a axial flow path 42a2 radial flow path 43b2 large diameter portion (first connection port)
45 pipe (tubing material)
46 O-ring (seal member)
50A left bracket (bracket)
50B right bracket (bracket)
52 bearing part (bearing)
60 Cooler C2 Gap (passage inside bearing)
J Joint S Hull

Claims (5)

An outboard motor provided in a hull to propel the hull,
an outboard motor body;
a swing mechanism having a bracket fixed to the hull; and a swivel case fixed to the outboard motor main body and connected to the bracket so as to swing freely;
a cooler arranged underwater while being supported by at least one of the bracket and the hull;
with
One of the bracket and the swivel case is provided with a shaft, and the other is provided with a bearing for rotatably supporting the shaft,
An outboard motor, wherein a cooling passage passing through the shaft and the bearing is provided between the outboard motor main body and the cooler. the rocking mechanism comprises a pair of connecting parts each having the shaft and the bearing and spaced apart from each other;
2. An outboard motor according to claim 1, wherein said cooling passage has an outward path passing through one of said pair of connecting portions and a return path passing through the other. the shaft has an in-shaft flow path formed inside the shaft;
wherein the connecting portion has an inner bearing channel formed between an inner surface of the bearing and an outer surface of the shaft and communicating with the inner shaft channel;
3. An outboard motor according to claim 1, wherein the in-shaft channel and the in-bearing channel are included in the cooling channel. 4. The ship according to claim 3, wherein the in-shaft flow path is branched into a plurality of radial flow paths extending in the radial direction of the shaft and each communicating with the in-bearing flow path. outside machine. the swivel case has a first connection port through which the cooling passage passes and which is connected to the outboard motor main body,
the outboard motor main body has a second connection port to which the first connection port is coaxially connected,
The rocking mechanism moves a pipe member coaxially inserted into both the first connection port and the second connection port, and between the pipe member and both the first connection port and the second connection port. and a sealing member for sealing,
A center line passing through each of the first connection port, the pipe member, and the second connection port is parallel to an assembly direction of the swivel case with respect to the outboard motor main body. 1. The outboard motor according to claim 1.

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