JPH0443439Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Industrial Application Field] 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 counter-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 hull outer plate 13' and protrude toward the stern side. There is.

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. 3, 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. The oil flows into the outer shaft 2' through the rear outer shaft hole 23' and between the oil grooves 5',
8' and 24' lubricate the bearing bush 3' and floating bush 6' that constitute the inner shaft bearing on the stern side, and then flow forward between the inner shaft 1' and the outer shaft 2', and lubricate the inner shaft on the bow side. The lubricating oil lubricates the bearing bush 3' and floating bush 6' constituting the shaft bearing, and is discharged from the lubricating oil outlet hole 20' via the outer shaft hole 25'.

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 (signs 3', 6', 9'', 1
Since there are many oil holes (see 23', 25', 26', and 27') provided on the inner shaft 1' and the outer shaft 2', 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 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. If bushes 3' and 6' are used, 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. 5 and 6 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' on the stern side is supplied from the back surface 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. 5 and 6, lubricating oil is supplied from the back surface of the flange 30a', so hydraulic pressure acts directly on the back surface of the flange 30a', as shown in FIG. Then, the flange 30a' is pressed against the notch 2a' of the outer shaft 2'.

Therefore, the floating bush 30', which should be stationary and floating between the inner shaft 1' and the outer shaft 2', rotates with the outer shaft 2' due to the frictional force, and as a result, the floating bush 30' and the inner shaft 1' 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 by ensuring the reliable flow of lubricating oil and suppressing the floating bush's tangling with the outer shaft, thereby improving the lubrication performance of the bearing. An object of the present invention is to provide a bearing lubrication device for a counter-rotating marine propeller, which has improved performance.

[Means for solving problems]

Therefore, the bearing lubricating 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 rear inner circumference of the outer shaft in a counter-rotating propeller shaft system installed at the stern of the ship. and an inner shaft supported concentrically inside the floating bush, and a flange is formed at the rear end of the floating bush to engage with the stepped portion of the outer shaft on the front surface, and An oil port for supplying lubricating oil to the bushing is formed on the outer circumferential surface of the inner shaft in front of the back surface of the flange, and is connected to a lubricating oil supply path passing inside the inner shaft. It is said that

[Effect]

In the bearing lubrication device for marine contra-rotating propellers of the present invention described above, the floating bush that supports the inner shaft includes:
Lubricating oil passes through a lubricating oil supply path inside the inner shaft and is supplied from an oil port formed on the outer peripheral surface of the inner shaft.

Furthermore, since the oil port is formed in front of the back surface of the flange of the floating bushing, the oil pressure of the lubricating oil does not directly act on the back surface of the flange, so that the floating bush may not rotate along with the outer shaft. This allows the floating bush to approach a stationary state.

In other words, the lubricating oil supplied from the oil port is
In the conventional case, the lubricating oil flows directly into the oil chamber facing the back surface, as it is squeezed between the outer circumferential surface of the inner shaft and the inner circumferential surface of the floating bush and goes around to the back surface of the flange. Compared to this, the oil pressure in the oil chamber is less likely to rise, and the force acting on the back of the floating bushing flange becomes weaker by the amount of the reduction in oil pressure.
This prevents the bush from twisting around the outer shaft.

〔Example〕

Hereinafter, embodiments of the present invention will be explained with reference to the drawings. Fig. 1 is a longitudinal sectional view showing a bearing lubricating device for a contra-rotating marine propeller as a first embodiment of the invention, and Fig. 2 is a longitudinal sectional view showing a bearing lubricating device for a contra-rotating marine propeller as a first embodiment of the invention. It is a longitudinal cross-sectional view showing a bearing lubricating device for a marine contra-rotating propeller as a second embodiment.

As shown in FIG. 1, in a contra-rotating marine propeller to which the device of the first embodiment of the present invention is applied, a tubular outer shaft 4 having a front propeller 6 at its rear end passes through a stern frame 16. is arranged,
The stern frame 16 and the outer shaft 4 are supported by a stern outer shaft bearing 9 and a bow outer shaft bearing 10, which are interposed between the stern frame 16 and the outer shaft 4. These outer shaft bearings 9, 10
Both are configured as normal stern tube bearings.

In addition, an inner shaft 1 having a rear propeller 5 at the rear end
is disposed to penetrate through the outer shaft 4, and the inner shaft 1 is provided with floating bushes 7, 8 as inner shaft bearings along the inner circumference of the outer shaft 4.
These are supported concentrically inside the floating bushes 7 and 8.

These inner shaft 1 and outer shaft 4 are connected to a reversing device and a main engine (not shown) via an outer shaft joint 3, a hollow shaft 2 split in two, etc., and are connected to a propeller 5.
and 6 are rotated in mutually opposite directions at substantially constant speeds.

On the other hand, the outer shaft sealing devices 12 and 13 are connected to the stan frame 1 in the outboard and inboard areas, respectively.
6 and the outer shaft 4, and inner shaft sealing devices 11 and 14 are provided between the outer shaft 4 and the inner shaft 1 on the outboard and inboard sides, respectively. - 14 are designed to prevent relative axial movement of the outer shaft 4, inner shaft 1, and stand frame 16, as well as to prevent leakage of lubricating oil in the floating bushes 7, 8 and outer shaft bearings 9, 10. It's summery.

In addition, in the floating bushes 7 and 8 that support the inner shaft 1, a large number of white metal strips (not shown) are fixed along the axial direction on the inner and outer peripheral surfaces thereof to form lubricating oil grooves, and the ends thereof for,
Flanges 7a, 8a projecting outward are formed, respectively, and these flanges 7a, 8a
The floating bushes 7, 8 are positioned in the axial direction by coming into contact with notches 4a, 4a formed in the inner periphery of the rear end and the inner periphery of the front end of the outer shaft 4, respectively. That is, the immovable bush 7 serving as a bearing along the rear inner periphery of the outer shaft 4 is configured such that its front surface can engage with a step in the notch 4a of the outer shaft 4.

As shown in FIG. The channel 19 is connected to a fuel supply pipe (not shown) at its bow end, and
An oil port 19 is formed on the outer peripheral surface of the inner shaft 1 toward the inner peripheral surface of the floating bush 7, forward of the back surface of the flange 7a of the floating bush 7 on the stern side.
connected to a.

On the other hand, an oil supply pipe 20 is connected between the outer shaft seal device 12 and the stern outer shaft bearing 9 in order to supply lubricating oil to the seal device 12 and the outer shaft bearing 9.

Further, an outer shaft oil supply hole 21 is formed at the rear end of the outer shaft 4 in order to further guide the lubricating oil supplied to the seal device 12 and the outer shaft bearing 9 through the oil supply pipe 20 to the floating bush 7 on the stern side. The outer shaft oil supply hole 21 is connected to an oil port 21a formed in a notch 4a on the inner surface of the outer shaft 4 in front of the back surface of the flange 7a of the floating bush 7.

Further, an outer shaft is provided at the front end of the outer shaft 4 in order to guide the lubricating oil that has lubricated the floating bush 8 on the bow side and the inner shaft seal device 14 to the outer shaft seal device 13 and discharge it from the inside of the outer shaft 4. A shaft oil drain hole 25 is formed.

Note that an oil drain pipe 22 is connected between the outer shaft bearing 10 and the outer shaft seal device 13, and an oil drain pipe 23 is connected to the outer shaft seal device 13. 23 is connected to a lubricating oil tank (not shown).

Further, in FIG. 1, reference numeral 15 indicates a drain plug, 17 indicates a rear partition wall of the engine room, 18 indicates a rope guard, and 24 indicates a sight glass installed in the oil drain pipes 22 and 23, respectively.

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). The lubricating oil is supplied to a lubricating oil supply path 19 and an oil supply pipe 20 inside the inner shaft 1 .

In this way, the lubricating oil supplied to the lubricating oil supply path 19 of the inner shaft 1 flows from the bow side to the stern side through the lubricating oil supply path 19, and flows from the oil port 19a to the floating bush 7 on the stern side. and lubricates the floating bush 7 and the inner shaft sealing device 11.

The lubricating oil that lubed the floating bush 7 is
The oil flows toward the bow side along the gap between the inner shaft 1 and the outer shaft 4, and after lubricating the floating bush 8 on the bow side and the inner shaft sealing device 14, the outer shaft oil drain hole 25 formed in the outer shaft 4 flows. The oil flows out to the outer shaft sealing device 13 outside the outer shaft 4 to lubricate the sealing device 13, and then returns to the lubricating oil tank (not shown) through the oil drain pipe 23.

On the other hand, after the lubricating oil fed to the oil supply pipe 20 lubricates the outer shaft sealing device 12 , a part of it flows into the outer shaft oil supply hole 21 , and the remaining lubricating oil flows into the outer shaft 4 . It flows along the outer circumferential surface towards the bow side.

The lubricating oil that has flowed into the outer shaft oil supply hole 21 flows out from the oil port 21a that opens toward the front surface of the flange 7a of the floating bush 7 in the outer shaft 4, and together with the lubricating oil that flows out from the oil port 19a, it flows into the inner shaft. After lubricating the oil seal device 11 and the floating bush 7, the oil drain pipe 23 passes through the floating bush 8, the inner shaft seal device 14, the outer shaft oil drain hole 25, and the outer shaft seal device 13 to a lubricating oil tank (not shown). will be returned to.

Furthermore, the lubricating oil flowing along the outer peripheral surface of the outer shaft 4 flows through the stern outer shaft bearing 9 and the bow outer shaft bearing 10.
After lubricating the oil, the oil is returned to a lubricating oil tank (not shown) through the oil drain pipe 22.

As described above, according to the bearing lubrication device for a counter-rotating marine propeller of the first embodiment of the present invention, the lubricating oil supply system is changed from the conventional one system to the lubricating oil supply system that lubricates the outer shaft system and the inner shaft system. 2 with a lubricating oil supply system that lubricates the system.
Since it is divided into systems, it is possible to lubricate each bearing and shaft sealing device with low-temperature, high-quality lubricating oil, making it possible to dramatically improve the performance of each bearing compared to conventional systems.

In addition, the lubricating oil for lubricating the floating bushing 7 on the stern side flows out from the oil ports 19a and 21a in front of the back surface of the flange 7a of the floating bushing 7, so that the oil pressure of the lubricating oil is reduced as in the conventional case. It no longer acts directly on the back surface of the flange 7a, and the rotation of the floating bush 7 with respect to the outer shaft 4 can be suppressed.

In other words, the lubricating oil supplied from each oil port 19a, 21a is squeezed between the floating bush 7 and each of the inner shaft 1 and outer shaft 4, and then flows to the flange 7a.
Since the lubricating oil flows around to the oil chamber on the rear side of the oil chamber, compared to the conventional case where lubricating oil flows directly into the oil chamber, the oil pressure in the oil chamber is less likely to increase, and the force acting on the rear side of the flange 7a is reduced by the amount of decrease in oil pressure. This prevents the floating bush 7 from rotating around the outer shaft 4.

Therefore, the floating bush 7 can be brought close to a stationary state, and the formation of an oil film between the floating bush 7 and the inner shaft 1 is promoted, so problems such as seizure do not occur, and the lubrication in the inner shaft bearing is improved. Performance is greatly improved.

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. 2, this second embodiment is also applied to the same contra-rotating propeller shaft system as the first embodiment and has almost the same structure, but in the second embodiment, the stern side outer shaft bearing 9 In addition to using hydrostatic bearings as
A lubricating oil supply path 19 inside the inner shaft 1 is connected to an oil port 19a' formed on the outer peripheral surface of the inner shaft 1 between the floating bushes 7 and 8. That is, the oil port 19a' is provided in front of the back surface of the floating bush 7.

Further, an outer shaft oil drain pipe 27 is formed at the rear end of the outer shaft 4 in order to guide the lubricating oil that has lubricated the floating bush 7 on the stern side to the outer shaft sealing device 12 outside the outer shaft 4. At the same time, an oil drain pipe 26 is interposed between the seal device 12 and the oil drain pipe 22 in order to return the lubricating oil guided to the seal device 12 to a lubricating oil tank (not shown).

Further, a high pressure supply pipe 28 is provided to supply high pressure lubricating oil to the stern outer shaft bearing (static pressure bearing) 9'.

With the above-described configuration, the lubricating oil supply path 19 of the inner shaft 1
The lubricating oil supplied flows out from the oil port 19a' into the gap between the inner shaft 1 and the outer shaft 4, and flows along the outer peripheral surface of the inner shaft 1 toward the bow side and toward the stern side. Divided into things.

As in the first embodiment, the lubricating oil flowing toward the bow lubricates the floating bush 8 and the inner shaft seal device 14 on the bow side, and then flows through the outer shaft oil drain hole 25 formed in the outer shaft 4. The oil flows out to the outer shaft sealing device 13 outside the outer shaft 4 to lubricate the sealing device 13, and then returns to the lubricating oil tank (not shown) through the oil drain pipe 23.

In addition, the lubricating oil flowing toward the stern side is transferred to the floating bush 7 and the inner shaft sealing device 11 on the stern side.
After lubricating the outer shaft oil drain hole 2 formed in the outer shaft 4,
7 to the outer shaft sealing device 12 outside the outer shaft 4 to lubricate the sealing device 12, and then to the oil drain pipe 2.
6 and 22, and is returned to a lubricating oil tank (not shown).

On the other hand, high-pressure lubricating oil is supplied to the stern outer shaft bearing 9' from a high-pressure oil pump (not shown) through a high-pressure oil supply pipe 28. This lubricating oil is also divided into two types: one that flows toward the bow side along the outer peripheral surface of the outer shaft 4, and the other that flows toward the stern side.

As in the first embodiment, the lubricating oil flowing toward the bow side is transferred to the stern outer shaft bearing (static pressure bearing).
After lubricating the outer shaft bearing 9' and the bow side outer shaft bearing 10, the oil is returned to a lubricating oil tank (not shown) through the oil drain pipe 22.

Further, the lubricating oil flowing toward the stern side lubricates the stern side outer shaft bearing (static pressure bearing) 9' and the outer shaft sealing device 12, and then flows into the oil drain pipe 26 along with the lubricating oil from the outer shaft oil drain hole. , 22 and is returned to a lubricating oil tank (not shown).

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 contra-rotating propeller shaft system installed at the stern, the tubular outer shaft and the rear inner periphery of the outer shaft are The floating bushing is provided with a floating bushing as a bearing, and an inner shaft supported concentrically inside the floating bushing, and a flange is formed at the rear end of the floating bushing to engage with the stepped part of the outer shaft on the front surface. and an oil port for supplying lubricating oil to the floating bush is formed on the outer peripheral surface of the inner shaft in front of the back surface of the flange,
It has a simple configuration in which it is connected to a lubricating oil supply path that runs through the inside of the inner shaft, and the lubricating oil supply system has a lubricating oil supply system that lubricates the outer shaft system and a lubricating oil supply system that lubricates the inner shaft system. Since it is divided into two systems, low-temperature, high-quality lubricating oil is directly supplied to each of the outer shaft bearing and inner shaft bearing, and the sliding surfaces of the outer shaft bearing and inner shaft bearing are constantly maintained. Since they are fluid-lubricated, the bearing performance of the outer and inner shafts can be dramatically improved.

Furthermore, since the floating bush can be suppressed from spinning around the outer shaft, the floating bush can be brought close to a stationary state, and the formation of an oil film between the floating bush and the inner shaft is promoted. 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]

FIG. 1 is a longitudinal sectional view showing a bearing lubricating device for a contra-rotating marine propeller as a first embodiment of the present invention, and FIG. Fig. 3 is a vertical cross-sectional view showing a lubricating device, and Figs. 3 to 6 show a conventional bearing lubricating device for a counter-rotating marine propeller. FIG. 5 is a longitudinal cross-sectional view showing a modified example of the floating bush, and FIG. 6 is a vertical cross-sectional view showing the rotating state of the modified example. 1... Inner shaft, 2... Hollow shaft split in two, 3... Outer shaft joint, 4... Outer shaft, 4a... Notch, 5
...Rear propeller, 6...Front propeller, 7...
Floating bush, 7a...flange, 8...floating bush, 8a...flange, 9...stern side outer shaft bearing, 9'...stern side outer shaft bearing (static pressure bearing), 10...
... Bow side outer shaft bearing, 11 ... Seal device for inner shaft,
12, 13... Seal device for outer shaft, 14... Seal device for inner shaft, 15... Plug, 16... Stun frame, 17... Rear bulkhead of engine room, 18...
Rope guide, 19... Lubricating oil supply path, 19a...
...oil port, 20...oil supply pipe, 21...outer shaft oil supply hole,
21a... Oil port, 22, 23... Oil drain pipe, 24...
...Sight glass, 25... Outer shaft oil drain hole, 26...
Oil drain pipe, 27... Outer shaft oil drain hole, 28... High pressure oil supply pipe.

Claims (1)

[Scope of utility model registration request] In the contra-rotating propeller shaft system installed at the stern, there is a tubular outer shaft, a floating bush as a bearing along the rear inner circumference of the outer shaft, and an inner shaft supported concentrically inside the floating bush. At the rear end of the floating bushing, a flange is formed which engages the step part of the outer shaft on the front surface, and an oil port for supplying lubricating oil to the floating bushing is formed from the back surface of the flange. A bearing lubricating device for a counter-rotating marine propeller, characterized in that a bearing lubricating device is formed on the outer circumferential surface of the inner shaft at the front and is connected to a lubricating oil supply path passing through the inside of the inner shaft.