JPS6333576B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a planetary gear type reduction/reversing machine mainly used for ships.

Fig. 1 shows the structure of a conventional planetary gear type reduction/reversing machine. The external gear 3a of the large reduction gear 3 is fitted onto the outside of the large reduction gear 3 so as to be rotatable, and the external teeth 3a of the large reduction gear 3 mesh with the small gear 4 for reduction.
I like to drive. On the other hand, reduction gear 3
A flange 5 is formed integrally with the output shaft 2 on the side of the flange 5, and the planetary gear 6 is supported on the side of the flange 5, and the planetary gear 6 is covered from the side of the large reduction gear 3. Projected cylindrical part 7
An internal toothed portion 8 is formed on the internal toothed portion 8, and a planetary gear 6 is formed on this internal toothed portion 8.
Similarly, the planetary gear 6 is meshed with a sun gear 9 protruding from the case 1. Therefore, the power transmitted to the reduction gear 3 is transferred to the cylindrical portion 7.
is transmitted to the output shaft 2 via the planetary gear 6 and flange 5, but in such a conventional structure, the large reduction gear 3, flange 5, and planetary gear 6 are arranged in parallel in the axial direction, and therefore, The axial dimension is long and the overall size is large. The purpose of the present invention is to eliminate such drawbacks and provide a speed reduction/reversing machine that has a short axial dimension and is therefore capable of large speed reduction using planetary gears without increasing the overall size. This is a reduction/reversing machine in which an input shaft 12 and an output shaft 13 are arranged in parallel, and a reduction gear 17 and a clutch 22 for engaging and disengaging power between the reduction gear 17 and the input shaft 12 are provided. , the output shaft 1 is connected to the output shaft 13.
A planetary gear support 24 is provided which protrudes outward in the radial direction of 3 and has an outer peripheral surface 24a in the same direction as the rotational direction of the output shaft 13, and also has an outer peripheral surface 25a in the same direction as the rotational direction of the output shaft 13, and an annular member 25 that rotates integrally with the planetary gear support 24.
are arranged to the side of the planetary gear support 24, and the reduction gear 29, which is arranged astride between the annular member 25 and the planetary gear support 24, is attached to the annular member 2.
The bearing member 31 fitted onto the outer circumferential surface 25a of No. 5
Similarly, the outer peripheral surface 24a of the planetary gear support 24
Freely supported by the bearing member 31 fitted to the
Internal toothed portion 2 provided on the inner circumference of this large reduction gear 29
9b is arranged between the bearing members 31, 31, while the planetary gear 27 supported by the planetary gear support 24 is housed and arranged between the planetary gear support 24 and the annular member 25. The planetary gear 27 and the internal toothed portion 29b of the large reduction gear 29 mesh with each other, and an external toothed portion 29 is provided on the outer periphery of the large reduction gear 29 located radially outward of the internal toothed portion 29.
a, and its external toothed portion 29a is meshed with the input reduction gear 17, and the sun gear 34 is meshed with the planetary gear 27.

Hereinafter, one embodiment of the present invention will be described based on the drawings.

In FIG. 2, reference numeral 11 denotes a reduction/reversing machine case, and an input shaft 12 is mounted on the upper part of this reducing/reversing machine case 11, and an output shaft 13 is mounted parallel to each other on the lower part. The input shaft 12 has its front end protruding from the case 11 and is connected to the flywheel 15 of the engine via the shaft coupling 14, while the output shaft 13 has its rear end protruding from the case 11,
A shaft joint 16 connected to the propeller shaft is fitted.

17 is a reduction pinion loosely fitted into the front half of the input shaft 12; 18 is also fitted into the rear half of the input shaft 12, with its opening side facing the pinion 17; and a hydraulic piston 19. The figure shows a cylindrical clutch housing with a bottom. A clutch hub 20 protrudes from the rear side surface of the small gear 17, and the clutch hub 20 protrudes into the clutch housing 18, and the hydraulic piston 19 is provided on the inner and outer peripheral surfaces of the clutch hub 20 and the clutch housing 18, respectively. A multi-plate clutch plate 21 is provided which is pressed into contact with the input shaft 12 and the small gear 17 to engage and disengage the power therebetween.
That is, the power transmitted to the input shaft 12 rotates the small gear 17 via the clutch housing 18 and the multi-plate clutch plate 21, which together form one input forward unit 22. ing. A reverse drive gear 23 is integrally formed on the outer periphery of the clutch housing 18 to drive a reverse unit (not shown) which is provided on the side of the input forward unit 22 and has substantially the same structure as the input forward unit 22. has been done.

Next, the structure of the output shaft 13 driven by the input forward unit 22 or the reverse unit (not shown) will be explained. First, a flange-type planetary gear support 24 is attached to the output shaft 13. It is integrally formed. Reference numeral 25 denotes an annular plate paired with the planetary gear support 24, and the annular plate 25 has stepped bolt-shaped support shafts protruding from the front side of the planetary gear support 24 at appropriate intervals in the circumferential direction. 26 at predetermined intervals, and these annular plates 25 and planetary gear supports 24
In between, planetary gears 27 are freely rotatably mounted by selecting a plurality of the support shafts 26. Further, the annular plate 25 and the planetary gear support 24 have outer peripheral surfaces 25a and 24a having the same diameter, and bearing bushes 31 and 31 having the same diameter are fitted onto the outer peripheral surfaces 25a and 24a, respectively. . Note that the bearing bushes 31, 31, the annular plate 25, and the outer periphery of the planetary gear support 24 are held together via the stepped portions 28, 28 so that the bearing bushes 31, 31 do not slip outward. 29 has an external toothed part 29a on its outer periphery and an internal toothed part 29b in the center of its inner peripheral part,
It is a ring-shaped reduction gear with slightly large sliding inner circumferential surfaces 30, 30 on both sides of this internal toothed portion 29b,
The sliding inner circumferential surfaces 30, 30 are slidably fitted onto the outer circumferential surfaces of the bearing bushes 31, 31, and the internal toothed portions 29b are fitted onto the planetary gear 27, and the external toothed portions 29a
is meshed with the small gear 17 mentioned above. Further, a small gear of a reverse unit (not shown) also meshes with this external gear portion 29a. Note that the reduction large gear 29 is
As shown in the figure, a bearing bush 31 fitted to the outer peripheral surface 25a of one annular plate 25 and a planetary gear support 24 on the other side are disposed astride between the annular plate 25 and the planetary gear support 24. The bearing bush 31 is fitted onto the outer circumferential surface 24a of 24, and is supported on both front and rear sides of an internal toothed portion 29b provided on the inner circumferential portion thereof. Therefore, even if a thrust force in the axial direction is applied to the large reduction gear 29, the internal teeth 29a abut against the bearing bushing 31 and will not come off in the axial direction. 32
is a cylindrical boss inserted into the planetary gear 27 through the gap between the inner periphery of the annular plate 25 and the output shaft 13, and the flange 32a formed at the front end of this cylindrical boss 32 is connected to the reduction/reversing gear case 11. It is fixed to the front wall with bolts 33, and a sun gear 34 formed on the outer periphery of the boss 32 meshes with the planetary gear 27.

In the above configuration, the power transmitted from the input shaft 12 to the small gear 17 via the multi-plate clutch plate 21 is transmitted to the large reduction gear 29 meshed with the small gear 17, and during this time, the power is first transmitted to the small gear 29 of the first stage. Deceleration takes place. The reduction gear 29 is connected to the bearing bush 31.
The planetary gear 27 is rotated while rotating on the top, but since the sun gear 34 is fixed, the planetary gear 27 rotates on the outer periphery of the sun gear 34 and is connected to the output shaft via the planetary gear support 24. 13 is rotated, and the second stage deceleration is performed at this planetary gear 27 portion.

FIG. 3 shows a case where the device of the present invention is used for normal reduction without the planetary gear 27, and in this case, the support shaft 26, the annular plate 25, the planetary gear 27, the sun gear 34, and the large reduction gear 29 is removed, and another large reduction gear 35 having no internal teeth is removed.
The concave portion 35a formed on the side surface is connected to the planetary gear support 24.
Mounting hole 3 into which the support shaft 26 was inserted
6 portions are tightened and held by bolts 37, thereby connecting the large reduction gear 35 to the output shaft 13.
The power is transmitted directly to the

The present invention has the above configuration, and thus, according to the present invention, the large reduction gear is supported on the outside of the planet gear by the planet gear support outer periphery that supports the planet gear. Since the support and reduction gear are located at the same axial position, the axial dimension is shortened by that much compared to the conventional structure in which they are arranged in parallel in the axial direction, and the overall structure can be made more compact. In addition, a large reduction gear can be directly attached to the planetary gear support, which has the effect of being able to be used in conjunction with a normal reduction gear that does not have such a planetary gear. Moreover, in this invention, the reduction large gear is disposed astride between the annular member and the planetary gear support.
The bearing member fitted to the outer circumferential surface of one annular member and the bearing member fitted to the outer circumferential surface of the other planetary gear support support the internal toothed portion provided on the inner circumference of the annular member on both front and rear sides. This not only prevents run-out due to the dual-end support structure, but also shortens the axial dimension of the reduction gear itself, making the entire device even more compact. It has the advantage of becoming Furthermore,
In this invention, even if an axial thrust force acts on the reduction gear, the internal tooth portion contacts the side surface of the bearing member, so that the reduction gear does not slip out in the axial direction. It has the advantage that it requires no special regulating member and can be manufactured at low cost.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional view of the main parts of a reduction/reversing machine showing a conventional structure, Fig. 2 is a longitudinal sectional view of the entire reducing/reversing machine showing an embodiment of the present invention, and Fig. 3 is a longitudinal sectional view of the main part of a reduction/reversing machine showing the conventional structure. FIG. 12...Input shaft, 13...Output shaft, 17...Reduction small gear, 21...Multi-plate clutch plate, 24...Planetary gear support, 24a...Outer peripheral surface, 27...Planetary gear, 29...Reduction Large gear, 29a...External gear, 2
9b...Internal tooth portion, 34...Sun gear, 25...Annular plate, 31...Bearing bush.

Claims (1)

[Claims] 1 In a reduction/reversal machine in which an input shaft and an output shaft are arranged in parallel, and a reduction gear and a clutch for engaging and disengaging power between the reduction gear and the input shaft are provided, a radius of the output shaft is placed on the output shaft. A planetary gear support is provided that protrudes outward and has an outer peripheral surface in the same direction as the rotational direction of the output shaft, and also has an outer peripheral surface in the same direction as the output shaft rotational direction, and rotates integrally with the planetary gear support. A bearing in which an annular member is disposed on the side of the planetary gear support, and a reduction gear, which is disposed astride between these annular members and the planetary gear support, is fitted onto the outer peripheral surface of the annular member. and a bearing member fitted to the outer circumferential surface of the planetary gear support, and the internal gear provided on the inner circumferential portion of the large reduction gear is disposed between the bearing members, A planetary gear supported by the planetary gear support is stored and arranged between the planetary gear support and the annular member, and the planetary gear and the internal gear of the reduction gear are meshed with each other, An external gear is provided on the outer periphery of the large reduction gear located radially outward from the internal gear, and the external gear meshes with the input reduction gear described above, and the sun gear meshes with the planetary gear. A planetary gear type reduction/reversing machine characterized by the following.