JPS623568Y2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a structure for supporting an input shaft in a speed reduction/reversing machine.

Generally, in a marine speed reduction/reversing gear, the outer ring of the bearing that supports the input shaft rotates in the same direction as the inner ring, albeit at a relatively low speed, due to the frictional force inside the bearing. However, in conventional products, the outer ring of the bearing is directly supported by the case of the speed reducer/reverser, so the rotation of the outer ring causes the bearing part of the case to wear out, and as this wear progresses, even if it is localized wear of only the bearing part. However, it is necessary to replace the entire large case, which is time-consuming and costly. In addition, with conventional products, it takes time and effort to extract the input shaft, making it difficult to perform maintenance and inspection work. Furthermore, with conventional products, it is necessary to provide an oil relief groove in the case to lubricate the input shaft bearing.
Machining oil relief grooves in large cases is one of the causes of increased processing costs.

The present invention aims to solve the above-mentioned conventional problems by supporting the outer ring of the input shaft bearing with an annular spacer, and will be explained as follows with reference to the drawings.

In FIG. 1, which is a vertical cross-sectional view, an input shaft 3 of a speed reducer and reverser is connected to an engine flywheel 1 via a damper 2. As shown in FIG. The output shaft 4 is located behind the input shaft 3 (to the right in FIG. 1) and below, and extends parallel to the input shaft 3. An input gear 5 is provided at the rear end of the input shaft 3, and an output gear 6 is provided at the front end of the output shaft 4.

In FIG. 2, which is a partially cutaway view of FIG. , 6 are provided with a pair of forward rotation units F, F, and diagonally above the left and right reverse rotation units G, G are provided. In FIG. 1, the normal rotation unit F includes an intermediate gear 7, an output pinion 8, and a hydraulic multi-plate clutch 9 that can connect both 7 and 8, concentrically, the intermediate gear 7 meshes with the input gear 5, and the output pinion 8 It meshes with output gear 6. The pair of right and left normal rotation units F and F in FIG. 2 have the same structure and dimensions. Reversing units G and G also have almost the same structure and dimensions as unit F, except that intermediate gear 7' of unit G does not mesh with input gear 5, but meshes with intermediate gear 7 of unit F. are different.
Therefore, when the clutch 9 of the normal rotation unit F is connected, the rotational force of the input gear 5 is transmitted to the output gear 6 via the intermediate gear 7 of both units F, the clutch 9, and the output pinion 8, and the output shaft 4 is connected to the input shaft 3. Rotate in the same direction. Also, clutch 9' of reversing unit G
When connected, the rotational force of the input gear 5 is transmitted from the intermediate gear 7 of the forward rotation unit F to the output gear 6 via the intermediate gear 7', clutch 9', and output pinion 8 of the reverse rotation unit G, and the output shaft 4 is connected to the input shaft. Rotate in the opposite direction to 3.

The case of the speed reduction/reversing machine is formed into three parts: a lower case A, an intermediate case B, and an upper case C, which are fixed to each other by bolts 10 and 11. Divided surface (mating surface) a- of cases A, B, and C
a, bb are horizontal. The dividing plane a-a of the lower case A and the middle case B is below the output shaft center O, and only the lower part of the output shaft 4 is below the dividing plane a-a. The dividing plane bb of the intermediate case B and the upper case C passes through the centers f, f of both normal rotation units F, F. The lower case A forms an oil pan. The intermediate case B forms the main part of the bearing part when viewed as a whole of the speed reduction/reversing machine, and is used for the input shaft 3 and the support shaft 1 of the reversing unit G.
2 over the entire circumference, and the upper and middle parts of the output shaft 4 and the support shaft 1 of the normal rotation unit F.
It supports the lower half of 3. Horizontally protruding installation feet 15, 15 are integrally provided on both left and right walls of the intermediate case B, and the installation feet 15 are bolted to an engine stand of the hull (not shown). Further, as shown in FIG. 1, the front end of a generally annular mounting flange 2a that covers the damper 2 from the periphery is attached to the housing 1a of the flywheel 1 with a bolt 1b.
The rear end of the flange 2a is fixed by the bolt 2.
It is fixed to the lower case A and the middle case B by b and 2c. Note that the upper end surface c- of the upper case C
A lid D is bolted to c.

In FIG. 3, which is an enlarged partial view of FIG. 1, a mechanical seal 60 and a tapered roller bearing 61 are provided around the front part of the input shaft 3, and a damper 2 is attached to the front end surface of the input shaft 3 by a bolt 54c. tube boss 5
4b is fixed. The seal 60 includes a sleeve 65 fitted to the outer peripheral surface of the input shaft 3 and a
It includes an annular member 66 extending along the outer periphery of the front half (left half in FIG. 3) and an annular member 67 extending along the outer periphery of the rear half. 68 is a hole in the mounting flange 2a, and the member 66 is fixed to the front end of the peripheral edge of the hole 68 with a bolt 69. Part 6
A cylindrical portion 66a on the inner circumference of 6 is rotatably fitted into the sleeve 65. The member 67 includes a cylindrical portion 67a that fits into the inner peripheral surface of the hole 68, and a flange-shaped portion 67b that extends radially inward from the cylindrical portion 67a, with the inner periphery of the portion 67b being separated by a small gap. It fits into the sleeve 65. A protrusion 66b facing outward in the radial direction is provided at the rear end of the cylindrical portion 66a, and a protrusion 65a is provided on the sleeve 65 with a small gap therebetween, covering the outer peripheral surface of the protrusion 66b and the end surface on the bearing 61 side. .

A notch 70a is provided in a portion of the cylindrical portion 67a in front of the portion 67b. The notch 70a is located at the lowest position of the cylindrical portion 67a, and communicates with a notch 70b provided at the lower end of the inner circumference of the hole 68 of the mounting flange 2a. The notch 70b is open toward the inside of the case 71 and communicates with the inside of the case 71 via a notch 70c provided on the outer periphery of the lower end of the annular spacer 72.

The spacer 72 is a member that fits into a hole 73 in the front end wall of the case B. Its inner peripheral surface is fitted with the outer ring 61a of the bearing 61, and the outer diameter L (minimum diameter of the hole 73) is the outer diameter of the input gear 5. It is set slightly larger than . A locking pin 75 is attached to the upper end of the front end surface of the spacer 72, and a recess 75a into which the pin 75 fits is provided at the rear end of the inner circumference of the hole 68 of the mounting flange 2a. A positioning pin 76 fixed to the cylindrical portion 67a is also inserted into the recess 75a, and the pin 76 allows the member 67 to be inserted into the notch 70a.
is positioned so that it occupies the lower end position.

Note that the rear end of the input shaft 3 is supported by an annular boss 64 provided inside the case B via a tapered roller bearing 63. Further, the input gear 5 is integrally formed with the input shaft 3.

The lubricating effect will be explained. A portion of the lubricating oil droplets inside the case 71 pass between the outer ring 61a and the inner ring 61b of the bearing 61 and flow into the gap between the portion 67b and the bearing 61, thereby lubricating the bearing 61. The lubricating oil further flows from the gap 77 through the narrow gap between the part 67b and the member 65 into the gap 77 between the part 67b and the member 66, and from the gap 77 into the notches 70a,
It returns to the case interior 71 through 70b and 70c.

As explained above, according to the structure of the present invention, the bearing 61 of the input shaft 3 is supported on the inner periphery of the hole 73 of the case B via the annular spacer 72, and the spacer 72 is connected to the mounting flange 2 by, for example, the pin 75.
Since the bearing outer ring 61a is connected to the outer ring 61a and cannot rotate with respect to the case B, even if the bearing outer ring 61a rotates, only the spacer 72 is worn out and the case B is not worn out. Therefore, it is not necessary to replace the large case B, and it is sufficient to replace the small and simple spacer 72, which simplifies the repair work of the bearing portion and reduces the cost.

Further, since the outer diameter L of the spacer 72 is made larger than the outer diameter of the gear 5 fixed to the input shaft 3 in the case B, disassembly work can be easily performed.
In other words, when disassembling the mounting flange 2a
With the input shaft 3 removed from the case B, the fixed gear 5 and the input shaft 3 can be extracted out of the case B through the hole 73. Therefore, disassembly work can be simplified.

Furthermore, in the present invention, a mechanical seal 60 is disposed outside the bearing 61 to close the gap between the protrusion of the input shaft 3 that protrudes outside the case and the case B. The mechanical seal 60 includes the input shaft 3
The sleeve 65 is fixed to the protruding portion of the sleeve 65, and the closing portion (the annular member 6
6) and a partition wall portion (flange-shaped portion 67b) that is slidably fitted into the sleeve 65 between the closing portion 66 and the bearing 61. A lubricating oil recovery passage 70 extending from the gap 77 between the partition wall and the closing portion to the interior 71 of the case is formed at the lower end of the mechanical seal 60 and the spacer 72.

According to this structure, the partition wall portion 67b can prevent a large amount of lubricating oil that has passed through the inside of the bearing 61 from flowing to the blocking portion 66. In addition, the lubricating oil that has reached the gap 77 near the blocking portion 66 is transferred to the lubricating oil recovery passage 70.
can be returned to the interior 71 of the case. Therefore, leakage of lubricating oil to the outside can be reliably prevented.

Also, since the oil passage 70 can be formed in the spacer 72 or the mechanical seal 60 instead of in the case B, it is easier to form the oil passage than in the case where the oil passage is formed in a large case.
Processing costs can be reduced.

Furthermore, since the sleeve 65 was fixed to the input shaft 3,
The mechanical seal 60 does not wear out the input shaft 3, and the inside of the mechanical seal 60 (member 6
6 and the sleeve 65). Therefore, there is no need to replace the input shaft 3 due to wear, and in this respect as well, repair work can be simplified and costs can be reduced.

[Brief explanation of the drawing]

Fig. 1 is a vertical longitudinal sectional view of the embodiment, and Fig. 2 is a vertical cross-sectional view of the embodiment.
A partially cutaway view of the figure, and FIG. 3 is an enlarged partial view of FIG. 1. 3... Input shaft, 5... Input gear, 60... Mechanical seal, 61... Bearing, 65... Sleeve, 70... Lubricating oil recovery passage, 72... Spacer, 73... Hole, 77... Gap .

Claims (1)

[Scope of utility model registration request] A gear in which the input shaft is supported on the inner periphery of the hole in the case via a bearing and an annular spacer outside the bearing, the spacer is fixed non-rotatably to the case, and the outer diameter of the spacer is fixed to the input shaft inside the case. The input shaft has a protruding part that protrudes from the hole to the outside of the case, and a mechanical seal that closes the gap between the protruding part and the case is arranged outside the bearing. a sleeve fixed to the protruding portion of the input shaft, a blocking portion fitting to the outer periphery of the sleeve, and a partition portion slidably fitting to the sleeve between the blocking portion and the bearing; A lubricating oil recovery passage extending from the gap between the partition wall and the blocking part to the inside of the case,
A bearing structure for the input shaft of a speed reducer/reverser, characterized by a mechanical seal and a spacer formed at the lower end.