JPH0335860Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a control device for a marine self-reversing engine drive shaft generator.

Conventionally, as a marine self-reversing engine drive shaft generator, an arrangement as schematically shown in FIG. 1 of the accompanying drawings is known. That is, a gear and a clutch 3 are connected to a main shaft ₂₁ driven by a forward/reverse engine 1.
A propeller 4 is drivingly connected through the engine 1, and the boat can be propelled forward or backward depending on the direction of rotation of the engine 1. Also, engine 1
At the same time, the gear 7 is meshed with the gear 6 fixed to the main shaft 2 ₂ driven by the generator 5 so as to serve as a power source for driving the generator 5.
A shaft 8 integral with the gear 7 constitutes a speed-increasing gear train, and on the one hand, a slipping clutch 9
On the other hand, it can be connected to the generator 5 via its output shaft ₅₁ , and on the other hand, it can be connected to the generator 5 through its output shaft 51.
In order to control the actuation of the clutch 9, it is connected to a hydraulic pump 10 for generating hydraulic pressure to supply its control piston ₉₁ . The pressure oil generated by this hydraulic pump 10 is passed through a pipe line 11 to a control piston ₉₁ for pressing the clutch plate of the slipping clutch 9, and is then regulated to a constant oil pressure via a regulating valve 12. The water is supplied through a branch line 14 including a switching valve 13.
Further, a pipe line 15 is branched from this pressure oil pipe line 11, and this branch line 15 passes through a rotational speed control valve 16 and is connected to a centrifugal control valve attached to the clutch carrier on the output shaft side of the slipping clutch 9. 17 to press the valve body radially inward. The control piston ₉₁
The pressure of the pressure oil supplied to the generator 5 is controlled to maintain the generator 5 at a constant rotational speed regardless of its load. Regarding centrifugal control valves, for example, ``Friction clutch having centrifugal operation valve means'' is described in Japanese Patent Publication No. 44-29801.
A device such as that disclosed in the US Pat.

In addition, in the arrangement shown in FIG. 1, a lubricating oil pump 18 for pumping lubricating oil to the slipping clutch 9 can be driven independently by a motor 19, The lubricating oil is supplied to the slipping clutch 9 through a conduit 20, after being adjusted to a predetermined pressure by a pressure regulating valve 21, through a restriction 22.

In the conventional marine self-reversing engine-driven generator having such a configuration, as is clear from this configuration, the engine 1 is driven in the forward direction, and the forward rotation of the propeller 4 causes the ship to move. When moving forward, the gear ₆ ,
7 and shaft 8 is also driven in the forward direction, pressurized oil is pumped through line 11 and line 1.
4 and 15 to the control piston ₉₁ of the slipping clutch 9 and the centrifugal control valve 17, respectively, and under the control of the rotational speed control valve 16 and the centrifugal control valve 17, the generator 5 is maintained at the rated speed regardless of the load. It is now possible to drive the vehicle while maintaining the

However, when the forward/reverse rotation engine 1 is driven in the reverse direction to move the ship astern, the hydraulic pump 10, which is driven from the main shaft ₂₂ via the gears 6, 7 and the shaft 8, is also driven in the reverse direction. Therefore, it becomes impossible to generate pressurized oil. Therefore, in the case of reverse rotation of the engine 1, the supply of pressure oil to the slipping clutch 9 is immediately cut off, so that the drive of the generator 5 is also stopped. However, even in this case, since the hydraulic pump 10 is forced to continuously rotate in reverse, phenomena such as air being sucked into the hydraulic pump 10 occur. Therefore, in order to operate the hydraulic pump 10 normally when the engine 1 resumes driving in the forward direction, work such as replenishing the hydraulic oil is required.

As described above, conventionally known generators of this type are effectively driven when the ship is moving forward, but when the ship is restarted after stopping operation when moving astern,
Various inconveniences have occurred, such as the need for some supplementary work on the hydraulic pump 10.

Therefore, the present invention solves these inconveniences in the conventional marine self-reversing engine drive, which enables smooth re-operation of the generator immediately when switching from reverse rotation to forward rotation of the engine. The purpose is to obtain a control device for a shaft generator.

In order to achieve this objective, the control device according to the present invention is provided with a hydraulic slipping clutch which is driven via a speed increasing gear from the main shaft of a ship driven by a self-reversing engine, and whose output is A generator is directly coupled to the shaft, in which case the slipping clutch is provided with means for maintaining a constant rotational speed of the output shaft, and the slipping clutch supplies clutch hydraulic fluid to the control piston. A hydraulic pump for clutch actuation is also driven by its output shaft, and a lubricating oil pump for supplying lubricating oil to the slipping clutch is provided so that it can be driven independently. A pipe line for supplying pressure oil from the lubricating oil pump to the slipping clutch is provided, and a lubricating oil supply line is branched from the lubricating oil pump to the slipping clutch. , is directly connected to the control piston of the slipping clutch via a clutch hydraulic oil switching valve, and is directly connected to a conduit having means for maintaining the rotational speed of the output shaft of the slipping clutch constant. This is a characteristic feature.

Note that the means for maintaining the rotational speed of the output shaft of the slipping clutch constant may be electrical means instead of mechanical means.

Hereinafter, the present invention will be explained based on FIGS. 2 to 4 of the accompanying drawings showing embodiments thereof. In these figures, the same or similar members as in the apparatus shown in FIG. 1 are given the same reference numerals as in FIG. 1.

First, FIG. 2 shows a first embodiment of the present invention. In this embodiment, as shown in the figure, _a speed increasing gear 6,
A generator 5 is connected to an output shaft ₅₁ of a slipping clutch 9 connected to the slipping clutch ₉ via a gear 30, and a gear 30 is attached to the output shaft 51, and a hydraulic pump 10 is driven via a gear 31 meshing with this gear 30. It is designed to do so. Further, the pressure oil generated by this hydraulic pump 10 passes through a line 33 having a check valve 32 and is connected to the centrifugal control valve 17 of the slipping clutch 9 and the control piston 9 in FIG. Branch line 15 similar to that shown
A speed control valve 16 and a hydraulic pressure oil switching valve 13 are arranged in each of the pipes 15 and 14, respectively. At the same time, the pressurized lubricating oil discharged from the lubricating oil pump 18 is transferred to a pipe line 3 branched from the pipe line 20.
4 through a check valve 35 and connected to a conduit 33 from the hydraulic pump 10 downstream of the check valve 32.

This embodiment has such an arrangement, but
Its operation will be explained as follows.

First, the lubricating oil pump 18 is operated at all times,
The lines 20 and 34 provide ready supply of pressurized lubricating oil via the check valve 35 to the slipping clutch 9 and the centrifugal control valve 17 via lines 14 and 15. In this state, when the forward/reverse rotation engine 1 is rotated in the forward direction, by opening the hydraulic oil switching valve 13 at the same time, the engine 1 can be rotated in the same manner as in the arrangement shown in FIG. The generator 5 will be driven gradually via the slipping clutch 9. At this time, the supply of pressurized lubricating oil from the hydraulic pump 10 to the conduit 33 is still blocked by the check valve 32. However, as the rotation of the generator 5 increases, the rotation of the hydraulic pump 10 in the forward direction via the gears 30 and 31 also increases, and the hydraulic pump 10
The pressure from
The slipping pipe 14 and the branch pipe 15
Pressure oil at a predetermined pressure is supplied to the clutch 9, and the generator 5 is continuously driven through the clutch 9. Further, at this time, the supply of pressurized lubricating oil from the lubricating oil pump 18 is stopped by closing the check valve 35 due to the higher pressure from the hydraulic pump 10.

On the other hand, when the forward/reverse rotation engine 1 is rotated in the reverse direction, the generator 5 is stopped, so the hydraulic pump 10 is not operated, and therefore, no air suction occurs. At the same time as the rotation of the engine 1 is switched in the forward direction, the oil pressure of the lubricating oil pump 18 that is always present is used as described above.
Driving of the generator 5 is immediately resumed.

In this case, the forward/reverse changeover switch (not shown) of the engine 1 and the changeover valve 13 of the operating hydraulic pressure of the slipping clutch 9 are electrically linked, so that the forward/reverse changeover switch (not shown) of the engine 1 is electrically linked with the changeover valve 13 of the hydraulic pressure of the slipping clutch 9, so that the forward/reverse changeover switch (not shown) of the engine 1 is electrically interlocked with the changeover valve 13 of the hydraulic pressure of the slipping clutch 9. By making the switching valve 13 freely switchable between opening and closing, its operation can be performed automatically and reliably.

Next, FIG. 3 shows another embodiment of the present invention. In this embodiment, the rotation speed control valve 16 and the centrifugal control valve 17 in the embodiment shown in FIG. The electro-hydraulic converter 42 uses a rotation speed detector 40 for detecting the rotation speed of the machine 5, a PID controller 41 connected thereto, and an electro-hydraulic converter 42 controlled thereby. It consists of essentially the same hydraulic circuit as shown in FIG. 2, except that it is arranged downstream of the switching valve 13 in the hydraulic line ₁₄ to the control piston 91 of the slipping clutch 9.

In this embodiment as well, the generator 5 is driven in exactly the same way as in the embodiment shown in FIG. instrument 40, PID controller 4
1 and the electro-hydraulic converter 42 to maintain a constant value. Incidentally, since such electrical control of the slipping clutch is conventionally known, a description of the structure and operation of each member thereof will be omitted.

Furthermore, in the above embodiment, the generator and hydraulic pump were driven from the bow side of the self-reversing engine via the slipping clutch.
It is clear that it could also be driven in a similar manner from the propulsion shaft on the stern side.

As described above, the present invention allows a marine self-reversing engine-driven shaft generator to smoothly and easily resume operation from a stopped state when the engine is rotating in reverse to when the engine changes to normal rotation. Therefore, various problems and difficulties in conventional equipment can be solved.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram showing one example of the arrangement of a conventional marine self-reversing engine drive shaft generator, FIG. 2 is a schematic diagram of the overall arrangement showing one embodiment of the present invention, and FIG.
It is a schematic diagram showing a modified example thereof. 1... Engine, 5... Generator, 5 ₁ ... Output shaft, 6, 7... Speed increasing gear, 9... Hydraulic slipping clutch, 10... Hydraulic pump for clutch actuation, 12, 21... Pressure regulating valve, 13... switching valve,
14, 15...Pipeline, 16...Rotation speed control valve, 1
7... Centrifugal control valve, 18... Lubricating oil pump, 19
...Motor, 30, 31...Gear, 33, 34...
...Pipeline, 40...Rotation speed detector, 41...PID
Controller, 42...Electro-oil converter.

Claims (1)

[Claims for Utility Model Registration] 1. A hydraulic slipping clutch 9 driven by a main shaft 2 ₂ or 2 ₁ of a ship driven by a self-reversing engine 1 through speed increasing gears 6 and 7. and the input shaft of the generator 5 is directly connected to the output shaft 5 ₁ , in which case the slipping clutch 9 is provided with means for maintaining the rotational speed of the output shaft 5 ₁ constant, and , a clutch operating hydraulic pump 10 for supplying clutch operating pressure oil to the control piston 9 ₁ of the hydraulic slipping clutch 9 is driven by the output shaft 5 ₁ of the slipping clutch 9; A lubricating oil pump 18 for supplying lubricating oil to the slipping clutch 9 is provided to be able to be driven independently, and a pipe line 33 is connected from the hydraulic pump 10 for clutch operation to the slipping clutch 9, and the lubricating oil pump 18 is connected to the slipping clutch 9. A lubricating oil supply pipe 34 is connected to the clutch 9, and these pipes 33, 34 are connected to each other.
After merging through the check valves 35 and 32 provided respectively, the clutch operating pressure oil is connected from the switching valve 13 to the hydraulic control mechanisms 17 and 42 through the pipe 14.
A control device for a self-reversing engine drive shaft generator for marine vessels, which is connected to a control piston ₉₁ of a slipping clutch 9 through a control piston 91 of a slipping clutch 9. 2 a forward/reverse switch for the self-reversing engine 1;
The clutch operating pressure oil switching valve 13 is connected to the forward/reverse switching switch for forward and reverse rotation.
The clutch operating pressure oil switching valve 13 is
The control device according to claim 1 of the utility model registration, wherein the control device is interlocked to switch between opening and closing. 3. Means 16, 17 for maintaining constant rotational speed of the output shaft ₅₁ of the slipping clutch 9
However, the rotational speed control valve 16 disposed in the pipe line 15
and a centrifugal control valve 17 attached to the slipping clutch 9. 4 Means for maintaining the rotational speed of the output shaft ₅₁ of the slipping clutch 9 constant includes a rotational speed detector 40 for the output shaft ₅₁ , a PID controller 41 connected to this, and a PID controller 41 connected to this. The electro-hydraulic converter 42 is controlled by the electro-hydraulic converter 4.
2 is a clutch operating pressure oil switching valve 1 in the pipe line 14;
3. The control device according to claim 1 or 2 of the utility model registration claim, which is provided downstream of the controller.