JPS6250698B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a speed reducing/reversing machine with a built-in planetary gear mechanism suitable for vessels such as fishing boats.

A conventional example of this type of speed reduction/reversing machine will be explained with reference to FIG. 1, which is a partial vertical cross-sectional view. In FIG. 1, a large gear 3 (helical gear) is rotatably supported on an output shaft 1 via a plain bearing 2 (sliding bearing).
The large gear 3 meshes with the small gear 5, and the small gear 5
The rotational force from the engine is transmitted through a clutch, etc. (not shown). Big gear 3
A cylindrical member 7 is fixed to the side surface of the cylindrical member 7 by bolts 6, and an internal gear 8 is formed on the inner circumferential surface of a portion of the cylindrical member 7 away from the large gear 3. For example, three planetary gears 10 (only one is shown) are meshed with the internal gear 8, and the planetary gears 10 are each connected via a support shaft 11 by a carrier 12 projecting radially outward from the output shaft 1. It is supported reversibly.
A portion of the sun gear 13 that is not shown is fixed to the case. However, according to the above structure, since the width l of the plain bearing 2 is narrow, it is difficult to accurately support the large gear 3 in a position coaxial with the output shaft 1.
Due to the radial load and thrust load applied from the small gear 5 to the large gear 3, a shift or inclination occurs between the center line of the large gear 3 and the center line of the output shaft 1, and as a result, the internal teeth of the sun gear 13 and the planetary gear 10 gear 8
The concentricity and parallelism of the gears become inconsistent, resulting in problems such as low power transmission efficiency and severe wear of each gear. Further, since the internal gear 8 protrudes from the large gear 3 in the axial direction, there is a problem in that when the large gear 3 is tilted, the internal gear 8 is largely displaced in the radial direction. Furthermore, since the large gear 3 and the planetary gear mechanism are arranged side by side in the longitudinal direction of the output shaft 1, there is a problem that the axial length of the entire device increases.

In order to solve the above-mentioned conventional problems, the present invention has the following features:
The large gear is formed of a cylindrical member, the planetary gear mechanism is placed inside the large gear in the radial direction, and both side edges of the large gear are supported by annular frames placed on both sides of the planetary gear mechanism. The following is an explanation using the drawings.

FIG. 2 is a vertical longitudinal sectional view, and in the embodiment shown in FIG. 2, the input shaft 15 and the output shaft 16 are
The support shaft 18 is arranged horizontally and concentrically at the bottom of the case 17 , and a support shaft 18 is arranged parallel to the output shaft 16 at the top of the case 17 . A multi-plate clutch 20 is arranged around the support shaft 18 at a position close to a flywheel 19 of an engine (not shown), and a small gear 21 is arranged at a position away from the flywheel 19. Around the output shaft 16, a large gear 22 and a planetary gear mechanism 23 are arranged below the small gear 21. As will be described later, the rotational force transmitted from the flywheel 19 to the input shaft 15 is transferred to the multi-plate clutch 20 and the small gear 2.
1. Each part is configured so that the power is transmitted to the output shaft 16 via the large gear 22 and the planetary gear mechanism 23.

The outer periphery of an annular plate 24 is connected to the flywheel 19 via a pin 25.
The inner circumference of the input shaft 15 is fixed to the end surface of the cylindrical input shaft 15 with bolts 26 . Input shaft 15 is in case 17
The cylindrical member 2 is attached to the inner periphery of the hole 28 provided in the end wall 27 of the
9. Supported via a rolling bearing 30,
A helical gear 31 is formed on a portion of the input shaft 15 that protrudes into the case 17. A helical gear 32 is located above the gear 31, and both gears 31 and 32 mesh with each other via an intermediate gear (not shown). The cylindrical boss 33 of the gear 32 is supported on the inner periphery of the hole 35 in the case end wall 27 via a bearing 36.
One end of the support shaft 18 is fitted and fixed to the inner circumferential surface of the cylinder boss 33. The other end of the support shaft 18 is supported in a hole 38 of the other case end wall 37 via a bearing 40. The holes 35, 38 are covered by covers 41, 42, respectively, and each cover 41, 42 is bolted to the outer surface of the corresponding case end wall 27, 37.

The outer peripheral drum 45 of the multi-plate clutch 20 is fixed to the end face of the helical gear 32 by bolts 47 together with the outer peripheral portion of an annular pressure plate 46. Inside the drum 45, a plurality of friction plates 48 and plates 49 are arranged alternately. The protrusions on the outer circumference of the friction plate 48 are slidably fitted into grooves in the axial direction provided on the inner circumferential surface of the outer circumferential drum 45, and the protrusions on the inner circumference of the plate 49 are fitted in the grooves in the axial direction provided on the inner circumferential drum 50. It is slidably fitted into the groove of. The piston 51 is slidably fitted between the inner peripheral surface of the rim of the gear 32 and the outer peripheral surface of the support shaft 18. A compression coil spring 52 is compressed between the annular stepped portion of the support shaft 18 and the piston 51 inside the inner peripheral drum 50 . piston 51
A hydraulic chamber 53 is formed between the and boss 33, and the hydraulic chamber 53 receives oil via an oil passage 54 in the support shaft 18, an oil passage 55 in the cover 42, a pipe 56 outside the case 17, and a hydraulic control valve 57. It is connected to pump 58.
Another oil passage 59 is provided within the support shaft 18, and the oil passage 59 opens on the inside of the multi-plate clutch 20 and the pinion 21.

The pinion 21 (a small-diameter helical gear) is rotatably supported by the support shaft 18 via a bush, and the inner drum 50 is formed by an integral extension of the end of the pinion 21 on the piston 51 side. has been done.

A large gear 22 (a large diameter helical gear) that meshes with the small gear 21 is formed of a cylindrical member 60 arranged concentrically with the output shaft 16 . Annular frames 61 and 62 are arranged on both sides of the cylindrical member 60.
Each frame 61, 62 has an annular notch 63, 64
are provided on the mutually opposing inner surfaces of the outer periphery, both notches 63 and 64 fit into the side surface of the cylindrical member 60 and the inner periphery of the side part, and the outer periphery of each frame 61 and 62 is secured by a plurality of bolts. It is fixed to the side surface of the cylindrical member 60. Each frame 61, 62 is made of a partially tapered plate-like member, and each inner peripheral part is further away from the cylindrical member 60 in the axial direction than the outer peripheral part, and between the inner peripheral parts of both frames 61, 62. The distance L is the cylindrical member 60
It is larger than the axial width of. The inner circumference of the frame 61 is supported by the output shaft 16 via a rolling bearing 65, and the inner circumference of the frame 62 is supported by a cylindrical boss 67 via a rolling bearing 66. The cylinder boss 67 is a member arranged concentrically with the output shaft 16, and has an outward flange 68 at its outer end, and an annular notch 69 provided on the outer circumference of the flange 68 fits into the hole 70 in the case end wall 37. It is fitted to the inro model. The outer periphery of the flange 68 has a cylindrical member 71 and an annular cover 7 arranged concentrically on the outside thereof.
2 and a plurality of bolts 73 to the case end wall 37.
is fixed.

The inner periphery of the cylindrical member 60 having the large gear 22 forms an internal gear 74, and for example, three planetary gears 75 meshing with the internal gear 74 are arranged around the output shaft 16. Each planetary gear 75 is supported by a support shaft 76 parallel to the output shaft 16 via a bush 77, and the end of the support shaft 76 on the annular frame 61 side is connected to a carrier 78 that integrally projects from the output shaft 16 in the radial direction. It is firmly fitted and fixed into the hole. Support shaft 7
The other end of 6 is fitted and fixed into a hole in an annular plate 79, and the annular plate 76 is fitted with a stepped bolt 80.
is fixed to the carrier 78 and positioned in the axial direction. Bolt 80 is output shaft 1
Two planetary gears 75, 7 adjacent in the circumferential direction of 6
It is located between 5. Between the planetary gear 75 and the carrier 78, and between the planetary gear 75 and the annular plate 7
Sliding metals 81, 81 are interposed between 9. A sun gear 82 that meshes with the planetary gear 75 is formed in a portion where the cylindrical boss 67 is extended to the inside of the cylindrical member 60.

The outer circumferential surface of the end of the output shaft 16 protruding from the case 17 has a taper, and a joint flange 83 is fitted to the tapered outer circumferential surface. A flange 83 is fixed to the output shaft 16. The flange 83 is connected to a flange of a propeller drive shaft (not shown). Flange 8 of output shaft 16
The portion near 3 is supported by the inner circumferential surface of the aforementioned cylindrical member 71 via a bearing 86. The opposite end of the output shaft 16 is supported by the inner circumferential surface of the input shaft 15 via a bearing 87, and the portion near the bearing 87 is supported by the inner circumference of the rim of the helical gear 31 via a bearing 88. supported on the surface.

A circular plate 89 is fixed to the inner circumference of the input shaft 15 in a liquid-tight manner, and an oil chamber 90 is formed between the plate 89 and the output shaft 16. On the end face of the output shaft 16, a circular plate 91 is attached to a bolt 91' to prevent the inner race of the bearing 87 from coming off.
A series of oil passages 92 are formed inside the plate 91 and the output shaft 16, one end of which communicates with the oil chamber 90. The other end of the oil passage 92 extends in the radial direction inside the flange 68 and opens to the outer peripheral surface of the output shaft 16. A radially extending oil passage 93 is provided inside the flange 68, and a radially outer end of the oil passage 93 is connected to the oil pump 58 via a pipe (not shown).

As shown in FIG. 3, which is an enlarged partial view of FIG. 2, an annular notch 94 is provided on the inner peripheral surface of the flange 68, and the inner end of the oil passage 93 opens in the inner peripheral surface of the notch 94. ing. An annular support member 95 is press-fitted into the notch 94 and fixed thereto. The support member 95 has an oil hole 96 on its outer circumference that communicates with the oil passage 93, and an annular groove 97 on its inner circumference that communicates with the oil hole 96 and the oil passage 92 in the output shaft 16. The support member 95 is made of a soft material such as bronze, and is slidably fitted onto the outer peripheral surface of an annular protrusion 98 provided on the output shaft 16. A spacer 99 for receiving thrust is arranged between the support member 95 and the protrusion 98 and the inner race of the bearing 86.

The effect will be explained. When the hydraulic chamber 53 is pressurized, the piston 51 moves toward the pressure plate 46, and the friction plate 48 and plate 49 are brought into pressure contact with each other. As a result, the outer drum 45 comes to rotate together with the inner drum 50 via the friction plate 48 and the plate 49, and the clutch 20 is connected. When the clutch is connected, the flywheel 19 to the plate 24
The rotational force transmitted to the input shaft 15 via the gear 3
1 and 32 to the clutch 20, and from the clutch 20 to the small gear 21 to the large gear 22.
Further, while the rotational force is transmitted between the gears 21 and 22, the rotation direction is reversed and decelerated. When the large gear 22 rotates, the internal gear 74 also rotates.
The planetary gear 75 meshing with the output shaft 16 revolves around the output shaft 16 while rotating around the support shaft 76 . Due to its revolution, the output shaft 16 is connected to the support shaft 76 and the carrier 78.
While the rotational force is thus transmitted via the planetary gear mechanism 23, the second stage of deceleration is performed.

To explain the lubrication of the bearings 87 and 88, the lubricating oil sent from the oil pump 57 to the oil passage 93 in the flange 68 passes through the oil hole 96 of the support member 95 and the annular groove 97 in FIG. The oil flows into the oil passage 92, enters the oil chamber 90 shown in FIG. 2 from the oil passage 92, and flows from the oil chamber 90 into the bearing 87 to lubricate the bearing 87. The lubricating oil leaked from the bearing 87 is transferred to the output shaft 16.
and the input shaft 15 through the gap 90' between the bearing 88 and the input shaft 15.
and lubricates the bearing 88. Bearing 88
The lubricating oil that flows out from the case 17 collects at the bottom of the case 17.

In the rotational force transmission operation, a radial load and a thrust load are applied from the small gear 21 to the large gear 22, but both side edges of the large gear 22 are connected to the annular frame 61,
62 at two locations separated by a wide distance L, the center line of the large gear 22 is prevented from tilting or shifting in the radial direction with respect to the center line of the output shaft 16 as much as possible. Therefore, the concentricity and parallelism of the internal gear 74 with respect to the planetary gear 75 and the sun gear 82 are kept extremely high. Therefore, the power transmission efficiency of the planetary gear mechanism 23 is maintained high, and wear of various parts is also significantly reduced.

In the conventional product shown in FIG. 1, if the large gear 3 is tilted even slightly as described above, the internal gear 8 is largely displaced with respect to the output shaft 1, but in the present invention, the internal gear 74 is located inside the large gear 22. Because of this position, even if the large gear 22 is slightly tilted, the internal gear 74 will not deviate greatly with respect to the output shaft 16.
In this respect as well, the concentricity and parallelism of each part of the planetary gear mechanism 23 are enhanced. Since the large gear 22 is located outside the planetary gear mechanism 23, the axial length of the entire device can be reduced. As bearings for large gears, the conventional product shown in Fig. 1 uses plain bearings 2 (sliding bearings), while the embodiment shown in Fig. 2 uses rolling bearings 65 and 66.
In this respect as well, the parallelism and concentricity of the internal gear 74 are enhanced.

When embodying the present invention, the cylindrical member 60 and the annular frame 61 can also be integrated. The present invention can also be applied to various types of speed reduction/reversing machines. For example, the input shaft 15 can be eliminated and the flywheel connected to the boss 3 via a plate or damper disk.
3 or the support shaft 18. Support shaft 18
When the input shaft is the input shaft, it is necessary or preferable in terms of design to arrange the pinion 21 closer to the flywheel than the multi-plate clutch 20. The output shaft 16 can also be arranged at the same height as the support shaft 18 or at a higher position. It is also possible to eliminate the multi-plate clutch 20 and connect the small gear 21 directly to the input member.

[Brief explanation of the drawing]

FIG. 1 is a vertical cross-sectional partial view of a conventional example, FIG. 2 is a vertical vertical cross-sectional view of an embodiment of the present invention, and FIG. 3 is an enlarged partial view of FIG. 2. 16... Output shaft, 17... Case, 21... Small gear, 22... Large gear, 60...
Cylindrical member, 61, 62... annular frame, 65,
66...Bearing, 67...Cylinder boss, 74...Internal gear, 75...Planetary gear, 78...Carrier, 82
...Sun gear.

Claims (1)

[Claims] 1. An input small gear and an output shaft whose center lines are parallel to each other are arranged in a case, and a large gear that meshes with the small gear is formed on the outer periphery of a large diameter cylindrical member arranged concentrically with the output shaft. Both side edges of the shaped member are supported by the outer periphery of an annular frame, the inner periphery of one annular frame is supported by an output shaft via a bearing, and the inner periphery of the other annular frame is It is supported via a bearing by a cylindrical boss fixed to the case, and an internal gear is formed on the inner circumference of the cylindrical member.A planetary gear that meshes with the internal gear is connected to both annular frames by a carrier that rotates together with the output shaft. A speed reducing/reversing machine characterized in that a sun gear which is freely rotatably supported between the cylinder bosses and meshes with the planetary gears is formed in a part of the cylinder boss which projects between the two annular frames.