JP2007315497A - Outboard motor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent an oil filter and a control valve form clogging by foreign matters by collecting the foreign matters generated in a torque converter of an outboard motor by centrifugal separation from working oil. <P>SOLUTION: In the outboard motor having an engine E mounted to an upper part of a casing 1 by longitudinally installing a crankshaft 17 thereof, and having the longitudinally-installed torque converter T and a longitudinally-installed output shaft 20 connected to the crankshaft 17 via the torque converter T provided in the casing 1, the torque converter T comprises a turbine runner 26 connected to a pump impeller 25 and the output shaft 20, a transmission cover 29 arranged to cover the back surface of the turbine runner 26 and connecting the crankshaft 17 and the pump impeller 25, and an annular suck shape foreign matter pocket 89 opening upward is formed between mutually fitted and welded diameter expansion parts 85 and circumference walls 86 of the pump impeller 25 and the transmission cover 29. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  In the present invention, the engine is mounted on the upper part of the casing connected to the swivel case via the swivel shaft, the crankshaft is vertically installed, and the cylinder block is mounted in the direction opposite to the swivel shaft. A vertical torque converter, a vertical output shaft connected to the crankshaft via the torque converter, a propeller shaft horizontally disposed below the output shaft, and a connection between the output shaft and the propeller shaft The present invention relates to an improvement of an outboard motor provided with a forward / reverse switching mechanism.

Such an outboard motor is already known as disclosed in Patent Document 1.
US Pat. No. 3,407,600

  The outboard motor torque converter disclosed in Patent Document 1 does not have a means for removing foreign matter that flows into the torque converter, so that the foreign matter may clog an oil filter, a control valve, or the like. is there.

  The present invention has been made in view of the above points, and the foreign matter that has flowed into the torque converter is collected by centrifuging it from the working oil with a simple structure using the vertical placement of the torque converter. It is an object of the present invention to provide the outboard motor in which clogging of a filter, a control valve, etc. does not occur.

  In order to achieve the above object, the present invention has an engine placed on the upper part of a casing connected to a swivel case via a swivel shaft, the crankshaft is placed vertically, and the cylinder block is directed in a direction opposite to the swivel shaft. In the same casing, a vertical torque converter, a vertical output shaft connected to the crankshaft via the torque converter, a propeller shaft horizontally disposed below the output shaft, and In an outboard motor provided with a forward / reverse switching mechanism that connects between an output shaft and a propeller shaft, a torque converter includes a pump impeller, a turbine runner that is disposed opposite to the pump impeller and coupled to the output shaft, , A stator arranged between the pump impeller and the turbine runner, and a clutch arranged so as to cover the rear surface of the turbine runner. It is composed of a transmission cover that connects the pump shaft and the pump impeller, and opens upward on the inner peripheral surface of the pump impeller and the maximum diameter of the transmission cover in order to capture the foreign matter centrifuged from the working oil in the torque converter. The first feature is that an annular and bag-like foreign substance reservoir is formed.

  According to the present invention, in addition to the first feature, the pump impeller and the transmission cover are fitted to the female fitting surface of the inner peripheral portion of the transmission cover on the male fitting surface of the outer periphery of the enlarged diameter portion extending to the outer peripheral end of the pump impeller. The surface is fitted to each other and joined by welding between the enlarged diameter portion and the peripheral wall portion, and an annular recess adjacent to the female fitting surface is formed on the inner peripheral surface of the peripheral wall portion, A second feature is that the enlarged diameter portion is formed with an extension wall that covers the annular recess from the inner peripheral side and serves as the foreign substance reservoir.

  Furthermore, in addition to the second feature, the third feature of the present invention is that the extension wall is formed in a thin wall that stands up from the inner peripheral edge of the enlarged diameter portion.

  In addition to the second feature of the present invention, the portion constituting the inner peripheral wall of the foreign substance reservoir of the enlarged diameter portion is squeezed radially inward, and the portion constituting the outer peripheral wall of the foreign substance reservoir of the peripheral wall portion The fourth feature is that is expanded radially outward.

  According to the first feature of the present invention, an annular and bag-like foreign substance reservoir that opens upward is formed on the inner peripheral surface of the maximum diameter portion of the pump impeller and the transmission cover. The foreign matter that has flowed into the cylinder can be efficiently stored in the annular foreign matter reservoir by centrifuging from the working oil. In addition, the torque converter is vertically placed with its axis vertical, and the foreign substance reservoir is in the form of a bag. Therefore, foreign substances once stored in the foreign substance reservoir are reliably captured even when the torque converter is stopped. Since it can be continued, clogging of oil filters and control valves due to foreign matter can be prevented.

  According to the second feature of the present invention, the foreign substance reservoir can be easily formed by utilizing the coupling portion between the pump impeller and the transmission cover.

  According to the third feature of the present invention, the capacity of the foreign substance reservoir can be increased without increasing the outer diameter of the torque converter.

  According to the fourth feature of the present invention, the throttle portion and the extended portion serve as reinforcing ribs, and the strength of the shell and the transmission cover can be enhanced, and the durability against centrifugal force can be enhanced.

  Embodiments of the present invention will be described below based on preferred embodiments of the present invention shown in the drawings.

  1 is a side view of an outboard motor according to an embodiment of the present invention, FIG. 2 is an enlarged cross-sectional view of part 2 of FIG. 1, FIG. 3 is an enlarged view of a torque converter part of FIG. 5 and 5 are enlarged views of part 5 (foreign material reservoir) of FIG. 3, FIG. 6 shows a modified example of the foreign material reservoir, a corresponding diagram with FIG. 5, and FIG. 7 shows another modified example of the foreign material reservoir, FIG. FIG.

  In FIG. 1, a casing 1 of an outboard motor O is mounted with a water-cooled multi-cylinder four-stroke engine E on the top and supports a propeller shaft 3 having a propeller 2 at the rear end at the bottom. Immediately before the casing 1, a vertical swivel shaft 6 attached to the casing 1 via the upper arm 4 and the lower arm 5 is disposed. It is connected to a stern bracket 8 clamped to Bt via a tilt shaft 9 in the horizontal direction. Therefore, the casing 1 can be steered left and right around the swivel shaft 6 and can be tilted up and down around the tilt shaft 9. Reference numeral Ef is a detachable engine hood that covers the engine E.

1 and 2, the casing 1 includes an extension case 10, a mount case 11 that is bolted to the upper end of the extension case 10, and a gear case 12 that is bolted to the lower end of the extension case 10. The extension case 10 includes an upper case 10a and a lower case 10b coupled to the upper case 10a. A mount case 11 is coupled to the upper end surface of the upper case 10a by a plurality of bolts 16 ₃ .

The casing 1 further includes an annular lower distance member 13, a bearing bracket 14, and an annular upper distance member 15 that are sequentially stacked on the upper end of the mount case 11. The engine E is mounted on the upper distance member 15 with its crankshaft 17 placed vertically, that is, in the vertical direction and with the cylinder block 18 directed rearward. At that time, the bottom wall of the cylinder block 18 and the crankcase 19 of the engine E, bearing bracket 14 and upper distance member 15 are secured by a plurality of bolts 16 ₁ and the lower distance member 13, the bearing bracket 14 and upper distance member 15 are fixed to each other by a plurality of bolts 16 ₂ .

  In the annular upper distance member 15, a vertically placed torque converter T with its axis line oriented in the vertical direction is disposed, and the output shaft 20 connected to the crankshaft 17 via the torque converter T is vertically connected to the extension case 10. Arranged in place.

  The gear case 12 horizontally supports the propeller shaft 3 having the propeller 2 attached to the rear outer end thereof, and houses a forward / reverse switching mechanism 21 for connecting the output shaft 20 to the propeller shaft 3.

  Thus, during operation of the engine E, the power is transmitted from the crankshaft 17 to the output shaft 20 via the torque converter T and further to the propeller shaft 3 via the forward / reverse switching mechanism 21 to drive the propeller 2. . At that time, the rotation direction of the propeller 2 is controlled by the forward / reverse switching mechanism 21.

  In the extension case 10, an oil tank 22 (see FIGS. 1 and 4) that opens toward the mount case 11 is integrally formed in the upper case 10 a of the extension case 10, and lubricates the engine E and the torque converter T. The oil 23 that is commonly used for the operation of is stored in the oil tank 22.

  As clearly shown in FIG. 3, the torque converter T includes a pump impeller 25, a turbine runner 26 disposed above the pump impeller 25, a stator 27 disposed between the inner peripheral portions thereof, and the three It is comprised with the circulation circuit 28 for hydraulic oil defined between the impellers 25-27. These three-blade wheels 25 to 27 are arranged such that a common axis is oriented in the vertical direction in the same manner as the crankshaft 17 and the output shaft 20.

A transmission cover 29 that covers the upper surface of the turbine runner 3 is integrally connected to the pump impeller 25. A starting ring gear 30 is fixed to the outer peripheral surface of the transmission cover 29, and a steel plate drive plate 31 fixed to the lower end of the crankshaft 17 by a plurality of first bolts 32 ₁ in an annular arrangement. Are fixed by a plurality of second bolts 32 ₂ in an annular arrangement. The torque converter T is suspended from the crankshaft 17 via the drive plate 31. At this time, a dish-like recess 29a for receiving the head of the first bolt 32 ₁ is formed at the center of the transmission cover 29, and the drive plate 31 is disposed close to the transmission cover 29.

  A cup-shaped support cylinder 34 that is slidably fitted into a support hole 33 that opens at the center of the lower end surface of the crankshaft 17 is fixed to the center of the transmission cover 29. The output shaft 20 has an upper end extending into the support cylinder 34, and the upper end is supported in the support cylinder 34 via a bearing bush 35. A hub 26 h of the turbine runner 26 is attached to the output shaft 20. Splined. A hollow stator shaft 37 supported by a needle bearing 36 is disposed on the outer periphery of the output shaft 20, and a known free wheel 38 is interposed between the stator shaft 37 and the hub 27 h of the stator 27. Be dressed.

  On the outer periphery of the stator shaft 37, a hollow pump shaft 39 that is integrally connected to the pump impeller 25 and extends downward is disposed. The pump shaft 39 is supported on the bearing bracket 14 via an upper ball bearing 43 on the outer peripheral side, and an oil pump 41 driven at the lower end of the pump shaft 39 is formed on the lower surface of the bearing bracket 14. A pump cover 42 attached to the pump housing 40 and covering the lower surface of the oil pump 41 is bolted to the lower surface of the bearing bracket 14. At this time, the pump shaft 39 is slidably fitted to the inner race of the upper ball bearing 43, and is also slidably fitted to the rotor of the oil pump 41. Thus, the lower end portion of the torque converter T is free to move in the axial direction.

  An oil seal 45 that attaches a lip to the outer peripheral surface of the pump shaft 39 immediately above the ball bearing 43 is attached to the upper end portion of the bearing bracket 14.

  The stator shaft 37 has an enlarged diameter wall 37a at its lower end, and a flange 37b fixed to the pump cover 42 with a bolt 46 is integrally formed on the outer circumference of the enlarged diameter wall 37a. A lower ball bearing 44 that supports the output shaft 20 is mounted on the periphery.

  Thus, the pump shaft 39 is supported on the bearing bracket 14 via the upper ball bearing 43, and the output shaft 20 is supported on the diameter-enlarging wall 37a of the stator shaft 37 via the lower ball bearing 44. The support of the pump shaft 39, the stator shaft 37, and the output shaft 20 becomes rational, and the vertical fluid transmission device including the torque converter T and the output shaft 20 can be made compact.

  Since the oil pump 41 is attached to the bearing bracket 14 using the space between the upper and lower ball bearings 43, 44, the vertical fluid transmission device with the oil pump 41 can be configured in a compact manner.

  Thrust needle bearings 47 and 47 ′ are interposed between the pump impeller 25, the stator 27, and the hubs 25 h and 26 h of the turbine runner 26, respectively, and between the hub 26 h and the transmission cover 29 of the turbine runner 26. Also, a thrust needle bearing 48 is interposed.

  2 to 4, the oil pump 41 sucks up the stored oil 23 in the oil tank 22 through the suction oil passage 50 and discharges it to the first supply oil passage 51. The oil discharged to the first supply oil passage 51 is filtered by an oil filter 53 provided in the middle of the first supply oil passage 51 and then supplied to the lubrication part of the engine E. The lubricated oil flows down to the bottom of the crankcase 19 of the engine E, and returns to the oil tank 22 through the first return oil passage 54. A relief oil passage 55 that reaches the suction oil passage 50 is branched from the first supply oil passage 51 upstream of the oil filter 53, and the oil pressure of the first supply oil passage 51 is a specified value in the relief oil passage 55. A relief valve 56 is provided that opens when the above is reached.

  The first supply oil passage 51 is connected to a second supply oil passage 52 that supplies the working oil to the torque converter T. On the suction side of the oil pump 41, the second supply oil passage 52 that induces the reflux oil from the torque converter T is connected. A return oil passage 59 is connected.

  As shown in FIG. 3, between the turbine runner 26 and the transmission cover 29, a clutch oil chamber 81 communicating with the circulation circuit 28 at the outer peripheral portion is defined. At this time, the transmission cover 29 is integrally formed with a cylindrical peripheral wall portion 86 surrounding the turbine runner 26, and the shell 25 s of the pump impeller 25 has a radially expanded wall extending radially from the outer peripheral end thereof. 85 is integrally formed, and the peripheral wall portion 86 and the enlarged diameter wall 85 are connected to each other, and the outer peripheral portion of the clutch chamber 81 having a diameter larger than that of the circulation circuit 28 by the peripheral wall portion 86 and the enlarged diameter wall 85. Is defined. The clutch chamber 81 is provided with a lockup clutch L that can directly connect the turbine runner 26 and the transmission cover 29.

  The lock-up clutch L is a disc-shaped circulation circuit disposed in the clutch oil chamber 81 so as to partition the clutch oil chamber 81 into an inner chamber 81a on the turbine runner 26 side and an outer chamber 81b on the transmission cover 29 side. A clutch piston 82 having a diameter larger than 28 is provided. The clutch piston 82 includes an annular friction lining 83 having a diameter larger than that of the circulation circuit 28 on a side surface facing the inner wall of the transmission cover 29, and a connection position for pressing the friction lining 83 against the inner wall of the transmission cover 29; The hub 82h of its own is slidably supported on the outer peripheral surface of the hub 26h of the turbine runner 26 so that the hub 82h can move between a non-connection position separated from the inner wall. Thus, the lock-up clutch L is configured to have a larger diameter than the circulation circuit 28. As shown in FIG. 2, the torque converter T is disposed such that the pump impeller 25 and the turbine runner 26 are close to the swivel case 7 and the lock-up clutch L is above the swivel case 7.

  An annular rim portion 82r bent toward the turbine runner 26 is integrally formed at the outer peripheral end of the clutch piston 82, and the clutch piston 82 and the turbine runner 26 are connected to each other in a buffered manner in the rim portion 82r. A torque damper D is provided.

  Here, with reference to FIG.3 and FIG.5, the coupling structure of the said enlarged diameter wall 85 and the surrounding wall part 86 is demonstrated.

  A male fitting surface 85a and an annular positioning step 85b extending in the radial direction from the inner end of the male fitting surface 85a are formed on the outer periphery of the enlarged wall 85. On the other hand, the transmission cover 29 is thicker than the shell 25s. On the inner periphery of the peripheral wall portion 86 formed on the outer periphery of the transmission cover 29, there is a female fitting surface 86a connected to the outer end, An annular recess 86b adjacent to the inner end of the female fitting surface 86a is formed.

  Thus, when the shell 25s and the transmission cover 29 are coupled, the male fitting surface 85a of the enlarged diameter wall 85 of the shell 25s and the female fitting surface 86a of the peripheral wall portion 86a of the transmission cover 29 are fitted together. Thus, the distal end surface of the peripheral wall portion 86 is brought into contact with the positioning step portion 85 b of the enlarged diameter wall 85. Thereafter, a fillet weld 87 extending over the entire circumference is formed between the distal end surface of the peripheral wall portion 86 and the outer peripheral surface of the enlarged diameter wall 85. Thus, the shell 25s and the transmission cover 29 are coupled to each other.

  In addition, a thin, cylindrical extension wall 88 is integrally formed on the enlarged diameter wall 85 so as to stand up from the inner peripheral edge thereof and cover the annular recess 86b from the inner peripheral side. A bag-like foreign substance reservoir 89 opened inside is formed. Thus, an annular foreign substance reservoir 89 that opens upward is formed on the inner periphery of the maximum diameter portion of the pump impeller 25 and the transmission cover 29.

  2 and 3 again, the output shaft 20 has a bottomed vertical hole 61 located at the center thereof, and this vertical hole 61 is connected to the outer chamber 81b of the clutch oil chamber 81 through the thrust needle bearing 48. A lateral hole 62 is provided. A cylindrical oil passage 69 communicated with the inner peripheral portion of the circulation circuit 28 between the output shaft 20 and the stator shaft 37 via the lateral hole 62 of the stator shaft 37 and the thrust needle bearings 47 and 47 ′ and the needle bearing 36. Is defined. First and second control oil passages 63 and 64 are connected to the vertical hole 61 and the cylindrical oil passage 69, respectively. The first control oil passage 63 and the second control oil passage 64 are as shown in FIG. The lockup control valve 65 is alternately connected to the second supply oil passage 52 and the second return oil passage 59.

  As shown in FIG. 2, the suction oil passage 50 has a suction pipe 50 a that is suspended by the bearing bracket 14 and enters a lower end portion into the oil tank 22, and an upper end of the suction pipe 50 a that is provided in the bearing bracket 14. It is constituted by a lateral oil passage 50 b communicating with the suction port of the oil pump 41.

  Further, as shown in FIG. 2, the bottom wall of the crankcase 19 of the engine E is provided with an opening 66 through which oil that has been lubricated by the engine E flows out. The opening 66 is formed by the upper distance member 15 and the bearing. The bracket 14 is opened to the upper surface of the mount case 11 through a series of longitudinal through holes 67 provided in the outer peripheral portion of the bracket 14 and the inner portion of the annular lower distance member 13. The mount case 11 is provided with an opening 68 that opens toward the oil tank 22. Thus, the oil that has finished lubricating the engine E and has flowed down to the bottom of the crankcase 19 flows down onto the mount case 11 through the opening 66, the through hole 67, and the opening 68. It returns to the oil tank 22 through the opening 68. The opening 66, the through hole 67, and the opening 68 constitute the first return oil passage 54 (see FIG. 4).

  2 and 3, the output shaft 20 includes the upper output shaft 20a having the vertical hole 61 and supported by the lower ball bearing 44, and the forward / reverse switching mechanism 21 (see FIG. 1). And a lower output shaft 20b connected to the lower output shaft 20b. The upper output shaft 20 a is integrally formed with a flange 73 that is supported on the upper end surface of the inner race of the lower ball bearing 44 that is mounted on the inner periphery of the enlarged wall 37 a of the stator shaft 37. A retaining ring 74 that supports the lower end surface is locked to the inner peripheral surface of the enlarged-diameter wall 37a. Therefore, unless the retaining ring 74 is removed, the upper output shaft 20a is prevented from coming out downward from the center of the torque converter T.

  A spline shaft 80 is formed at the upper end of the lower output shaft 20b, and the upper and lower output shafts 20a and 20b are connected to each other by fitting the spline shaft 80 into the spline hole 77.

  Next, the operation of this embodiment will be described.

  In the engine idling or extremely low speed operation region, the lockup control valve 65 connects the first control oil passage 63 to the second supply oil passage 52 while the second control oil passage 64 is connected to the second control oil passage 64 as shown in FIG. It is controlled by an electronic control unit (not shown) so as to be connected to the two return oil passages 59.

  Thus, the output torque of the crankshaft 17 of the engine is transmitted to the drive plate 31, the transmission cover 29, and the pump impeller 25, which is driven to rotate, and the oil pump 41 is also driven. When the oil pump 41 is driven, the oil 23 in the oil tank 22 is sucked up through the suction oil passage 50, discharged to the first supply oil passage 51 and the second supply oil passage 52, and discharged to the first supply oil passage 51. The oil thus supplied is supplied to the lubrication part of the engine E as described above.

  On the other hand, the oil supplied to the second supply oil passage 52 is the working oil, the outer chamber 81b of the clutch oil chamber 81 through the first control oil passage 63, the vertical hole 61 and the horizontal hole 62 from the lockup control valve 65, After sequentially flowing into the circulation circuit 28 through the inner chamber 81a and filling the circuit 28, the second control oil path 64 is transferred through the lateral hole 75 and the cylindrical oil path 69, and the second return from the lockup control valve 65. Reflux to oil path 59.

  Thus, in the clutch oil chamber 81, the outer chamber 81b has a higher pressure than the inner chamber 81a due to the flow of the working oil as described above, and the clutch piston 82 moves away from the inner wall of the transmission cover 29 due to the pressure difference. Since it is pressed, the lock-up clutch L is in a disconnected state and allows the pump impeller 25 and the turbine runner 26 to rotate relative to each other. Therefore, when the pump impeller 25 is rotationally driven from the crankshaft 17, the working oil that fills the circulation circuit 28 circulates in the circulation circuit 28 as shown by the arrow, so that the rotational torque of the pump impeller 25 is transferred to the turbine runner 26. Is transmitted, and the output shaft 20 is driven. At this time, if a torque amplifying action is generated between the pump impeller 25 and the turbine runner 26, a reaction force associated therewith is borne by the stator 27, and the stator 27 is fixed by the locking action of the free wheel 38. Since the propeller 2 can be driven strongly by such torque amplification action of the torque converter T, the start and acceleration of the ship can be effectively enhanced.

  When the torque amplification operation is finished, the stator 27 rotates in the same direction together with the pump impeller 25 and the turbine runner 26 while idling the free wheel 38 due to the reversal of the torque direction received by the stator 27.

  When the torque converter T is in such a coupling state, the lockup control valve 65 is switched by the electronic control unit. As a result, the hydraulic oil supplied to the second supply oil passage 52 flows into the circulation circuit 28 from the lock-up control valve 65 through the second control oil passage 64, contrary to the previous time, and fills the circuit 28. After that, it moves to the inner chamber 81a of the clutch oil chamber 81 and fills the inner chamber 81a. On the other hand, the outer chamber 81b of the clutch oil chamber 81 is opened to the second return oil passage 59 via the first control oil passage 63 and the lock-up control valve 65. Becomes higher than the outer chamber 81b, the clutch piston 82 is pressed toward the transmission cover 29 by the pressure difference, the friction lining 83 is pressed against the inner wall of the transmission cover 29, and the lockup clutch L is connected. Then, since the rotational torque transmitted from the crankshaft 17 to the pump impeller 25 is mechanically transmitted from the transmission cover 29 to the turbine runner 26 via the clutch piston 82 and the torque damper D, the pump impeller 25 and the turbine runner 26 are transmitted. Is in a directly connected state, and the output torque of the crankshaft 17 can be efficiently transmitted to the output shaft 20, thereby reducing fuel consumption.

  In particular, since the lock-up clutch L is configured to have a larger diameter than the circulation circuit 28 of the torque converter T, the lock-up clutch L is brought into the connected state without specially increasing the size of the pump impeller 25 and the turbine runner 26. Thus, a large torque can be efficiently transmitted from the crankshaft 17 to the output shaft 20 via the lockup clutch L. In addition, since the lockup clutch L having a diameter larger than that of the circulation circuit 28 is disposed above the pump impeller 25 and the turbine runner 26, the lockup clutch L is disposed above the swivel case 7, so that the pump The impeller 25 and the turbine runner 26 can be disposed close to the swivel case 7, and the outboard motor O can be made compact.

  Further, since the outer peripheral portion of the clutch chamber 81 is defined by the peripheral wall portion 86 of the transmission cover 29 coupled to each other and the enlarged diameter wall 85 of the shell 25s of the pump impeller 25, a clutch having a larger diameter than the circulation circuit 28 is formed. The chamber 81 can be easily formed, and the friction engagement portion of the lock-up clutch L having a diameter larger than that of the circulation circuit 28, that is, the friction lining 83 of the clutch piston 82, and the clutch lip 83 are opposed to the outer periphery of the clutch chamber 81. The inner wall portion of the transmission cover 29 can be easily disposed. In addition, the diameter-enlarging wall 85 serves to reinforce the outer periphery of the pump impeller 25 by extending in the radial direction from the outer peripheral end of the shell 25s of the pump impeller 25, and contributes to improving the durability of the pump impeller 25. obtain.

  Since the oil circulates through the second supply oil path 52 and the second return oil path 59 between the circulation circuit 28 of the torque converter T and the oil tank 22 disposed below the torque circuit T, the torque converter T has an oil reservoir. It is not necessary to provide the air conditioner, and it is possible to reduce the size of the circulating oil and promote the cooling of the circulating oil and prevent its deterioration.

  In particular, the oil tank 22 disposed below the torque converter T is separated from the engine E, so that the heating by the engine E is small, and the capacity is relatively large without being interfered by the engine E and the torque converter T. The cooling of the circulating oil can be further promoted, for example, by increasing the oil flow rate to the circulation circuit 28. In addition, the engine E, the torque converter T, and the oil tank 22 are arranged in that order, and the torque converter T can be configured compactly without being interfered with the oil tank 22. The outer unit O can be made slim and lightweight.

  The oil supplied to the circulation circuit 28 is the oil discharged from the oil pump 41 for lubrication of the engine E, so that the oil tank 22 and the oil pump 41 are connected to supply the oil to the circulation circuit 28. There is no need for special expansion, and it is possible to avoid the outboard motor O from being enlarged and complicated in structure.

In the torque converter T, the turbine runner 26 is disposed above the pump impeller 25, and a transmission cover 29 covering the turbine runner 26 is integrally connected to the shell 25s of the pump impeller 25. The torque converter T is suspended from the crankshaft 17 via the drive plate 31 by fastening the outer periphery of the drive plate 31 whose center is fastened to the lower end of the shaft 17 with the first bolt 32 ₁ with the second bolt 32 _2. Since the lower end of the torque converter T is freed, the entire weight of the torque converter is borne by the crankshaft 17 that is firmly supported by the crankcase 19 of the engine E. The use of dedicated bearings that support the full weight is not necessary, and costs can be reduced. Moreover, it is possible to prevent an excessive thrust load from being applied to the torque converter T and the crankshaft 17 even during thermal expansion in the axial direction of the torque converter T, and the drive plate 31 made of a steel plate has appropriate elasticity. When the ship vibrates up and down, the impact on the torque converter T can be mitigated by appropriate elastic deformation of the drive plate 31, which can contribute to improvement in durability.

  The output shaft 20 includes an upper output shaft 20a that is spline-fitted to the hub 26h of the turbine runner 26, and a lower output shaft that is spline-fitted to the lower end portion of the upper output shaft 20a and connected to the forward / reverse switching mechanism 21. Since the flange 73 formed on the upper output shaft 20a is supported by the lower ball bearing 44 in order to support the downward load of the upper output shaft 20a, the weight of the output shaft 20 is converted into the torque converter. It is possible to avoid burdening T, the drive plate 31 and the crankshaft 17 and to prevent the thermal expansion in the axial direction of the torque converter T from affecting the output shaft 20. Further, the thermal expansion in the axial direction of the torque converter T, the upper output shaft 20a, and the lower output shaft 20b can be absorbed by the respective spline fitting portions, thereby preventing the occurrence of excessive stress. In addition, since the lower ball bearing 44 supports only a downward load including the weight of the upper output shaft 20a, the load is relatively small and the durability can be improved.

  In addition, since the thrust needle bearing 47 is interposed between the hubs 25 h and 27 h of the pump impeller 25 and the stator 27, the weight of the turbine runner 26 and the stator 27 is easily loaded on the pump impeller 25 via the thrust needle bearing 47. Thus, the durability of the torque converter T can be improved.

Furthermore, since a dish-shaped recess 29 a that receives the head of the first bolt 32 ₁ is formed at the center of the transmission cover 29, the head of the first bolt 32 ₁ is received in the dish-shaped recess 29 a of the transmission cover 29. Thus, the drive plate 31 and the transmission cover 29 that are interfered with the head of the first bolt 32 ₁ can be disposed close to each other, and the power unit including the engine E and the torque converter T can be made compact.

  Further, even if foreign matter flows into the torque converter T and the lockup clutch L, the foreign matter is centrifuged from the working oil while circulating through the circulation circuit 28 together with the working oil, and the pump impeller 25 and the transmission are transmitted. The cover 29 can be efficiently accommodated in an annular foreign substance reservoir 89 having an upward opening formed on the inner peripheral surface of the maximum diameter portion. In addition, since the torque converter T is vertically placed with the axis thereof vertical, and the foreign substance reservoir 89 is formed in a bag shape, the foreign substance once accommodated in the foreign substance reservoir 89 is retained even when the torque converter T is stopped. The oil filter 53 and the control valve 65 can be prevented from being clogged with foreign matter.

  Further, the foreign substance reservoir 89 is formed by an annular recess 86b and an extension wall 88 respectively formed on the enlarged diameter wall 85 of the pump impeller 25 and the peripheral wall portion 86 of the transmission cover 29 which are fitted and welded to each other. This can be easily formed.

  Further, according to the present invention, the extension wall 88 is formed to have a thin wall standing from the inner peripheral edge of the enlarged diameter wall 85, so that the capacity of the foreign substance reservoir 89 can be increased without particularly increasing the outer diameter of the torque converter T. it can.

  The engine E includes a bearing bracket 14 that supports the pump shaft 39 of the torque converter T, an upper distance member 15 that is connected to the upper end of the bearing bracket 14 and surrounds the torque converter T, and a lower distance that is connected to the lower end of the bearing bracket 14. Since it is attached to the mount case 11 via the member 13, the engine E can be easily attached to the mount case 11 without being interfered by the torque converter T, and the assemblability is good.

  FIG. 6 shows a modified example of the foreign substance reservoir 89. The annular extension wall 88 constituting the inner peripheral wall of the foreign substance reservoir 89 is made of a thin steel plate, and this is the inner peripheral surface of the enlarged wall 85 of the shell 25s. It was welded to. According to this structure, the thickness of the expanded wall 85 facing the foreign material reservoir 89 is the lateral width of the foreign material reservoir 89, and a larger capacity foreign material reservoir 89 can be obtained.

  FIG. 7 shows another modified example of the foreign substance reservoir 89. A throttle part 851 constituting the inner peripheral wall of the foreign substance reservoir 89 of the enlarged wall 85 of the shell 25s is throttled inward in the radial direction, and the transmission cover 29 is shown. The expanded portion 861 constituting the outer peripheral wall of the foreign matter reservoir 89 of the peripheral wall portion 86 is expanded radially outward. According to this structure, the volume of the foreign matter reservoir 89 is increased and the portions 851 and 861 are also increased. As a reinforcing rib, the strength of the shell 25s and the transmission cover 29 can be increased, and the durability against centrifugal force can be increased.

  The present invention is not limited to the above embodiment, and various design changes can be made without departing from the scope of the invention. For example, the oil tank 22 may be divided into a working oil for the torque converter T and a lubricating oil for the engine E, and each oil may be suitable for the application.

The side view of the outboard motor which concerns on the Example of this invention. FIG. 2 is an enlarged sectional view of a part 2 in FIG. 1. The torque converter part enlarged view of FIG. 1 is a hydraulic circuit diagram including an oil pump. FIG. 5 is an enlarged view of part 5 (foreign material reservoir) in FIG. 3. FIG. 6 is a diagram corresponding to FIG. 5 showing a modified example of the foreign substance reservoir. FIG. 6 is a correspondence diagram with FIG. 5 showing another modified example of the foreign substance reservoir.

Explanation of symbols

E ... Engine O ... Outboard motor T ... Torque converter 1 ... Casing 3 ... Propeller shaft 6 ... · Swivel shaft 7 ··· swivel case 17 · · · crankshaft 18 · · · cylinder block 20 · · · output shaft 25 · · · pump impeller 26 · · · Turbine runner 27 ··· Stator 29 ··· Transmission cover 85 ··· Diameter-expanded portion 85a ··· Male fitting surface 86 · · · Peripheral wall portion 86a ··· Female fitting Joint surface 87... Welded portion 88... Extension wall 89 .. foreign matter reservoir 851... Throttle portion 861.

Claims (4)

The engine (E) is placed on the upper part of the casing (1) connected to the swivel case (7) via the swivel shaft (6), the crankshaft (17) is placed vertically, and the cylinder block (18) is placed on the swivel shaft. (6) Mounted in the opposite direction, and in the same casing (1), the vertical torque converter (T) and the vertical installation connected to the crankshaft (17) via this torque converter (T) Output shaft (20), a propeller shaft (3) disposed horizontally below the output shaft (20), and a forward / reverse switching mechanism for connecting the output shaft (20) and the propeller shaft (3) ( 21) and an outboard motor provided with
The torque converter (T) includes a pump impeller (25), a turbine runner (26) disposed opposite to the pump impeller (25) and connected to the output shaft (20), the pump impeller (25) and the turbine runner. (26) and a transmission cover (29) arranged so as to cover the rear surface of the turbine runner (26) and connecting the crankshaft (17) and the pump impeller (25). An annular and bag opening upward to capture foreign matter centrifuged from the working oil in the torque converter (T) on the inner peripheral surface of the maximum diameter portion of the pump impeller (25) and transmission cover (29) An outboard motor characterized by forming a foreign substance reservoir (89). The outboard motor according to claim 1,
The pump impeller (25) and the transmission cover (29) are connected to the male fitting surface (85a) on the outer periphery of the enlarged diameter portion (85) extending to the outer peripheral end of the pump impeller (25). (86) The inner wall female fitting surface (86a) is fitted to each other, and the enlarged-diameter portion (85) and the peripheral wall portion (86) are joined together by welding, and the peripheral wall portion (86) An annular recess (86b) adjacent to the female fitting surface (47) is formed on the inner peripheral surface of the inner diameter surface, while the enlarged diameter portion (85) covers the annular recess (86b) from the inner peripheral side. An outboard motor characterized in that an extension wall (88) that forms the foreign substance reservoir (89) is formed. The outboard motor according to claim 2,
The outboard motor characterized in that the extension wall (88) is formed in a thin wall standing up from the inner peripheral edge of the enlarged diameter portion (85). The outboard motor according to claim 2,
The portion (851) constituting the inner peripheral wall of the foreign substance reservoir (89) of the enlarged diameter portion (85) is squeezed radially inward, and the portion constituting the outer peripheral wall of the foreign substance reservoir 89 of the peripheral wall portion (86) An outboard motor characterized by extending (861) radially outward.

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