JPH0439840Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Field of Application] The present invention relates to a bearing lubrication device in the shaft system of a counter-rotating propeller used as a propulsion device for ships.

[Conventional technology]

Conventionally, the shaft system and its bearing lubrication system of a contra-rotating propeller device used as a propulsion device for ships are constructed as shown in FIGS. An outer shaft 2' and an inner shaft 1' that is fitted into the outer shaft 2' and rotates the rear propeller 11' are provided so as to penetrate the stern frame 13' and protrude toward the stern side.

The inner shaft 1' and the outer shaft 2' are connected to a reversing device and a main engine (not shown), and are driven to rotate in opposite directions.

In addition, as shown in Fig. 4, the front propeller 1
Between the outer shaft 2' and the inner shaft 1' near 2',
A bearing bushing 3' with oil grooves 24' and 5' formed on the outer and inner peripheral surfaces of the white metal 4', respectively, is inserted into the outer shaft 2', and the same bearing bush 3' and the inner shaft 1' A floating bush 6' with oil grooves 8' formed on the outer and inner circumferential surfaces of the white metal 7' is inserted between the stern side and the inner shaft 1' to support the inner shaft 1' concentrically with the outer shaft 2'. The inner shaft bearing is configured.

Similarly, the rear bulkhead 14' of the engine room inside the hull
A bearing bush 3' and a floating bush 6' are also inserted between the outer shaft 2' and the inner shaft 1' in the vicinity of the front part of the boat, thereby forming an inner shaft bearing on the bow side.

On the other hand, on the outer periphery of the outer shaft 2' in the front part of the rear partition wall 14' of the engine room, there is a lubricating oil inlet hole 19' for supplying lubricating oil to the bearing, and a lubricating oil inlet hole 19' for discharging the oil after lubrication. Outlet holes 20', 21' are provided.

In order to circulate lubricating oil, an inner shaft hole 26' is formed in the inner shaft 1', and outer shaft holes 23', 25', and 27' are formed in the outer shaft 2'.

The hull is also provided with a stern fixed bearing bush 9'' and a bow fixed bearing bush 10' for supporting the outer shaft 2'.

In FIG. 4, numerals 15' to 18' represent sealing devices, and 28' represents a backflow prevention lip.

With the above-described configuration, when the ship is sailing, the inner shaft 1' and the outer shaft 2' are driven to rotate in opposite directions at approximately the same rotational speed, so that the propellers 11', 1
The rotational energy that was flowing out to the rear of the propeller 2' is recovered, making it possible to increase the propulsion efficiency compared to a general ship with a single propeller.

At this time, the lubricating oil supplied from the lubricating oil inlet hole 19' is applied to the outer peripheral surfaces of the bow side fixed bearing bush 10', the stern side fixed bearing bush 9'' and the outer shaft 2', as shown by the arrows in FIG. Oil grooves 5', 8',
After lubricating the bearing bush 3' and floating bush 6' that constitute the inner shaft bearing on the stern side with 24',
The flow flows forward between the inner shaft 1' and the outer shaft 2', lubricates the bearing bush 3' and floating bush 6' that constitute the inner shaft bearing on the bow side, and passes through the outer shaft hole 25' to the lubricating oil outlet hole. It is discharged from 20'.

Also, a part of the lubricating oil that has lubricated the inner shaft bearing on the bow side is sent to the sealing device 17' through the inner shaft hole 26', and then is sent to the sealing device 17' through the front outer shaft hole 27'.
After being sent to 8', it is discharged from the lubricating oil outlet hole 21'.

In this way, each bearing is lubricated by the lubricating oil, and the sealing devices 17', 18' are cooled.

Note that the lubricating oil is circulated by piping and a pump (not shown), and a lubricating oil cooling device is also provided as necessary.

Further, the seal devices 15' and 16 are in contact with outside water and are cooled by this outside water.

[Problem that the invention attempts to solve]

However, in the conventional bearing lubrication system for marine contra-rotating propellers as described above, there is only one lubricating oil supply system, so the path is extremely long.
Also, bearings (symbols 3', 6', 9', 1
Since there are many oil passage holes (see 23', 25', 26', and 27) provided on the inner shaft 1' and the outer shaft 2' (see 0'), the resistance to lubricating oil becomes extremely large.

Therefore, it is necessary to increase the lubricating oil supply pressure compared to normal ships, and the seal devices 15' to 1
This will adversely affect the sealing performance of 8'.

In addition, the inner shaft bearing on the stern side has severe operating conditions such as uneven contact and bearing load, and it is necessary to supply lubricating oil with a low oil supply temperature to form an oil film. The lubricating oil that lubricates the inner shaft bearing on the stern side, which has a long path, is supplied to the fixed bearing bush 9″,
After passing through 10' and sealing devices 16' and 15', it reaches the inner shaft bearing on the stern side, so the temperature there is high and there is a risk of seizure of the bearing.

Furthermore, since the inner shaft bearing is composed of a bearing bush 3' and a floating bush 6', the thickness of each bush 3' and 6' becomes thin, which poses a problem in terms of strength. When using bushes 3' and 6', it is necessary to increase the inner diameter of the outer shaft 2'.
This will lead to an increase in the cost of the shaft system. Therefore, inner shaft bearings as shown in FIGS. 6 and 7 have also been proposed.

That is, the floating bush 3 supporting the inner shaft 1'
0', a large number of white metals 31' are fixed along the axial direction on the inner peripheral surface and the outer peripheral surface to form lubricating oil grooves, and a flange 30a' protrudes outward at the end thereof. The floating bush 30' is positioned in the axial direction by the flange 30a' coming into contact with a notch 2a' formed on the inner periphery of the end of the outer shaft 2'.

Lubricating oil for lubricating the floating bush 30' is supplied from the end face of the flange 30a' through an oil supply hole 29' formed in the outer shaft 2'.

However, in the case of the floating bush 30' shown in FIGS. 6 and 7, lubricating oil is supplied from the end face of the flange 30a', so hydraulic pressure acts directly on the back surface of the flange 30a', as shown in FIG. Not only is the flange 30a' pressed against the notch 2a' of the outer shaft 2', but the area of the outer periphery of the floating bush 30' that contacts the outer shaft 2' is larger than that of the floating bush 30 that contacts the inner shaft 1'. ′ is larger than the area of the inner circumference of
Moreover, the peripheral speed of the inner peripheral surface of the outer shaft 2' is higher than the peripheral speed of the outer peripheral surface of the inner shaft 1'.

Therefore, the floating bush 30', which is to be movable in a stationary state between the inner shaft 1' and the outer shaft 2', is attached to the flange 3'.
Due to the frictional force between 0a' and the notch 2a' and between the outer circumferential surface of the floating bush 30' and the inner circumferential surface of the outer shaft 2', the floating bush 30' is largely dragged around the outer shaft 2', and as a result, the floating bush 30' There is a problem in that an oil film pressure sufficient to support the load is not generated between the floating bush 30' and the inner shaft 1', and the floating bush 30' and the inner shaft 1' seize.

The present invention attempts to solve these problems, and is a bearing for counter-rotating marine propellers that suppresses the rotation of the floating bush with the outer shaft and improves the lubrication performance of the bearing. The purpose is to provide a lubricating device.

[Means for solving problems]

Therefore, the bearing lubrication device for a counter-rotating marine propeller of the present invention has a tubular outer shaft and a floating bush as a bearing along the inner circumference of the outer shaft in a counter-rotating propeller shaft system installed at the stern of the ship. , an inner shaft supported concentrically inside the floating bush,
An inwardly projecting flange is formed at the end of the floating bushing to engage with the enlarged diameter shoulder of the inner shaft, and an oil port for supplying lubricating oil to the floating bushing is formed in the flange. The oil port is formed on the inner peripheral surface of the outer shaft or the outer peripheral surface of the inner shaft so as to separate the center of the oil port from the floating bushing, and is connected to the lubricating oil supply path in order to apply hydraulic pressure to the end face of the oil port. It is characterized by

[Effect]

In the bearing lubricating device for a counter-rotating marine propeller of the present invention described above, the flange of the floating bush is loaded by the hydraulic pressure of the lubricating oil supplied from the oil port and is pressed against the enlarged diameter shoulder of the inner shaft. The frictional force between the flange and the enlarged-diameter shoulder can suppress the floating bush from rotating along the outer shaft, allowing the floating bush to approach a stationary state.

〔Example〕

Embodiments of the present invention will be described below with reference to the drawings. Figures 1 and 2 show a bearing lubricating device for a counter-rotating marine propeller as the first embodiment of the present invention, and Figure 1 is a longitudinal cross-sectional view thereof. 2 is an enlarged sectional view of the floating bush, and FIG. 3 is a longitudinal sectional view showing a bearing lubricating device for a contra-rotating marine propeller as a second embodiment of the present invention.

As shown in FIG. 1, the contra-rotating propeller shaft system to which the device of the first embodiment of the present invention is applied is also constructed almost the same as the conventional one, and the front propeller 4 is rotationally driven at the stern part. Tubular outer shaft 2
and an inner shaft 1 which is fitted into the outer shaft 2 and rotationally drives the rear propeller 3, are provided so as to penetrate the stern frame 16 and protrude toward the stern side.

The outer shaft 2 is supported on the hull side by a bow-side outer shaft bearing 13 and a stern-side outer shaft bearing 14, while the inner shaft 1 is supported within the outer shaft 2 by an inner shaft bearing along the inner circumference of the outer shaft 2. It is supported concentrically inside the floating bushes 11 and 12 by means of floating bushes 11 and 12 as shaft bearings.

These inner shaft 1 and outer shaft 2 are connected to a reversing device and a main engine (not shown) via an outer shaft joint 10, a split hollow shaft 9, etc., and are driven to rotate in opposite directions at substantially constant speeds. It's becoming like that.

On the other hand, outer shaft sealing devices 6 and 7 are provided between the stan frame 16 and the outer shaft 2 on the outboard and inboard locations, respectively, and inner shaft sealing devices 5 and 8 are provided on the outboard and inboard locations, respectively. It is provided between the shaft 2 and the inner shaft 1,
These seal devices 5 to 8 prevent relative axial movement of the outer shaft 2, inner shaft 1, and stan frame 16, respectively, and also prevent the floating bushes 11, 12 from moving relative to each other in the axial direction.
Also, leakage of lubricating oil in the outer shaft bearings 13 and 14 is prevented.

In addition, the reference numeral 15 in FIG. 1 indicates the rear bulkhead of the engine room, and the reference numeral 17 indicates a rope guard.

By the way, the floating bush 12 supporting the inner shaft 1
As shown in Fig. 2, a large number of white metals 12a are fixed along the axial direction on the inner and outer peripheral surfaces to form lubricating oil grooves, and grooves for lubricating oil are formed at the ends thereof. protruding flange 12
b is formed, and this flange 12b is adapted to engage with an enlarged diameter shoulder portion 1a formed on the outer periphery of the inner shaft 1.

Note that the floating bush 11 is also formed in the same manner as the floating bush 12, as shown in FIG.

In the device of the first embodiment of the present invention for lubricating the bearing of the shaft system for a marine contra-rotating propeller as described above, as shown in FIG.
Oil ports 27a, 25 that supply lubricating oil to 1, 12
In order to apply hydraulic pressure to the end faces 11c and 12c of the flanges 11b and 12b of the floating bushes 11 and 12, respectively, the outer shaft 2 is separated from the centers of these oil ports 27a and 25a from the floating bushes 11 and 12. It is formed on the inner circumferential surface of the lubricating oil supply path and is connected to the outer shaft oil supply holes 27 and 25 as a lubricating oil supply path.

On the other hand, the outer shaft sealing device 6 and the stern outer shaft bearing 1
4, an oil supply pipe 24 is connected to supply lubricating oil to the seal device 6 and the outer shaft bearing 14.

In addition, the rear end of the outer shaft 2 is provided with the aforementioned lubricating oil supply path in order to further guide the lubricating oil supplied to the seal device 6 and the outer shaft bearing 14 through the oil supply pipe 24 to the floating bush 12 on the stern side. An outer shaft oil supply hole 25 is formed.

Furthermore, an oil supply pipe 26 is connected to the outer shaft sealing device 7 in order to supply lubricating oil to the sealing device 7, and an oil supply pipe 26 is connected to the front end of the outer shaft 2.
In order to further guide the lubricating oil supplied to the seal device 7 to the floating bush 11 on the bow side, the outer shaft oil supply hole 27 is formed as the aforementioned lubricating oil supply path.

In order to discharge the lubricating oil after lubricating the floating bushes 11 and 12 from the gap between the inner shaft 1 and the outer shaft 2, in the vicinity between the outer shaft sealing device 7 and the bow side outer shaft bearing 13, An outer shaft oil drain hole 28 is formed in the outer shaft 2.

Further, an oil drain pipe 29 is provided near between the sealing device 7 and the outer shaft bearing 13 for discharging lubricating oil from the gap between the outer shaft 2 and the stan frame 16. connected to the oil tank.

Since the bearing lubricating device for a marine counter-rotating propeller according to the first embodiment of the present invention is constructed as described above, lubricating oil stored in a lubricating oil tank (not shown) is sent out by a lubricating oil pump (not shown). It is fed into oil supply pipes 24 and 26.

In this way, the lubricating oil supplied to the oil supply pipe 26 lubricates the outer shaft seal device 7, and then flows into the outer shaft oil supply hole 27 and flows from the oil port 27a to the floating bushing on the bow side in the outer shaft 2. It flows out to around 11.

At this time, the lubricating oil applies hydraulic pressure to the end surface 11c of the flange 11b of the floating bush 11, presses the flange 11b against the enlarged diameter shoulder 1a of the inner shaft 1, and lubricates the inner shaft sealing device 8. It flows to the side and lubricates the floating bush 11.

The lubricating oil that has lubricated the floating bush 11 flows toward the stern side along the gap between the inner shaft 1 and the outer shaft 2, and flows through the outer shaft oil drain hole 28 formed in the outer shaft 2.
After flowing out of the outer shaft 2, the oil is returned to a lubricating oil tank (not shown) through an oil drain pipe 29.

On the other hand, after the lubricating oil supplied to the oil supply pipe 24 lubricates the outer shaft sealing device 6, a part of it flows into the outer shaft oil supply hole 25, and the remaining lubricating oil flows into the outer shaft 2. It flows along the outer circumferential surface toward the bow side.

The lubricating oil that has flowed into the outer shaft oil supply hole 25 flows through the oil port 25.
a flows out to the vicinity of the floating bush 12 on the stern side within the outer shaft 2.

At this time, as in the case of the floating bush 11, the lubricating oil applies hydraulic pressure to the end face 12c of the flange 12b of the floating bush 12, and while pressing the flange 12b against the enlarged diameter shoulder 1a of the inner shaft 1, the lubricating oil is applied to the inner shaft seal. It lubricates the device 5 and flows toward the bow side to lubricate the floating bush 12.

The lubricating oil that has lubricated the floating bushing 12 flows toward the bow side along the gap between the inner shaft 1 and the outer shaft 2, and together with the lubricating oil that has lubricated the floating bushing 11, flows from the outer shaft oil drain hole 28 to the outer shaft. After flowing out of the lubricating oil tank 2, the oil is returned to a lubricating oil tank (not shown) through an oil drain pipe 29.

Furthermore, the lubricating oil flowing along the outer peripheral surface of the outer shaft 2 flows through the stern outer shaft bearing 14 and the bow outer shaft bearing 1.
After lubricating the floating bushes 11 and 12, the floating bushes 11 and 12 are returned to a lubricating oil tank (not shown) through an oil drain pipe 29.

As described above, according to the bearing lubrication device for a marine counter-rotating propeller according to the first embodiment of the present invention, the lubricating oil supply system can be changed from the conventional single system with a complicated and long route to multiple systems with a simple and short route. Since it is divided into three systems (in the first embodiment), it is possible to lubricate each bearing and shaft sealing device with low-temperature, high-quality lubricating oil, dramatically improving the performance of each bearing compared to before. can be increased.

Furthermore, the lubricating oil for lubricating the floating bushes 11, 12 flows out from the oil ports 27a, 25a so as to apply the oil pressure to the end surfaces 11c, 12c of the flanges 11b, 12b of each floating bush 11, 12. The flanges 11b and 12b are pressed against the enlarged diameter shoulders 1a and 1a of the inner shaft 1, respectively.

At this time, a frictional force is generated between each flange 11b, 12b and the enlarged diameter shoulder portions 1a, 1a, and this frictional force is applied so that the floating bushes 11, 12 rotate with the inner shaft 1 having a small rotational moment. It turns out.

Therefore, the rotational moment acting on the floating bushes 11, 12 can be balanced between the outer shaft 2 and the inner shaft 1, which have a large rotational moment, and the rotational moment of the floating bushes 11, 12 with the outer shaft 2 can be balanced. These floating bushes 11 and 12
can be brought close to a stationary state.

As a result, the floating bushes 11 and 12 and the inner shaft 1
This promotes the formation of an oil film between the inner shaft bearing, which prevents problems such as seizure, and greatly improves the lubrication performance of the inner shaft bearing.

Next, a bearing lubricating device for a marine counter-rotating propeller as a second embodiment of the present invention will be explained.
As shown in FIG. 3, this second embodiment is also applied to the same counter-rotating propeller shaft system as the first embodiment and has almost the same construction, but in the second embodiment, the floating In place of outer shaft oil supply holes 25, 27 and oil supply pipes 26 provided for lubricating bushes 11, 12, oil supply passages 18 and lubricating oil supply passages 19, 20 are formed in inner shaft 1.

That is, the oil supply path 1 formed inside the inner shaft 1
8 is connected at its bow side end to a lubricating oil tank (not shown) via an oil supply pipe (not shown), and is also communicatively connected to lubricating oil supply passages 19, 20 formed in the radial direction of the inner shaft 1. The lubricating oil supply paths 19 and 20 are connected to oil ports 19a and 20a formed on the outer peripheral surface of the inner shaft 1, respectively.

These oil ports 19a, 20a are the first oil ports 19a, 20a.
Similar to the embodiment, floating bushes 11 and 1, respectively
End faces 11c, 12 of flanges 11b, 12b of 2
The centers of the oil ports 19a, 20a are separated from the floating bushes 11, 12 in order to apply hydraulic pressure to the oil pumps 19a, 20a.

With the above configuration, the lubricating oil supplied to the oil supply path 18 in the inner shaft 1 passes through the lubricant oil supply paths 19 and 20 from the oil ports 19a and 20a to the inner shaft 1 near the floating bushes 11 and 12, respectively. It flows out into the gap with the outer shaft 2. At this time, the lubricating oil applies hydraulic pressure to the end surfaces 11c and 12c of the flanges 11b and 12b of the floating bushes 11 and 12, and
b, 12b are the enlarged diameter shoulders 1a, 1 of the inner shaft 1, respectively.
It lubricates the sealing devices 8, 5 while being pressed against the tank a, and also lubricates the floating bushes 11, 12 by flowing toward the stern or bow side.

After lubrication, the lubricating oil is returned to the lubricating oil tank (not shown) through the outer shaft oil drain hole 28 and the oil drain pipe 29, as in the first embodiment.

In this way, the second embodiment of the present invention can achieve exactly the same effects as the first embodiment.

[Effect of idea]

As described in detail above, according to the bearing lubrication device for a counter-rotating marine propeller of the present invention, in the counter-rotating propeller shaft system installed at the stern, a tubular outer shaft and a A floating bushing as a bearing and an inner shaft supported concentrically inside the floating bushing are provided, and an end portion of the floating bushing is moved inwardly so as to engage with an enlarged diameter shoulder of the inner shaft. A projecting flange is formed, and an oil port for supplying lubricating oil to the floating bushing is arranged such that the center of the oil port is isolated from the floating bushing in order to apply hydraulic pressure to the end face of the flange. With a simple structure that is formed on the inner circumferential surface of the outer shaft or the outer circumferential surface of the above-mentioned inner shaft and connected to the lubricating oil supply path, it is possible to suppress the tangling of the floating bush with the outer shaft. This makes it possible to bring the floating bushing close to a stationary state, thereby promoting the formation of an oil film between the floating bushing and the inner shaft. Therefore, problems such as seizure do not occur, and there is also the advantage that the lubrication performance of the bearing is greatly improved.

[Brief explanation of the drawing]

Figure 1 shows a bearing lubrication device for a contra-rotating marine propeller as a first embodiment of the present invention, and Figures 1 and 2 show bearing lubrication for a contra-rotating marine propeller as a first embodiment of the present invention. This indicates the device and the first
The figure is a longitudinal sectional view of the same, FIG. 2 is an enlarged sectional view of the floating bush, and FIG. 3 is a longitudinal sectional view of a bearing lubricating device for a contra-rotating marine propeller as a second embodiment of the present invention. 4 to 7 show a conventional bearing lubrication device for a counter-rotating marine propeller, FIG. 4 is a longitudinal cross-sectional view thereof, and FIG. 5 is a perspective view showing the floating bush cut away. FIG. 6 is a longitudinal cross-sectional view showing a modified example of the floating bush, and FIG. 7 is a vertical cross-sectional view showing the rotating state of the modified example. 1... Inner shaft, 1a... Expanded diameter shoulder, 2... Outer shaft,
3... Rear propeller, 4... Front propeller, 5...
... Seal device for inner shaft, 6, 7 ... Seal device for outer shaft, 8 ... Seal device for inner shaft, 9 ... Hollow shaft split in two, 10 ... Outer shaft joint, 11 ... Inner shaft bearing Floating bush as, 11b...flange, 11
c... End face of flange, 12... Floating bush as inner shaft bearing, 12a... White metal, 1
2b...flange, 12c...end face of flange,
13... Bow side outer shaft bearing, 14... Stern side outer shaft bearing, 15... Rear bulkhead of engine room, 16... Stun frame, 17... Rope guard, 18... Oil supply path, 19... Lubricating oil Supply path, 19a... oil mouth, 2
0...Lubricating oil supply path, 20a...Oil port, 24...
Oil supply pipe, 25... Outer shaft oil supply hole as a lubricating oil supply path, 25a... Oil port, 26... Oil supply pipe, 27...
Outer shaft oil supply hole as a lubricating oil supply path, 27a... Oil port, 28... Outer shaft oil drain hole, 29... Oil drain pipe.

Claims (1)

[Scope of utility model registration request] The contra-rotating propeller shaft system installed at the stern has a tubular outer shaft, a floating bush as a bearing along the inner circumference of the outer shaft, and an inner shaft supported concentrically inside the floating bush. An inwardly protruding flange is formed at the end of the floating bushing to engage with the enlarged diameter shoulder of the inner shaft, and an oil port for supplying lubricating oil to the floating bushing. In order to apply hydraulic pressure to the end face of the flange, an oil port is formed on the inner circumferential surface of the outer shaft or the outer circumferential surface of the inner shaft so as to isolate the center of the oil port from the floating bush, and is connected to the lubricating oil supply path. A bearing lubrication device for a marine counter-rotating propeller, characterized in that: