JPS626144B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a top cover of a speed reduction/reversing machine suitable for a marine propulsion device.

In general, marine speed reduction/reversing gears require lubricating oil to be supplied from the outside, and internal clutches, gears, bearings, etc. may need to be inspected. However, in conventional marine speed reduction and reversing gears, the structure of the window for performing the above-mentioned refueling and inspection work is complicated, causing an increase in costs.

In order to solve the above-mentioned conventional problems, the present invention has the following features:
An input gear, an output gear, and a plurality of transmission units capable of connecting the two gears are provided inside the case body, and an opening is provided in the upper wall of the case body to provide an emergency manual operation mechanism for the hydraulic clutch of each transmission unit. The operating section of the above is exposed below the opening, a top cover that closes the opening is removably attached to the upper wall of the case, and a window is provided in the top cover for oil bunkering and inspection as well as for operating the above operating section. The feature is that the window is covered with a removable window cover.

Next, embodiments will be described 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' of the reverse rotation unit G, the clutch 9', and the output pinion 8, 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 surfaces (mating surfaces) a- for 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 located below the output shaft center O, and only the lower part of the output shaft 4 is located 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 and f of both normal rotation units F and F, respectively. The lower case A forms an oil pan. The intermediate case B forms the main part of the bearing section 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 the left and right side 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. A lid D is bolted to the upper end surface cc of the upper case C.

As shown in FIG. 3, which is a partial cross-sectional view of FIG. Pinion 8 is bush 31
The support shaft 13 is rotatably supported at the rear of the support shaft 13 via the support shaft 13 . The hydraulic multi-plate clutch 9 has approximately the same structure as a conventional product, with the input part 9a being formed of a cylindrical part extending rearward from the outer periphery of the intermediate gear 7, and the output part 9b being a cylindrical part extending forward from the output pinion 8. It is formed of an elongated cylindrical part. The friction plates 9c on the input side and the output side are connected to the input section 9a and the output section 9b, respectively. 9d is an annular stopper fixed to the inner periphery of the tip of the input section 9a, and 9e is a friction plate 9c.
A piston 9f provided between the gear 7 and the gear 7 (cylinder end wall) is a return spring for the piston 9e provided inside the output portion 9b in the radial direction.

A boss cylinder 7a that protrudes to the front end of the support shaft 13 is provided on the inner circumference of the gear 7, and the front end of the support shaft 13 includes the boss cylinder 7a, a tapered roller bearing 32,
It is supported by bearing portions 35 of cases B and C via an annular spacer 33. The spacer 33 has an inner circumferential surface that is the outer circumferential surface of the outer ring 32a of the bearing 32 and the front end surface (the third
Case B is supported by a rotation pin 33a (screw) parallel to the support shaft 13.
(or C) is provided with a rotation stopper. The pin 33a is fixed to the outer periphery of the spacer 33 from the side opposite to the gear 7, and its front end protruding from the spacer 33 fits into the recess of the case B. The bearing parts 35 of the cases B and C are joined together on the plane b-b to form a cylindrical body as a whole, and the spacer 33
It supports the outer peripheral surface and front end surface of.

The rear part of the support shaft 13 is a small-diameter annular spacer 3.
6. Tapered roller bearing 37, large diameter annular spacer 38
are supported on the inner peripheral surfaces of the holes 39 of the cases B and C via the holes 39 of the cases B and C. The spacer 36 is in contact with the rear end surface of the pinion 8 via a bush 36a, and the bearing 37
The inner peripheral surface and front end surface of the inner ring 37b are supported by a spacer 36. The outer ring 37a of the bearing 37 is supported by a spacer 38 on its outer peripheral surface and rear end surface. The spacer 38 is held in the hole 39 while being prevented from rotating by a pin 38a fixed to the rear part of the outer peripheral surface.
It fits on the inner circumferential surface of. The pin 38a fits into a recess 39a provided on the inner peripheral surface of the hole 39, and
a opens rearward (to the right in FIG. 3) and is covered by a lid 40. The hole 39 is formed by a semicircular recess at the upper end of the case B and a semicircular recess at the lower end of the case C, and the inner diameter of the hole 39 is set larger than the outer diameter of the pinion 8.

The small-diameter rear end portion of the support shaft 13 projects further rearward than the cases B and C and into the hole 41 of the rear lid 40. The lid 40 is attached to the case B by bolts 42.
A member fixed to the rear surface of C, which has internal oil passages m and n that connect to external hydraulic oil passage M and lubricating oil passage N, and hydraulic oil passage m and lubricating oil passage n are respectively inside the support shaft 13. The pressure chamber 9g on the back side of the piston 9e and the bush 31 are
It is connected to sliding parts such as the friction plate 9c and the like.

An oil pump 43 is fixed to the rear end surface of the lid 40 with a plurality of bolts 44. An input shaft 45 of the pump 43 projects into the hole 41, and a cylindrical joint 46 is screwed to the outer peripheral surface of the projecting end of the shaft 45. A portion of the joint 46 projecting from the shaft 45 (the left half in FIG. 3) fits into a diametrical slit (or concentric hole, etc.) at the rear end of the support shaft 13 and is fixed by a pin 47. Although not shown, the pump 43 is provided in both normal rotation units F in FIG. 2, and the two pumps 43 supply clutch hydraulic pressure and lubricating oil.

In FIG. 4, which is a partial cross-sectional view of FIG. 2, the reverse rotation unit G is the normal rotation unit F (FIG. 3)
The only difference is the following: In FIG. 4, parts corresponding to those in FIG. 3 are given the same reference numerals. In FIG. 4, the bearing portion 35 and the hole 39 are formed by the case B alone. Also, no oil pump is attached to the rear lid 40,
The hole 41 is closed by a cover 48 fixed to the rear end surface of the lid 40. The above is the difference, but the seat surface and bolt holes for mounting the cover 48 provided on the lid 40 in FIG. 4 are the same as those for the pump 4 provided on the lid 40 in FIG. 3.
3. Matches the mounting surface and bolt holes. Therefore, instead of the cover 48, the pump 43 in FIG.
The input shaft 4 of the pump 43 is fixed to the lid 40 shown in the figure.
5 can be connected to the diametrical slit 12a at the rear end of the support shaft 12 within the hole 41 shown in FIG. 4, and the hole 41 shown in FIG. 3 can be closed by a cover 48.

Next, the lubricating oil and clutch hydraulic oil supply device will be explained. In FIG. 5, which is a layout diagram of oil passages, the pair of oil pumps 43, 43' are connected to oil passages 101, 101' in the upper case C via oil passages 100, 100' in the lid 40, respectively. ,
Both oil passages 101 and 101' meet at the confluence point 9 in case C.
It is connected to one oil passage 102 at 0. The oil passage 102 is connected to an oil passage 104 in the upper lid D via an opening 103 on the mating surface cc, and the oil passage 104 is connected to an inlet q of a hydraulic oil pressure regulating valve Q (primary pressure regulating valve). .

The pressure regulating valve Q itself has a conventionally known structure, as shown in its cross section in FIG. are doing. The outlet j1 of the switching valve J is connected to the four external passages M, internal oil passages m,
m' to the clutches 9, 9' of the forward unit F and the reverse unit G, respectively.

The oil drain port q2 of the pressure regulating valve Q is the oil passage 10 inside the upper lid D.
5 and an oil passage 106 inside the case C to an inlet of an oil cooler K, and an outlet of the oil cooler K is connected to an oil passage 108 inside the upper lid D via an oil passage 107 inside the case C. The middle part of the oil passage 108 is connected to the lubricating oil pressure regulating valve L through the oil passage 1 inside the case D.
The oil drain port l1 of the pressure regulating valve L is connected to an oil reservoir 93, which will be described later, via an oil hole 92 inside the upper lid D.

The outlet of the oil passage 108 is connected to an oil passage 109 in the case C, and the outlet of the oil passage 109 is connected to a pair of strainers 95 via a two-pronged oil passage 112 that extends into the case C through the inside of the pot 94. The outlets of both strainers 95 are connected to one oil passage 114 inside the case C via a two-pronged oil passage 113 that passes through the inside of the case C and joins inside the pot 94. The oil passage 114 (main gear rally) is continuous in the case C with an oil passage 115 provided with a pair of outlet openings 116 and 116', and both openings 116 and 116' are connected to a pair of oil passages in the upper cover D, respectively. 117, 117'.
Both oil passages 117, 117' are open at the upper surface d of the upper lid D, and the joint 9 attached to the outlet opening
6 and 96', it is connected to the lubricating oil external passage N.

Each of the above-mentioned oil passages is formed by a bored hole.
Further, unnecessary end openings of each of the oil passages shown in FIGS. 6 and 7 are closed with blind plugs. Next, the oil passage structure etc. will be explained in detail.

In FIG. 6, which is a partial view (plan view of case C) in FIG. 2, a pair of oil pumps 4
3, 43' oil passage 101 in case C,
Inlet part 120 of one oil passage 101' among 101'
and the other oil passage 101 are provided at positions separated to the left and right with the center plane HH in between. The inlet part 120 has two holes 121 and 122 that open on the upper surface of the case c--c.
It is equipped with Both holes 121 and 122 are close to each other and communicate with each other via an oil groove 125 provided on the lower surface of the lid 124. The lid 124 is a small plate-like component that has four screw holes 12 near the oil holes 121 and 122.
A bolt (not shown) screwed into the upper surface c-
It is fastened to c. Downstream section 12 of oil passage 101'
3 extends from the bottom of the oil hole 122 at the front (on the side away from the oil pump 43') inside the case C at right angles to the center plane H-H, joins the oil passage 101 at the confluence point 90, and connects to the oil passage 102. are doing. The oil passage 102 extends forward from the merging point 90, and the upward opening 103 on the outlet side is connected to the vertical oil passage 104 shown in FIG. 7 at the middle part of the case C in the longitudinal direction.

FIG. 7 is a partial view (a plan view of the upper cover D) of FIG. 2 in the direction of the - arrow, and as shown in FIG. The upper surface d of the upper lid D is provided with four bolt holes 128 for fixing the pressure regulating valve Q and a seat surface. The oil passage 105 connected to the oil drain port q2 of the pressure regulating valve Q extends to the right in a manner that intersects the center plane H-H, and the downward outlet opening 105' at the right end is the sixth
It is connected to the internal oil passage 106 of case C in the figure.

The oil passage 106 extends rearward, and a rightward bent portion at the rear end opens on the upper right end surface 130 of the case C, and is connected to an inlet of an oil cooler K (FIG. 2) attached to the end surface. The outlet of the cooler K passes through the oil passage 107 in Fig. 6 and then the downward opening 1 of the oil passage 108 in Fig. 7.
It is connected to 31.

The oil passage 108 extends between the downward openings 131 and 132 at both left and right ends of the upper cover D at right angles to the center plane H-H, and an oil passage l for the lubricating oil pressure regulating valve L is provided in a portion near the left end of the oil passage 108. are connected horizontally from the rear. The lubricating oil pressure regulating valve L itself has a known structure, as shown in the cross section of FIG. 10, which will be described later, and is fixed by fitting into a hole l' provided at the left end of the rear end surface of the upper cover D, as shown in FIG. There is.

The outlet opening 132 of the oil passage 108 is connected to the internal oil passage 109 of case C in FIG.
After connecting to the oil strainer 95 through 2, the oil path 113
It is connected to the oil passage 114 through the. oil strainer 95
are a pair of vertical holes 9 in the front and rear provided at the left end of the case C.
A filter element is attached to the filter element 5' as shown in FIG. Also, as shown in Figure 2, Kotoku 9
4 is attached to the left end surface of case C. As shown in FIG. 6, the oil passage 114 extends from the inlet opening on the left end surface of the case C to the right through between the two oil strainers 95, and connects to the oil passage 115 near the oil strainer 95. There is. The oil passage 115 extends to the right half of the case C in a manner perpendicular to the center plane HH. Upward openings 116 and 11 provided at both ends of the oil passage 115
6' are located symmetrically with respect to the center plane H--H, and the oil passages 117, 117' of the upper cover D in FIG. ing. Both oil passages 117, 117' are formed by vertical holes.
The joints 96, 96' in Fig. 8 that connect to the center plane H
- It is installed symmetrically with respect to H.

As shown in FIG. 8, which is a view in the direction of the - arrow in FIG.
6', and fittings N1 to each pipe N1.
A pair of pipes NF and NG are connected to each other via 2, and the outlet of each pipe NF and NG is connected to the internal passage n of the lid 40 (FIGS. 3 and 4). Left and right 1
Each pair of pipes N1, NF, NG and joint N2 also have a center plane H
- They are arranged symmetrically with respect to H, and the two pipes NF and NG connected to each joint N2 also have approximately the same length. Therefore, the left and right normal rotation and reverse rotation units F,
The length of the oil path to the lubrication part of G is approximately the same.

As shown in FIG. 9, which is a view from the - arrow in FIG. 8, the forward/reverse switching valve J is attached to the rear of the upper cover D.
As shown in FIG. 8, it is located at the center in the left-right direction of the speed reduction/reversing machine. A pair of joints M1 are attached to the left and right side surfaces of the lower part of the switching valve J, and the aforementioned external hydraulic oil passage M (piping) extends from each joint M1 to the hydraulic oil inlet of each lid 40. The lengths of the pair of passages M, M connected to the forward rotation units F, F are approximately the same, and the lengths of the pair of passages M, M connected to the reverse rotation units G, G are also approximately the same. be.

As shown in FIG. 10, which is an enlarged partial view of FIG. 1, the oil reservoir 93 attached to the lubricating oil pressure regulating valve L is formed by a depression provided on the upper surface of the upper wall C2 of the case C. A vertical hole 92 in the upper lid D, which serves as an oil drain hole, opens above the oil reservoir 93. The front wall of the oil sump 93 (the left wall in FIG. 10) forms a weir 140 that is shorter than the other wall parts, and the weir 140
A guide portion 141 extending above the gears 7, 7' is formed below by the oil passage circumferential wall of the case C. Further, as shown by the broken line hatching in FIG. 6, the oil reservoir 93 extends in the left-right direction in the center of the upper wall of the case C.

An opening 141' is provided on the front side of the weir 140,
A baffle plate 143 forming a maze 142 for a breather is provided in the opening 141' as shown in FIG.
The baffle plate 143 is an assembly of a plurality of plates, and the bolt 14
4 is attached to the lower surface of the upper lid D. Maze 1
The upper end outlet of 42 communicates with the internal cavity 145 of the upper lid D, and the cavity 145 is connected to the horizontal hole 1 provided at the front end of the upper lid D.
It communicates with the outside via 46.

As shown in FIG. 7, a pair of windows 147 are provided at the front part of the upper lid D at intervals on the left and right sides. The window 147 is attached to the lid 14 fixed with bolts 148 as shown in FIG.
9 is normally closed, and the bolt 148 and lid 14
By removing 9, oil can be supplied to the inside of the speed reduction/reversing gear through the window 147, and the inside can be inspected. In addition, in the event of a failure of the oil pump, a tool can be inserted through the window 147 and the clutch can be connected manually as described below.

In FIG. 3, the gear 7 facing the pressurizing chamber 9g
A screw hole into which a bolt 150 is screwed is provided in the portion. A plurality of bolts 150 are provided at intervals in the circumferential direction of the gear 7, and each bolt 150 extends parallel to the support shaft 13. The bolt 150 has a head 151 with a rectangular cross section, and the head 151 protrudes toward the bearing 32 side. Therefore, the window 147 (the tenth
When the head 151 is turned with the tool inserted from the figure), the bolt 150 moves the piston 9e to the friction plate 9.
Even if hydraulic pressure cannot be supplied to the pressurizing chamber 9g, navigation is possible by connecting the clutch 9 with the bolt 150 when the engine is stopped and then starting the engine. . As shown in FIG. 4, a similar bolt 150 is provided on the clutch 9' of the reversing unit G, and a window 147' for operating the bolt is provided on the side surface of the case B. 149 and 148 are windows 14
This is the lid and bolt that closes 7'.

In FIG. 5, the oil discharged from both oil pumps 43, 43' is supplied to the hydraulic pressure regulating valve Q through the aforementioned oil passage, and the hydraulic pressure supplied from the pressure regulating valve Q passes through the switching valve J to the clutch 9, 9'. Also, almost all of the oil that has flowed into the pressure regulating valve Q is discharged from the oil drain port 82, and is supplied to each lubricating section via the cooler K and filter 95. In this way, normally two oil pumps 43, 43' operate, but even if one of the oil pumps 43 or 43' breaks down, the following structure related to the oil passage 101' in FIG. The ship is now able to continue sailing.

That is, in the ship, apart from the illustrated lid 124,
A blind cover or a blind stopper without an oil groove 125 is provided, and by replacing the blind cover with the illustrated cover 124, the oil passage 101' can be interrupted midway. Therefore, if the oil pump 43' breaks down, the oil passage 10
By blocking 1', oil can be prevented from flowing backward from the oil passage 101 to the oil pump 43', and high-pressure oil can be reliably supplied to the pressure regulating valve Q using only one oil pump 43. In addition, if the oil pump 43 breaks down, both oil pumps 43 and 43' are replaced and the oil passage 10
By blocking 1', high pressure oil can be reliably supplied to the pressure regulating valve Q. The structure for replacing the oil pumps 43, 43' is as follows:
3' can be replaced with the lid 40 by itself, or
Alternatively, any structure in which the pumps 43, 43' together with the lid 40 can be replaced with respect to the cases B and C can be adopted. The mounting bolt holes 126 and seat surface of the lid 124 shown in FIG. 6 can also be used for mounting the blind lid.

Also, during the above operation, the oil discharged from the lubricating oil pressure regulating valve L shown in FIG.
The oil that accumulated in the boss 1 and overflowed from the weir 140
41 and flows down onto gears 7 and 7'.

As explained above, according to the present invention, the upper end opening 141' of the case C main body of the speed reduction/reversing gear is covered by the upper cover D, and the window 147 for oil bunkering and inspection is covered by the upper cover D.
Since the lid 147 is closed by the removable window lid 149, the window 147 and the window lid 149 can be integrated into the upper lid D to simplify the structure. Furthermore, in the present invention, the operation part (head 151) of the emergency manual operation mechanism (bolt 150) of the hydraulic clutch 9 of the transmission units F, G is exposed below the upper end opening 141', and the window 147 of the upper cover D is exposed. In addition to being used for bunkering and inspection, it can also be used to operate the above-mentioned operating section.

In this way, in the present invention, the window 147 is configured so that it can be used for three types of work: refueling and inspection, and manual clutch operation, and the window 147 and window cover 149 are integrated into the upper cover D to simplify the structure. ing. Therefore, according to the present invention, it is possible to reduce the manufacturing cost of the window opening structure for performing the three types of work, lubrication and inspection, and manual clutch operation, and to perform these works easily.

[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.
Partial cutaway of the figure - arrow view, Figures 3 and 4 are partial cross-sectional views of Figure 2, respectively,
Figure 5 is a schematic diagram of the oil path, Figures 6 and 7 are the
- and - partial view of the figure, Fig. 8 is the 1st
9 is a view taken along the arrow in FIG. 8, and FIG. 10 is an enlarged partial view of FIG. 1. 5... Input gear, 6... Output gear, 9... Hydraulic clutch, 141'... Opening, 147... Window, 149...
Window cover, 150 bolts (emergency manual operation mechanism),
151...Head (operation part), C...Case (case body), C2...Upper wall, D...Upper lid, F, G...Transmission unit.

Claims (1)

[Claims] 1. An input gear, an output gear, and a plurality of transmission units capable of connecting the two gears are provided inside the case body, and an opening is provided in the upper wall of the case body to allow emergency manual operation of the hydraulic clutch of each transmission unit. The operation part of the mechanism is exposed below the opening,
A top cover that closes the opening is removably attached to the top wall of the case, a window is provided in the top cover for refueling and inspection, and for operating the operation section, and the window is covered by a removable window cover. The upper cover of the speed reduction/reversing machine.