JP2505458Y2 - Marine reversing machine - Google Patents

Description

[Detailed Description of the Invention] [Industrial field of application] The present invention relates to a marine reversing machine used in a small boat such as a pleasure boat or a fishing boat.

[Conventional technology]

As disclosed in, for example, Japanese Utility Model Laid-Open No. 61-116234 and Japanese Patent Laid-Open No. 61-165050, as a marine reversing machine for this purpose, a cone for switching between forward and backward movement in a transmission path between an input shaft and an output shaft It is publicly known that a rotary clutch device and a friction multi-plate torque limiter for shutting off excessive torque are inserted and installed.

In particular, the torque limiter as described above cuts the peak torque when the front and rear clutches of the cone type clutch device are engaged, thereby preventing the occurrence of impact and damage to the cone.

[Problems to be solved by the invention]

The limit torque of the friction multi-plate torque limiter, that is, the maximum torque that can be transmitted is set in accordance with the maximum torque required for ship propulsion.When such a limit torque is set, this torque limiter certainly does Although such an impact is generated and the cone is prevented from being damaged, it is not possible to prevent the noise from being generated at the moment when the conical conical clutch surfaces of the cone clutch engage each other in a biting manner. There was a lot of noise.

The main object of this invention is not to set the limit torque of the friction multi-plate torque limiter only by the biasing force of the spring as in the conventional structure, but to set the limit torque for the hydraulic pressure after the cone clutch is fitted. Provided is a novel marine reversing machine, in which the above-mentioned problems are solved by reducing the spring load of a spring for limiting torque setting and thereby lowering the limiting torque value set accordingly. There is.

The accompanying object is to simplify the structure of the reversing machine for a ship by making the hydraulic pump provided for obtaining the above hydraulic pressure also serve as the hydraulic pump for supplying lubricating oil, which has been provided separately in the past. .

[Means for solving problems]

Therefore, as shown in the attached drawing, the present invention inserts and installs a cone type clutch device 5 for switching between forward and backward movements and a friction multi-plate type torque limiter 6 for shutting off excessive torque in the transmission path between the input shaft 2 and the output shaft 3. In the marine reversing machine,
The following technical measures were taken.

That is, a hydraulically actuated piston 10 for further pressing the friction elements 8 and 9 of the torque limiter 6 pressed by the spring 7 in the frictional engagement direction and driven by the input shaft 2 via the clutch device 5. The friction multi-plate torque limiter 6 is provided with a hydraulic pump 11, a hydraulic oil passage 12 for guiding the discharge oil of the hydraulic pump 11 to the hydraulic piston 10, and a pressure adjusting valve 13 for setting the hydraulic pressure of the hydraulic oil passage 12. The limit torque due to is set by both the biasing force of the spring 7 and the hydraulic pressure.

The present invention also proposes to provide a lubricating oil supply oil passage 14 branched from the hydraulic oil passage 12 and guide the lubricating oil supply oil passage 14 to a lubrication necessary portion of the clutch device 5. There is (claim 2).

[Function and effect of device]

In the neutral state where the cone type clutch device 5 is not engaged, the power transmission to the hydraulic pump 11 is cut off by the clutch device 5, and the hydraulic pump 11 is stopped. Therefore, the hydraulic pressure is not supplied to the hydraulically actuated piston 11, the friction elements 8 and 9 group of the friction multi-plate torque limiter 6 are pressed only by the spring 7 and frictionally engage, and the limiting torque of the torque limiter 6 is limited to the spring. It is set by the force of 7.

When the clutch device 5 is engaged and engaged from this state, power transmission to the clutch device driven side starts, the hydraulic pump 11 is driven, and the hydraulic pressure set by the pressure regulating valve 13 acts on the hydraulic operating piston 10. Then, the friction elements 8 and 9 group of the torque limiter 6 are pressed not only by the urging force of the spring 7 but also by the hydraulic pressure through the hydraulically actuated piston 11 to be frictionally engaged, thereby increasing the limiting torque by the hydraulic pressure. . The engagement of the clutch device 5 is almost completed while the limiting torque of the torque limiter 6 is set only by the biasing force of the spring 7.

Therefore, according to the present invention, the torque set by the spring 7 is set within the limit torque that does not generate noise at the moment when the conical clutch surfaces of the cone clutch device engage with each other in a biting manner. By selecting a small spring load for the spring 7 and supplementing the maximum torque required for propulsion of the ship with the hydraulic force set by the pressure regulating valve 13, it is possible to obtain the instantaneous noise at the end of clutch engagement that has been seen in the past. The problem of occurrence can be solved.

The lubricating oil is supplied to the lubrication necessary portion of the cone type clutch device 5 by the hydraulic pump 11 during the normal navigation of the vessel according to the structure of claim 2, and the cone type clutch device 5 is set to the neutral state to replace the other vessels. Even when the ship is towed by the ship, the hydraulic pump 11 is driven by the driven side of the clutch device 5 being driven by the propeller that rotates due to the movement of the ship, and the lubricating oil is supplied to the lubrication necessary portion of the clutch device 5. Is supplied. The same applies to the case where a ship equipped with a two-shaft two-shaft type propulsion device having an engine and a reversing machine on the left and right is used to navigate the ship with only one engine due to trouble or the like. The lubricating oil is supplied by the drive of the pump 11 from the propeller side, although the type clutch device is in the neutral state.

In the conventional reversing machine of a ship, a hydraulic pump for supplying lubricating oil, which is driven from the propeller side, was separately provided in case of the above case, but the structure using the hydraulic pump 11 is adopted as described above. By doing so, it is not necessary to provide a separate pump, and the structure of the marine reversing machine is simplified.

〔Example〕

The illustrated embodiment relates to an example in which the present invention is implemented as an angle drive type reversing machine. In FIG. 1, reference numeral 1 denotes a reversing machine casing which is installed at the stern portion of a ship with its output end facing rearward.

In the casing 1, the horizontally arranged input shaft 2 extending forward and the output shaft 3 extending rearward and downward are provided in front and rear, and these input shafts 2 are provided.
Also, a clutch shaft 4 equipped with the cone type clutch device 5 is provided above the output shaft 3 in a horizontal arrangement. The torque limiter 6 is installed in the casing 1 on the input shaft 2 connected to the engine flywheel 19 via the coupling 18 on the front side of the casing 1. This torque limiter 6 is a housing 20 that is loosely fitted and installed on the input shaft 2.
The housing 20 is integrally formed with a gear 21. A forward gear 22 and a reverse gear 23 are loosely fitted and installed on the clutch shaft 4 at intervals in the front and rear.
22 is directly meshed with the gear 21. A horizontal idler shaft 24 shown in FIG. 2 is also provided in the casing 1, and a hollow shaft 27 having a gear 25 meshing with the gear 21 and a gear 26 meshing with the reverse gear 23 is loosely fitted on the idler shaft 24. When installed, the reverse gear 23 is supposed to rotate in the opposite direction to the forward gear 22. The horizontal clutch shaft 4 and the output shaft 3 inclined rearward and downward are a reduction gear formed by meshing a small cylindrical gear 28 fixedly installed on the clutch shaft 4 and a large conical gear 29 fixedly installed on the output shaft 3. Connected by columns. Output shaft 3
A coupling half 30 is provided outside the casing 1 for connecting a propeller shaft (not shown).

Similarly, as shown in FIG. 1, the clutch device 5 uses a helical spline 32 formed on the clutch shaft 4 and includes a cone 33 spline-fitted to the clutch shaft 4.
Cone 33 has a pair of conical clutch surfaces 33a, 33b,
Corresponding conical clutch surfaces 22a and 23a are formed on the forward gear 22 and the reverse gear 23, respectively. The clutch device 5 is turned on and off by slidingly displacing the cone 33 on the clutch shaft 4 by the clutch lever 34 schematically shown in FIG. 4, and the cone 33 is moved from the neutral position shown in FIG. When the clutch gears 22a and 33a are displaced to the position where engagement is obtained, the forward gear 22 moves, and when the clutch faces 23a and 33b are engaged to position, the reverse gear 23 moves relative to the clutch shaft 4. They will be combined respectively.

As shown in FIGS. 1 and 3, the torque limiter 6 includes a plurality of friction elements 8 and 9 on the input shaft 2 and the housing 20, respectively.
Each of them is configured to be a friction multi-plate type which is slidably supported. Inside the housing 20, there is provided a pressure receiving plate 37 whose rearward displacement is prevented by a ball bearing 36 which supports the rear end side of the housing 20, and the hydraulically actuated piston 10 together with the pressure receiving plate 37 are provided with a friction element. It is provided at the front end of the housing 20 so as to sandwich the 8, 9 group. A short cylinder member 38 is screwed 39 to the input shaft 2, and the hydraulically actuated piston 10 is adapted to be in oil-tight contact with the inner peripheral surface of the cylinder member 38 and the outer peripheral surface of the input shaft 2. There is. The spring 7 is also provided as a pair of disc springs, and is received by the cylinder member 38 so that a hydraulically actuated piston is provided.
The friction elements 8 and 9 are pressed against the pressure receiving plate 37 via the piston 10. The cylinder member 38 is formed with an engagement hole 38a for a screwing operation tool, and by adjusting the forward and backward positions of the cylinder member 38 by screwing, the biasing force of the spring 7 can be adjusted. There is.

As shown in FIG. 1, the hydraulic pump 11 is configured as a gear pump, and is mounted on the front surface of the front cover 1a of the casing 1 at the same level as the clutch shaft 4. A square hole is formed at the front end of the clutch shaft 4, and a corresponding square portion 11b is formed at the end of the pump shaft 11a and fitted into the square hole. Therefore, only when the clutch device 5 is engaged, the input shaft is formed. The hydraulic pump 11 is driven by means of 2. A water-cooled oil cooler 41 is arranged in a lower portion of the casing 1, and an oil filter 42 for cleaning the oil cooled by the oil cooler 41 is connected to the inside of the casing 1 in the front lid 1a. It is inserted and installed in the formed oil passage 43. The oil passage 43 is communicated with an oil passage 45 in a plate 44 mounted on the front surface of the front lid 1a, and the latter oil passage 45 is guided toward the hydraulic pump 11.
As shown in FIG. 4, the oil passage 45 is connected to a pair of suction / discharge ports of the reversible hydraulic pump 11 via a pair of check valves 46 that allow only the oil flow in the direction of the port. There is.

As shown in FIG. 4, the pair of suction and discharge ports of the hydraulic pump 11 allow only the oil flow toward the hydraulic passage 12 regardless of the rotation direction of the hydraulic pump 11. They are connected via a pair of check valves 48. The pressure regulating valve 13 is provided in connection with the hydraulic oil passage 12. As shown in FIG. 1, the hydraulic oil passage 12 is formed in the plate 44 and the input shaft 2 so as to communicate with the inside of the cylinder member 38. As shown in FIGS. 1 and 3, the pressure regulating valve 13 is installed inside the input shaft 2, and the input shaft 2 on the rear end side of the hydraulic oil passage 12 is provided.
The relief valve is configured to set a predetermined hydraulic pressure while relieving the oil inside the hole 49. The valve spring 13a of the pressure regulating valve 13 is screwed into the rear end of the hole 49 and is received by the receiving member 50 attached to the rear end of the input shaft 2. An oil passage hole 51 is formed in the input shaft 2 for guiding the oil from the hole 49 to the friction elements 8 and 9 of the tricriminator 6, and the receiving metal 50 receives the oil from the hole 49.
A conical roller bearing 53 that supports the rear end side of the input shaft 2 and a conical roller bearing 54 that supports the front end side of the output shaft 3.
Is formed with an oil passage hole 52 leading to the. That is, the relief oil of the pressure regulating valve 13 is used to lubricate the friction elements 8 and 9 and the bearings 53 and 54.
Lubricating oil supplied to the 9th part is further added to the ball bearing 3
Guided to 6. The lubricating oil passes through the position of the outer peripheral surface of the cylinder member 38 and is also guided to the ball bearing 55 portion that supports the front end side of the housing 20. In Fig. 4, pressure regulator valve
The lubricated portion to which the relief oil of 13 is supplied is indicated by reference numeral L ₂ .

The portion to be lubricated including the necessary lubrication portion of the clutch device 5 is indicated by reference numeral L ₁ in FIG. 4, and the lubricating oil supply oil passage 14 causes the oil pressure in the hydraulic oil passage 13 to be lower than the set pressure of the pressure regulating valve 13. A diaphragm 56 is provided so that the aperture cannot be lowered. Explaining the concrete structure, the void 57 communicating with the hydraulic oil passage 12
As shown in FIG. 1, the oil seal 58 provides an oil-tight seal in the front lid 1a, and the lubricating oil supply oil passage 14 is formed in the clutch shaft 4 so as to communicate with the space 57. There is. The lubricating oil supply oil passage 14 is provided on the clutch shaft 4 and a conical roller bearing 60 portion that supports the cone 33 portion and the front and rear ends of the clutch shaft 4 by a plurality of radial oil passages 59 formed in the clutch shaft 4. Thrust collar 61 part, needle bearing 62
It is communicated with the parts that require lubrication of the clutch device 5. The oil passage 59 has a small diameter so as to give a throttle effect, and the lubricating oil supply oil passage 14 on the axis of the clutch shaft 4 is opened in the casing 1 with a small diameter portion 56a giving a throttle effect. An oil passage hole 65 connected to the space 57 shown in FIG. 1 is led to the front end position of the idler shaft 24 as shown in FIG. The hollow shaft 27 is supported by the idler shaft 24 through a pair of front and rear conical roller bearings 66, 67, and the oil passage hole 65 is formed by an oil passage 68 in the idler shaft 24 and a spacer sleeve between the bearings 66, 67. Lubricating oil is supplied to both the bearings 66, 67 through an oil passage hole 70 formed in 69.

Even when the clutch lever 34 shown in FIG. 4 is rapidly operated between the forward drive position F and the reverse drive position R, oil is temporarily drained from the cylinder member 38 (FIGS. 1 and 3) of the tricriminator 6. , So that the subsequent engagement of the clutch device 5 can be carried out without noise.
Is provided. The hydraulic unload valve 72 has a neutral position N, a forward drive position F, and a reverse drive position R corresponding to the respective positions of the clutch lever 34, and the hydraulic pressure in the hydraulic passage 12 is unloaded only at the neutral position N. The clutch lever 34 is operated in conjunction with the clutch device 5 for displacement operation. When the clutch lever 34 is operated between the forward drive position F and the reverse drive position R and passes through the neutral position N, the hydraulic unload valve
72 also passes the neutral position N, so that even if the lever 34 is operated quickly, the hydraulic unloading from the hydraulic oil passage 12, that is, the oil drain from the inside of the cylinder member 38 shown in FIGS. , Will certainly be done.

The illustrated tri-limiter 6 functions as described above as a function of the invention. The clutch device 5 is activated when the reversing machine is started.
The hydraulic pump 11 is not driven until the clutch is inserted, and the lubrication oil is not supplied to the lubrication necessary portion of the clutch device 5 by the hydraulic pump 11, but the time between them is short and the torque limiter housing 20 Lubricating oil to be supplied by the oil scraping action by the gear 21 on the outer peripheral surface can sufficiently cope.

In the illustrated embodiment, the torque limiter 6 is replaced by the clutch device 5.
The torque limiter is provided on the driven side of the clutch device 5 because the desired action can be obtained when the transmission torque is limited at any part of the transmission path during the normal operation as well as during the clutch engagement. It does not matter even if it is provided in. Further, although the hydraulically actuated piston 10 is structured to act on the friction elements 8 and 9 from the same side as the spring 7, for example, by disposing the spring 7 between the pressure receiving plate 37 and the ball bearing 36 shown in the drawing, the piston 10 It is of course possible to adopt a structure in which the spring 7 and the spring 7 press the friction elements 8 and 9 from opposite directions.

[Brief description of drawings]

FIG. 1 is a partially developed longitudinal side view of an embodiment of the present invention, FIG. 2 is a cross-sectional plan view of a portion of the embodiment, FIG. 3 is an enlarged view of a portion of FIG. 1, and FIG. 4 is provided in the embodiment. It is a circuit diagram of a hydraulic circuit. 2 ... Input shaft, 3 ... Output shaft, 4 ... Clutch shaft, 5 ...
… Clutch device, 6 …… Torque limiter, 7 …… Spring, 8,9 …… Friction element, 10 …… Hydraulic piston, 11 …… Hydraulic pump, 11a …… Pump shaft, 11b …… Square section, 12 …… Hydraulic oil passage, 13 ... Pressure regulating valve, 14 ... Lubricating oil supply passage, 20 ... Housing, 21 ... Gear, 22 ... Forward gear, 22a ... Clutch surface, 23 ... Reverse gear, 23a ... … Clutch surface, 33 …… Cone, 33a, 33b …… Clutch surface, 38
...... Cylinder member.

Claims (2)

(57) [Scope of utility model registration request] 1. A marine reversing machine in which a cone type clutch device 5 for switching between forward and reverse and a friction multi-plate type torque limiter 6 for shutting off excessive torque are inserted and installed in a transmission path between an input shaft 2 and an output shaft 3. A hydraulically actuated piston 10 for further pressing the friction elements 8 and 9 of the torque limiter 6 pressed by the spring 7 in the frictional engagement direction, and the hydraulic pressure driven by the input shaft 2 via the clutch device 5. The friction multi-plate torque limiter 6 is provided with a pump 11, a hydraulic oil passage 12 for guiding the discharge oil of the hydraulic pump 11 to the hydraulic piston 10, and a pressure regulating valve 13 for setting the hydraulic pressure of the hydraulic oil passage 12. A reverse engine for a ship, wherein the limiting torque is set by both the biasing force of the spring 7 and the hydraulic pressure. 2. The lubricating oil supply oil passage 14 branched from the hydraulic oil passage 12 is provided, and the lubricating oil supply oil passage 14 is guided to a necessary lubrication portion of the clutch device 5. Marine reversing machine.