JPH0523437Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a lubricating device for a bearing in a propeller shaft system of a counter-rotating marine propeller.

[Conventional technology]

In general, there is a contra-rotating marine propeller as shown in Fig. 7, in which an outer shaft 2' with a front propeller 12' at the rear end is attached to a stern frame.
3', and the stun frame 1
It is supported by a stern side fixed bearing bush 9' and a bow side fixed bearing bush 10' which are interposed between the inner peripheral surface of the shaft 3' and the outer peripheral surface of the outer shaft 2'. Of these bearing bushes 9', 10', the stern fixed bearing bush 9' is constructed as a hydrostatic bearing, and the bow fixed bearing bush 10' is constructed as a normal stern tube bearing.

The inner shaft 1', which has a rear propeller 11' at its rear end, penetrates the outer shaft 2' and is arranged concentrically with the outer shaft 2', and is supported by inner shaft bearings 24', 24' disposed on the stern and bow sides, respectively, between the inner peripheral surface of the outer shaft 2' and the outer peripheral surface of the inner shaft 1'. These inner shaft bearings 24', 24' are supported by bearing bushes 3' fixed to the inner peripheral surface of the outer shaft 2'.
and a floating bushing 6' that is loosely fitted between the bearing bushing 3' and the outer circumferential surface of the inner shaft 1', thereby forming a hydrodynamic type sliding bearing.

The inner shaft 1' is connected to a reversing device (not shown), and the outer shaft 2' is also split into two hollow shafts 2'.
It is connected to a reversing device (not shown) via 3'.
These inner shaft 1' and outer shaft 2' are connected to the main engine (not shown) via the above-mentioned reversing device, and the propeller 1'
1' and 12' can be rotated in opposite directions.

On the other hand, the outer shaft seal devices 16' and 18' are
An inner shaft sealing device 15' is provided between the stern frame 13' and the outer shaft 2' on the outside and inside the ship, respectively, and an inner shaft sealing device 15' closes the gap between the outer shaft 2' and the inner shaft 1' outside the ship. These seal devices 15', 16', and 18' prevent relative axial movement of the outer shaft 2', inner shaft 1', and stan frame 13', and also prevent the bearings from moving in the relative axial direction. This prevents lubricating oil from leaking from the bushes 9', 10' and the inner shaft bearing 24'.

In the above-mentioned bearing lubrication device for a marine contra-rotating propeller shaft system, as shown in FIG. In order to supply high pressure lubricating oil between the inner peripheral surface of the shaft 9' and the outer peripheral surface of the outer shaft 2',
A high-pressure oil supply pipe 19' is connected, and this high-pressure oil supply pipe 19' is connected to a high-pressure oil tank (not shown) via a high-pressure oil pump (not shown).

Additionally, a low pressure oil supply pipe 2 is attached to the stern frame 13' at a position between the outer shaft sealing device 16' and the stern side fixed bearing bush (static pressure bearing) 9'.
0' is open and connected. This low pressure oil supply pipe 20' is connected to a lubricating oil tank (not shown).

And the stern side fixed bearing bush (static pressure bearing)
The lubricating oil supplied to the co-bearing bushing 9' and flowing to the stern side after lubricating the co-bearing bushing 9', and the lubricating oil supplied to the sealing device 16' from the low pressure oil supply pipe 20' to the inner shaft sealing device 15'. A stern side outer shaft oil supply hole 21' is formed in the outer shaft 2' in order to guide oil flow to the stern side after lubricating the bearing bush 9' via the bearing bush 10' and the outer shaft sealing device 18'. A bow-side outer shaft oil supply hole 22' is formed in the outer shaft 2' in order to guide the lubricating oil into the hollow shaft 23'.

In addition, the reference numeral 14' in FIG. 7 indicates the rear bulkhead of the engine room, and the reference numeral 17' indicates a stopper for restricting the movement of the floating bush 6' on the bow side.

Furthermore, a discharge system (not shown) for discharging lubricating oil after lubrication is provided on the bow side of the two-split hollow shaft 23'.

Therefore, in the conventional bearing lubrication system for marine counter-rotating propellers as described above, lubricating oil stored in a high-pressure oil tank (not shown) and a lubricating oil tank are pumped out by a pump (not shown), etc. Pipe 19' and low pressure oil supply pipe 2
0' to the stern side fixed bearing bush (static pressure bearing) 9' and the outer shaft sealing device 16' on the outer peripheral surface of the outer shaft 2'.

Of the high-pressure lubricating oil that lubricates the fixed bearing bushing (static pressure bearing) 9', the oil that flows toward the bow along the outer circumferential surface of the outer shaft 2' is transferred to the bow side fixed bearing bushing 10' and the outer circumferential surface of the outer shaft 2'. After the shaft seal device 18' is lubricated, it is guided into the hollow shaft 23' which is split into two parts from the bow side outer shaft oil supply hole 22'.

On the other hand, the high pressure lubricating oil that flows along the outer peripheral surface of the outer shaft 2' toward the stern side joins with the low pressure lubricating oil supplied from the low pressure oil supply pipe 20',
After lubricating the outer shaft seal device 16', the lubricant is led to the inner shaft seal device 15' from the stern outer shaft oil supply hole 21'.

The lubricating oil that has lubricated this sealing device 15' flows toward the bow side between the inner circumferential surface of the outer shaft 2' and the outer circumferential surface of the inner shaft 1', and flows toward the bow side of the inner shaft bearing 24',
After lubricating 24', it flows into the hollow hollow shaft 23'.

The lubricating oil in the two-split hollow shaft 23' flows further toward the bow side along the outer peripheral surface of the inner shaft 1', and is returned to the lubricating oil tank or the high-pressure oil tank from a discharge system (not shown).

[Problem that the invention attempts to solve]

However, in the conventional bearing lubrication system for marine contra-rotating propellers as described above, the inner shaft 1' and the outer shaft 2', which have extremely large structural weights, are moved in opposite directions by the inner shaft bearings 24'. Rotates at high speed.

For this reason, in the inner shaft bearing 24' as a hydrodynamic sliding bearing, an oil film of lubricating oil is not formed on the sliding surface of the inner shaft bearing 24', and the lubrication performance of the inner shaft bearing 24' is deteriorated, causing uneven contact especially during low speed rotation. It becomes a problem. In some cases, the inner shaft 1' and the inner shaft bearing 24' may come into direct contact and cause seizure, so in order to improve uneven contact, the diameter of the inner shaft 1' is set to be larger than the rule diameter. This makes it difficult to arrange the propeller shaft system and is extremely uneconomical.

Therefore, it has been proposed to configure the inner shaft bearing interposed between the inner shaft and the outer shaft as a static pressure bearing to reliably form an oil film and prevent uneven contact. There is.

That is, as shown in FIG. 8 (cross-sectional view of main parts), the outer shaft 32' and the outer shaft bearing 33' are the same as the conventional ones, but the inner shaft 31' is supplied with high pressure oil from a hydraulic source (not shown). A guiding lubricating oil passage 30' is formed, and the lubricating oil passage 30' communicates with a plurality of holes 34' formed radially in the inner shaft 31'.

Small hole screws 35' having an orifice restricting function are tightened into the openings of these holes 34' on the outer periphery of the inner shaft 31'.

In such a hydrostatic bearing, high-pressure lubricating oil is supplied between the inner shaft 31' and the outer shaft 32' from a hydraulic source (not shown) via the lubricating oil passage 30' and the hole 34', and the bearing is The lubrication takes place as it is formed.

By the way, normally, the inner shaft 31' and the outer shaft 32' are
As shown in FIG. 8, there is a high possibility that contact will occur at the lowest part due to deflection, so it is required to reliably supply high-pressure lubricating oil to the vicinity of this lowest part.

Therefore, a plurality of holes 34' are formed radially, and an extremely large amount of lubricating oil is supplied.

However, in this hydrostatic bearing, the inner shaft 31'
Since no means is disclosed for reliably discharging a large amount of lubricating oil supplied between ) may be damaged and other problems may occur.

The present invention attempts to solve the above-mentioned problems by establishing a means for discharging lubricating oil when the inner shaft bearing is configured as a static pressure bearing, and thereby reliably preventing seizure due to uneven contact, etc. An object of the present invention is to provide a bearing lubrication device for a counter-rotating marine propeller, which improves the lubrication performance of a counter-rotating propeller shaft system.

[Means for solving problems]

For this reason, the bearing lubrication device for a counter-rotating marine propeller of the present invention has a bearing lubricating device for a counter-rotating propeller installed at the stern of the ship, which is installed on the tubular outer shaft and on the inner periphery of both ends of the outer shaft. It is equipped with a bow side hydrostatic pressure bearing and a stern side hydrostatic pressure bearing consisting of a bearing bush and a bearing metal provided on the inner circumference of the bearing bush, and an inner shaft supported by these hydrostatic pressure bearings, as well as high-pressure lubrication. a lubricating oil supply system that supplies oil to the inner periphery of the bearing metal via an inner shaft oil supply passage inside the inner shaft and an oil supply hole opening from the passage toward the inside of the bearing metal; On the bow side, the gap between the outer shaft and the inner shaft is closed in order to prevent leakage of the lubricating oil supplied from the oil supply hole on the front end side of the side hydrostatic pressure bearing and the rear end side of the stern side hydrostatic pressure bearing, respectively. Lubrication is provided between the seal mechanism, the stern seal mechanism, the rear end of the bow hydrostatic bearing, and the front end of the stern hydrostatic bearing from these hydrostatic bearings through the gap between the outer shaft and inner shaft. A lubricating oil discharge system including an oil drain hole formed in the pipe wall of the outer shaft is provided to discharge oil, and the lubricating oil discharge system is provided with a lubricating oil discharge system including an oil discharge hole formed in the pipe wall of the outer shaft, and In order to guide the lubricating oil that has leaked toward the bow side seal mechanism and the stern side seal mechanism to the above-mentioned lubricant oil discharge system, a co-bearing bushing is installed in each bearing bush of the above-mentioned bow side hydrostatic pressure bearing and stern side hydrostatic pressure bearing. It is characterized in that a lubricating oil guide path is formed that penetrates from one end to the other end.

[Effect]

In the bearing lubricating device for a counter-rotating marine propeller of the present invention described above, the high-pressure lubricating oil supplied to the inner circumference of the bearing metal by the lubricating oil supply system is supplied from the inside of the bearing metal toward the sealing mechanism. The spilled material is directed to the lubricant discharge system through a lubricant guide path formed in the bearing bush.

〔Example〕

Hereinafter, embodiments of the present invention will be explained with reference to the drawings. Figures 1 to 5 show a bearing lubricating device for a counter-rotating marine propeller as a first embodiment of the present invention, and Figure 1 is a longitudinal cross-sectional view thereof. , Fig. 2 is a longitudinal cross-sectional view showing an enlarged view of the main parts, Fig. 3 is a cross-sectional view of the hydrostatic bearing section, Fig. 4 is a cross-sectional view of the bearing bushing, and Fig. 5 is a cross-sectional view of the bearing bushing. FIG. 6 is a cross-sectional view showing a modified example of the present invention, and FIG. 6 is a vertical cross-sectional view showing a bearing lubricating device for a counter-rotating marine propeller as a second embodiment of the present invention.

As shown in FIG. 1, in a counter-rotating marine propeller to which the device of the first embodiment of the present invention is applied, a tubular outer shaft 2 having a front propeller 4 at its rear end passes through a stern frame 16. is arranged,
It is supported by a bow side outer shaft bearing 13 and a stern side outer shaft bearing 14 interposed between the inner peripheral surface of the stern frame 16 and the outer peripheral surface of the outer shaft 2. Both of these bearings 13 and 14 are configured as normal stern tube bearings.

Further, an inner shaft 1 having a rear propeller 3 at the rear end and having an inner shaft internal oil supply passage 21 passes through the outer shaft 2 and is disposed concentrically with the outer shaft 2, and is arranged at the rear end of the outer shaft 2. It is supported by a stern hydrostatic bearing 15 interposed between the inner circumferential surface of the front end of the outer shaft 2 and the outer circumferential surface of the inner shaft 1. It is supported by a bow-side hydrostatic bearing 12 installed therein.

Hydrostatic bearings 12 and 15 as these inner shaft bearings
As shown in FIGS. 2 to 4, the bearing bush 15c is mounted on the inner periphery of the outer shaft 2, and the bearing metal 1 is provided on the inner periphery of the same bearing bush 15c.
5a.

The inner shaft 1 is connected to a reversing device (not shown), and the outer shaft 2 is also connected to a reversing device (not shown) via an outer shaft joint 6 and a split hollow shaft 5. The shaft 2 is connected to a main engine (not shown) via the reversing device, and is configured to rotate the propellers 3 and 4 in opposite directions.

On the other hand, outer shaft sealing devices 9 and 8 are provided to close the gaps between the stern frame 16 and the outer shaft 2 on the outside and inside the boat, respectively, and the stern side sealing mechanism 10 and A bow side seal mechanism 7 is provided at one end side of the bearing bush 15c of the inner shaft bearings 12 and 15 on the outboard and inboard sides, respectively, so as to close the gap between the outer shaft 2 and the inner shaft 1. The seal mechanisms 7 and 10 prevent relative axial movement of the outer shaft 2, inner shaft 1, and stan frame 16, respectively, and also prevent leakage of lubricating oil from the bearings 12 and 15. .

In the device of the first embodiment of the present invention for lubricating the bearing of the contra-rotating marine propeller shaft system as described above, as shown in FIGS. The in-shaft oil supply passage 21 is connected to the oil supply pipe 20 at its bow end, and
In the vicinity of the inner shaft bearings 12 and 15, a number of oil supply holes 21a are formed radially on the inner shaft 1 and communicate with the inner periphery of the bearing metal 15a, and the oil supply pipes 2
The lubricating oil flowing into the inner shaft oil supply passage 21 from
A lubricating oil supply system is provided so as to pass through the oil supply hole 21a and reach the inner periphery of the bearing metal 15a.

In addition, the outer shaft 2 is provided with an inner shaft bearing 1 in the vicinity between the bow side outer shaft bearing 13 and the outer shaft sealing device 8.
2 and 15), the inside and outside of the outer shaft 2 are connected to each other, and the outer shaft 2
An oil drain hole 22 is formed as a lubricant oil discharge system that can drain lubricant oil from the gap between the inner shaft 1 and the inner shaft 1 .

Furthermore, oil drain pipes 23 and 30 are provided before and after the outer shaft bearing 13, respectively.
30 are connected to the high pressure oil tank 18 and the lubricating oil tank 31 via sight glasses 24, 24, respectively.

The high-pressure oil tank 18 is connected to the oil supply pipe 20 via the high-pressure oil pump 19, and supplies lubricating oil to the inner shaft oil supply passage 21 in the lubricating oil supply system.

On the other hand, the outer shaft sealing device 9 and the stern outer shaft bearing 1
4, an oil supply pipe 34 is connected to supply lubricating oil to the inner circumferential surface of the seal device 9 and the outer shaft bearing 14, and this oil supply pipe 34 supplies lubrication through a lubricant pump 33. It is connected to the oil tank 31.

The high-pressure oil tank 18 is provided with an overflow pipe 32, and when the lubricating oil in the high-pressure oil tank 18 exceeds a predetermined amount, it is discharged from the overflow pipe 32 into the lubricating oil tank 31. .

By the way, as shown in FIGS. 3 and 4, on the outer periphery of the bearing bush 15c of the inner shaft bearings 12 and 15, water flows from the inside of the bearing metal 15a toward the bow side seal mechanism 7 or the stern side seal mechanism 10. Oil drain hole 2 serves as a lubricating oil discharge system for discharging the lubricating oil.
In order to guide the lubricating oil to the second side, a plurality of oil drain grooves 15b are formed as lubricating oil guide paths.

These oil drain grooves 15b are connected to the bearing bush 15c.
is formed in the axial direction of the bearing bush 15c so as to have a contact area large enough to withstand press-fitting into the outer shaft 2, and a passage area large enough to sufficiently drain lubricating oil.

Note that the lubricating oil guide path is as shown in Fig. 5.
It may also be formed as an oil drain hole 15d in the wall of the bearing bush 15c.

In addition, the code 11 in FIG. 1 is a rope guard, 1
7 indicates the rear bulkhead of the engine room, and 29 indicates an air vent pipe.

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, the lubricating oil stored in the high-pressure oil tank 18 is pressurized by the high-pressure oil pump 19 and sent out. The oil is then fed to the oil supply pipe 20.

In this way, the high-pressure lubricating oil supplied to the oil supply pipe 20 flows through the inner shaft internal oil supply passage 21 of the inner shaft 1 from the bow to the stern, and flows through the numerous oil supply holes 21.
Bearing metal 15a of inner shaft bearings 12 and 15 from a
and lubricates these bearings 12 and 15.

Then, the bearing metal 15 of the inner shaft bearings 12 and 15
After lubricating these inner shaft bearings 12 and 15, the high-pressure lubricating oil supplied to the inner circumference of the shaft a flows out toward the bow side seal mechanism 7 and the stern side seal mechanism 10 at one end side of each bearing bush 15c. There are two types: one that flows out to the other end of the bearing bush 15c, and one that flows out to the other end of the bearing bush 15c.

Here, the lubricating oil that has flowed out to the other end side of the latter bearing bush 15c passes through the gap between the outer shaft 2 and the inner shaft 1 and from the oil drain hole 22 formed in the outer shaft 2 to the outside of the outer shaft 2. is discharged to.

Further, the lubricating oil that has leaked into the former seal mechanisms 7 and 10 lubricates the same seal mechanisms 7 and 10, and then flows into the oil drain groove 1 formed on the outer periphery of the bearing bush 15c.
5b to the other end of the bearing bush 15c, this lubricating oil is also discharged from the oil drain hole 22 to the outside of the outer shaft 2 together with the latter lubricating oil.

Note that oil is drained from one end of the bearing bush 15c to the other due to the pressure difference between both sides (approximately 0.2 to 0.3 Kg/cm ² ), so the amount of lubricating oil to be drained and the inner shaft bearings 12, 15 are Based on the dimensions of the oil drain groove 15
The shape and number of the oil drain holes b (or the oil drain holes 15d) are determined.

The lubricating oil discharged to the outside of the outer shaft 2 from the gap between the outer shaft 2 and the inner shaft 1 as described above lubricates the outer shaft sealing device 8 and the outer shaft bearing 13, and then flows to high pressure through the oil drain pipe 23. The oil is discharged to the oil tank 18.

On the other hand, the lubricating oil stored in the lubricating oil tank 31 is pressurized by the lubricating oil pump 33 and
4, and is supplied from this oil supply pipe 34 to the outer shaft sealing device 9 and the stern outer shaft bearing 14.

The lubricating oil that lubricates the seal device 9 and the outer shaft bearing 14 flows toward the bow side along the outer peripheral surface of the outer shaft 2 and lubricates the bow side outer shaft bearing 13, and then
The oil is discharged from the oil drain pipe 30 to the lubricating oil tank 31 .

As described above, according to the bearing lubrication device for marine contra-rotating propellers as the first embodiment of the present invention, high-pressure lubricating oil can be reliably discharged, so that hydrostatic bearings can be used as the inner shaft bearings 12 and 15. can be adopted without causing damage to the seal mechanisms 7 and 10, and an oil film is always formed on the inner shaft bearings 12 and 15 regardless of the one-sided contact angle or bearing load (even during low speed rotation). becomes possible.

Therefore, it is possible to reliably prevent seizure due to uneven contact, etc., which has conventionally been a problem when a dynamic pressure type bearing is adopted, and the lubrication performance of the shaft system of the counter-rotating propeller is improved.

In addition, since the shaft diameter of the inner shaft 1 can be kept below the rule diameter, the entire counter-rotating propeller shaft system can be
It can be easily constructed at low cost and compactly, and can also contribute to improving propeller performance.

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. 6, this second embodiment has almost the same structure as the first embodiment, but in the second embodiment, a hydrostatic bearing is used as the stern outer shaft bearing 14'. , a lubricating oil tank 31 and a lubricating oil pump 3 provided for supplying lubricating oil to the stern outer shaft bearing (stern tube bearing) 14 in the first embodiment.
3. The oil supply pipe 34 and the like have been removed, as well as the oil drain pipe 30.

At the center of the stern side outer shaft bearing (static pressure bearing) 14', the inner circumferential surface of the outer shaft bearing 14' and the outer shaft 2
An oil supply pipe 26 is connected to supply high-pressure lubricating oil between the outer peripheral surface of the oil supply pipe 26 and
is connected to the high pressure oil tank 18 via an orifice 25 and a high pressure oil pump 19.

Further, an oil drain pipe 27 is formed in the stern frame 16 with an opening at a position between the outer shaft sealing device 9 and the stern outer shaft bearing (static pressure bearing) 14'. flows through a flowmeter 28 and a sight glass 24 into an oil drain pipe 23 and is connected to a high pressure oil tank 18.

With the above-mentioned configuration, in the second embodiment, lubrication of the inner shaft bearings 12 and 15 is performed in exactly the same manner as in the first embodiment, while the high-pressure oil tank 1
8 is pressurized by a high-pressure oil pump 19 and fed into the oil supply pipe 2
A part of the high pressure lubricating oil fed to the outer shaft bearing (hydrostatic bearing) 14' is lubricated and then discharged.
The high-pressure lubricating oil flows along the outer peripheral surface of the outer shaft 2 toward the bow side, lubricates the bow-side outer shaft bearing 13, and is then discharged from the oil drain pipe 23 to the high-pressure oil tank 18. The high-pressure lubricating oil that flows along the outer peripheral surface of the outer shaft 2 toward the stern side lubricates the outer shaft seal device 9, and then
The oil is discharged from the oil drain pipe 27 to the high-pressure oil tank 18 .

In this way, the second embodiment of the present invention can provide 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 an inner wall at both ends of the outer shaft are provided. A bow side hydrostatic pressure bearing and a stern side hydrostatic pressure bearing, each consisting of a bearing bush attached to the periphery and a bearing metal provided on the inner periphery of the same bearing bush, and an inner shaft supported by these hydrostatic pressure bearings. At the same time, high-pressure lubricating oil is supplied to the inner periphery of the bearing metal via an inner shaft oil supply passage inside the inner shaft and an oil supply hole opening from the same passage toward the inside of the bearing metal. The supply system is connected to the outer shaft and the inner shaft to prevent leakage of the lubricating oil supplied from the oil supply hole at the front end of the bow hydrostatic bearing and the rear end of the stern hydrostatic bearing, respectively. A bow side seal mechanism and a stern side seal mechanism that close the gap, and a rear end side of the bow side hydrostatic pressure bearing and a front end side of the above stern side hydrostatic pressure bearing are connected to the outer shaft and the inner shaft from these hydrostatic pressure bearings. and a lubricating oil discharge system including an oil drain hole formed in the tube wall of the outer shaft to discharge the lubricating oil that has passed through the gap between the bow side hydrostatic bearing and the stern side hydrostatic bearing. In order to guide the lubricating oil flowing out from the inside of the bearing metal toward the bow side seal mechanism and the stern side seal mechanism, respectively, to the above lubricant oil discharge system,
A simple structure in which a lubricating oil guide path is formed in each bearing bush of the above-mentioned bow side hydrostatic bearing and stern side hydrostatic bearing from one end of the bearing bush to the other, allowing high pressure lubricating oil to be removed. Since the air can be reliably discharged from the gap between the shaft and the inner shaft, static pressure bearings can be used without damaging the seal mechanism.
Seizure caused by uneven contact is prevented, and the lubrication performance of the counter-rotating propeller shaft system is greatly improved. In addition, by using hydrostatic bearings, the diameter of the inner shaft can be kept below the rule diameter, making it possible to construct the entire contra-rotating propeller shaft system easily, at low cost, and compactly, resulting in improved propeller performance. There is also the advantage of significantly improving

[Brief explanation of the drawing]

1 to 5 show a bearing lubricating device for a contra-rotating marine propeller as a first embodiment of the present invention.
Figure 1 is a vertical cross-sectional view of the same, Figure 2 is a vertical cross-sectional view showing an enlarged view of the main parts, Figure 3 is a cross-sectional view of the hydrostatic bearing section, and Figure 4 is a cross-sectional view of the bearing bushing. ,
FIG. 5 is a cross-sectional view showing a modified example of the bearing bushing, FIG. 6 is a longitudinal cross-sectional view showing a bearing lubricating device for a counter-rotating marine propeller as a second embodiment of the present invention, and FIG. The figure is a longitudinal cross-sectional view showing a conventional bearing lubrication system for marine counter-rotating propellers using hydrodynamic sliding bearings, and Figure 8 shows the main parts of a conventional bearing lubrication system for marine contra-rotating propellers using hydrostatic pressure bearings. FIG. 1... Inner shaft, 2... Outer shaft, 3... Rear propeller, 4... Front propeller, 5... Hollow shaft split in two, 6... Outer shaft joint, 7... Bow side seal mechanism,
8, 9... Seal device for outer shaft, 10... Stern side seal mechanism, 11... Rope guard, 12... Bow side static pressure bearing, 13... Bow side outer shaft bearing (stern tube bearing), 14... ...Stern side outer shaft bearing (stern tube bearing), 1
4'...Stern side outer shaft bearing (static pressure bearing), 15...Stern side static pressure bearing, 15a...Bearing metal, 15b...
...Oil drain groove as a lubricating oil guide path, 15c... Bearing bush, 15d... Oil drain hole as a lubricating oil guide path, 16... Stan frame, 17... Rear bulkhead of engine room, 18... High pressure oil Tank, 19... High pressure oil pump, 20... Oil supply pipe, 21... Oil supply passage in the inner shaft, 21a... Oil supply hole, 22... Oil drain hole as a lubricating oil discharge system, 23... Oil drain pipe, 24 ... Sight glass, 25 ... Orifice, 26 ... Oil supply pipe, 27 ... Oil drain pipe, 28 ... Flowmeter, 29 ...
Air vent pipe, 30... oil drain pipe, 31... lubricating oil tank, 32... overflow pipe, 33... lubricating oil pump, 34... oil supply pipe.

Claims (1)

[Scope of utility model registration request] In the contra-rotating propeller shaft system installed at the stern, the shaft is made up of a tubular outer shaft, bearing bushes attached to the inner periphery of both ends of the outer shaft, and bearing metal provided on the inner periphery of the same bearing bushes. It is equipped with a bow side hydrostatic pressure bearing and a stern side hydrostatic pressure bearing, and an inner shaft supported by these hydrostatic pressure bearings.
A lubricating oil supply system that supplies high-pressure lubricating oil to the inner periphery of the bearing metal via an inner shaft oil supply passage inside the inner shaft and an oil supply hole opening from the same passage toward the inside of the bearing metal. , close the gap between the outer shaft and the inner shaft to prevent leakage of the lubricating oil supplied from the oil supply hole at the front end of the bow hydrostatic bearing and the rear end of the stern hydrostatic bearing, respectively. a bow side seal mechanism and a stern side seal mechanism,
In order to drain the lubricating oil that has passed through the gap between the outer shaft and the inner shaft from the hydrostatic bearings at the rear end of the bow hydrostatic bearing and the front end of the stern hydrostatic bearing, The bow side seal mechanism and the stern side seal are installed from the inside of each bearing metal of the bow side hydrostatic bearing and the stern side hydrostatic bearing, respectively. In order to guide the lubricating oil that has flowed out toward the mechanism to the lubricating oil discharge system, a lubricant is installed in each of the bearing bushes of the bow side hydrostatic bearing and the stern side hydrostatic bearing, which penetrates from one end of the bearing bush to the other end. A bearing lubricating device for a counter-rotating marine propeller, characterized in that an oil guide path is formed.