JPS6250697B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a reversing speed reducer suitable for vessels such as fishing boats.

For some fishing boats, attempts have been made to lower the propeller rotation speed and adopt larger diameter propellers with higher propulsion efficiency, and a device using a planetary gear mechanism as a reversing speed reducer has already been developed for this purpose. has been done. However, when increasing the reduction ratio of a planetary gear mechanism, the dimensions increase significantly.
For fishing boats with limited installation space, it is only possible to adopt a reversing speed reduction mechanism with a relatively small reduction ratio.
Therefore, the propeller rotation speed cannot be lowered to a desired value, and it is difficult to use a large diameter propeller with high propulsion efficiency. In addition, the mechanical efficiency (power transmission efficiency) of the planetary gear mechanism increases as the reduction ratio increases.
Therefore, it is impossible to set a sufficiently large reduction ratio in this respect as well.

In order to solve the above-mentioned conventional problems, the present invention has the following features:
A speed reduction mechanism including a parent bevel gear and a child bevel gear is provided in a speed reduction/reversing machine, and will be explained with reference to the drawings as follows.

In the drawing, which is a vertical cross-sectional view, a substantially horizontal cylindrical input shaft 1 is arranged at the upper part of a clutch case 2, and an output shaft 3 parallel to the input shaft 1 is arranged at the lower part of the clutch case 2. A multi-plate clutch 4 and a small-diameter helical gear 5 are provided around a support shaft 20 that extends concentrically with the input shaft 1, and a large-diameter helical gear 6 and a speed reduction mechanism 10 are provided around the output shaft 3. is provided.
The speed reduction mechanism 10 includes a pair of parent bevel gears 7 and 8 and a child bevel gear 9.

The clutch case 2 has holes 13 and 14 in the upper part of both end walls 11 and 12, and the end of the input shaft 1 protruding from the hole 13 to the outside of the case 2 is connected to the flywheel 16 of the engine via an annular input plate 15. are doing. The input shaft is supported on the inner periphery of the hole 13 via a bearing 18, and the portion of the input shaft 1 protruding into the case 2 forms an outer peripheral drum 30 of a multi-plate clutch 4, which will be described later. One end of a support shaft 20 is fixed to the inner periphery of the input shaft 1 by hydraulic fitting or the like. The support shaft 20 extends through the center of the multi-plate clutch 4 and the small gear 5 to the other case end wall 12, and a portion near the other end of the support shaft 20 extends through the center of the multi-plate clutch 4 and pinion 5 to the case end wall 12 via a ring 17 and a bearing 21. is supported on the inner periphery of the hole 14.
The hole 14 is covered by a cover 22 fixed to the outer surface of the end wall 12. The cover 22 is provided with a plurality of oil passages 23 and 24 therein, and the inlets of the oil passages 23 and 24 are connected to an oil pump 25 fixed to the upper end of the case 2 via a pipe (not shown). Oil road 2
3 and 24 are oil passages 27 and 28 in the support shaft 20, respectively.
is connected to. The oil passage 7 extends to the inside of the multi-plate clutch 4 and small gear 5, and is also connected to a gap on the side of the bearing 21.

The multi-plate clutch 4 is conventionally known and includes a plurality of friction plates 31 and plates 32 arranged alternately, and a protrusion on the outer periphery of each friction plate 31 is slidable in an axial groove provided in a drum 30. Fit and plate 3
The inner circumferential projection 2 is slidably fitted into an axial groove provided in the inner circumferential drum 33. Annular pressure plate 3
5 is fixed to the open end of the outer drum 30 with bolts, and the piston 36 is adjacent to the input shaft 1 and is slidably fitted between the drum 30 and the support shaft 20. The oil passage 28 is connected to a hydraulic chamber 37 formed between the piston 36 and the input shaft 1. A hydraulic control mechanism (not shown) is provided in the middle of the oil path from the pump 25 to the hydraulic chamber 37. A compression coil spring 38 is located inside the inner peripheral drum 33, and the spring 38 is compressed between a ring on the support shaft 20 and the piston 36.

The boss 40 of the inner drum 33 extends to the vicinity of the bearing 21, and the teeth of the small gear 5 are formed around the extended portion of the boss 40. The boss 40, ie, the small gear 5, is rotatably fitted to the support shaft 20 via a bush.

The boss of the large gear 6 that meshes with the small gear 5 is a bearing 41
The inner periphery of the end near the end wall 12 is rotatably supported by the output shaft 3 via the outer periphery of the main bevel gear 7, and an annular notch step 45 provided on the outer periphery of the main bevel gear 7 is firmly fitted into the other portion. Fixed.

The inner circumference of the gear 7 is connected to the output shaft 3 via a bush 42.
It is rotatably and concentrically supported. For example, three small diameter bevel gears 9 are meshed with the main bevel gear 7. The bevel gears 9 are located below the multi-plate clutch 4 and are arranged around the output shaft 3 at equal intervals. Each bevel gear 9 is rotatably supported by a shaft 47 extending in the radial direction of the output shaft 3 via a bush 48 . The shaft 47 projects integrally from the outer peripheral surface of the output shaft 3. A circular plate 50 is fixed to the distal end surface of the shaft 47 by bolts 51, and the bush 48 is fixed in the direction of the center line of the shaft 47 by a stepped portion 52 provided at the base end of the shaft 47 and the plate 50. Each bevel gear 9 is meshed with another large-diameter parent bevel gear 8 from the side opposite to the parent bevel gear 7. The number of teeth of the bevel gear 8 is the same as the number of teeth of the bevel gear 7, and a cylindrical portion 53 is integrally extended from the outer periphery of the rim of the bevel gear 8 in the opposite direction to the bevel gear 7. The tip end is fixed to a cylindrical portion 62 provided on the inner surface of the case end wall 11 with a bolt (not shown).

The output shaft 3 is rotatably supported on the inner periphery of the hole 56 in the end wall 12 via a bearing 60 . A cylindrical cover 57 is fixed to the peripheral edge of the hole 56 from the outside with bolts 58, and the inner circumference of the cover 57 and the output shaft 3
An oil seal 61 is provided between them. The outer periphery of the output shaft 3 at the left end in the figure is rotatably supported by a cylindrical portion 62 of the end wall 11 via a bearing 63. The opposite end of the output shaft 3 protrudes outside the case 2, and a joint flange 6 is provided on the tapered outer peripheral surface of the protruding end.
5 are fitted and fixed by a plate 66 and bolts 67. The flange 65 is connected by bolts 68 to a joint flange 69 on the propeller shaft (not shown).

The effect will be explained. When the hydraulic chamber 37 of the multi-disc clutch 4 is pressurized, the piston 36 moves against the pressure plate 35.
The friction plate 31 and the plate 32 are brought into pressure contact with each other, and the rotational force can be transmitted from the outer drum 30 to the inner drum 33 via the friction plate 31 and the plate 32. When the clutch 4 is connected in this way, the flywheel 16 is connected to the input plate 1.
The rotational force transmitted to the input shaft 1 via the outer drum 30 is transmitted to the clutch 4, and from the clutch 4 to the small gear 5, the large gear 6, and the main bevel gear 7. Also, during this time, the gears 5 and 6 perform the first stage of deceleration, and the rotation direction is also changed to the opposite direction. Main bevel gear 7
When rotates, the child bevel gear 9 freely rotates around the shaft 47 and rotates the output shaft 3 via the bush 48 and the shaft 47, and the rotational force is transmitted from the parent bevel gear 7 to the output shaft via the child bevel gear 9. It is transmitted to 3. Also, the reduction ratio between
That is, the reduction ratio e of the reduction mechanism 10 is expressed by the following equation.

e=1+Z ₇ /Z ₉ Z ₇ : Number of teeth of parent bevel gear 7 Z ₉ : Number of teeth of child bevel gear 9 Therefore, the reduction ratio i of the entire device is expressed by the following formula.

i = Z ₆ / Z ₅ × (1 + Z ₇ / Z ₉ ) Z ₅ : Number of teeth of small gear 5 Z ₆ : Number of teeth of large gear 6 As is clear from the above formula, in order to increase the reduction ratio i, The number of teeth _Z7 of the bevel gear 7 may be increased. In the present invention, the number of teeth _Z7 can be made sufficiently large. That is, since the gears 7, 8, and 9 of the reduction mechanism 10 are arranged side by side along the longitudinal direction of the output shaft 3, the outer diameter of the gear 7 is the same as that of the reduction mechanism 10.
It substantially matches the overall outer diameter, and only small members (bolts 51, etc.) protrude beyond the gear 7 on the outer peripheral side. Therefore, even if the gear 7 has a large diameter and its outer periphery is relatively close to the multi-plate clutch 4, the bolt 5
The first class does not interfere with the multi-plate clutch 4. Since the outer diameter of gear 7 can be increased in this way, it is possible to increase the number of teeth Z ₇ of gear 7,
A large reduction ratio e (2 to 8) can be obtained.
In other words, even if only a narrow space remains between the input shaft 1 (multi-plate clutch 4) and the output shaft 3, large reduction ratios e and i can be obtained by employing the reduction mechanism 10 according to the present invention. Can be done.
Compared to conventional products, the device of the present invention can be configured to be lighter and more compact when the reduction ratio is the same. The present invention can be easily implemented by simply replacing the planetary gear mechanism and output shaft of the conventional device with the mechanism 10 and output shaft 3 according to the present invention.

In addition to the above advantages, the bevel gears 7, 8, and 9 have a high mechanical efficiency (power transmission efficiency), and have the advantage that the mechanical efficiency does not decrease even if the reduction ratio e is set to a large value. , i can be set large.

Further, since the input shaft 1 of the device to which the present invention is applied is cylindrical, its radius is large, and therefore a larger torque can be transmitted than when the input shaft is a solid small diameter shaft.

In addition, when embodying this invention, the output shaft 3 can also be arrange|positioned at the same height as the input shaft 1, or above it.

[Brief explanation of the drawing]

The drawing is a vertical longitudinal sectional view of an embodiment of the present invention. 1
... Input shaft, 2 ... Clutch case, 3 ... Output shaft, 4 ... Multi-plate clutch, 5 ... Small gear, 6 ...
Large gear, 7, 8...Main bevel gear, 9...Small bevel gear,
10... Reduction mechanism, 20... Support shaft, 47... Axis.

Claims (1)

[Claims] 1 Arrange the input shaft and output shaft in parallel in the clutch case, form the input shaft with a cylindrical shaft, fit one end of the support shaft into the input shaft, support the other end of the support shaft with the clutch case, A multi-plate clutch is provided on the support shaft, and a small gear that is connected to and disconnected from the input shaft by the clutch, a large gear supported on the output shaft is meshed with the small gear, and the large gear and the output shaft are connected to form a reduction gear mechanism. In the reduction/reversing gear connected through the
The output shaft is rotatably supported by a shaft protruding in the radial direction from the outer peripheral surface of the output shaft, and another parent bevel gear that meshes with the small bevel gear from the opposite side of the parent bevel gear is clutched at a position concentric with the output shaft. A reduction/reversing machine characterized by being fixed to a case.