JPS62265098A - Bearing lubricating device for marine contrarotating propeller - Google Patents

Abstract

PURPOSE:To feed oil at the time of emergency and aim at preventing seizure or binding in a bearing from occurring, by installing a branch pipe in a high pressure feed oil pipe ranging from a discharge port of a lubricating pump to the hydrostatic bearing, and feeding the branch pipe with high pressure oil by an accumulator at the time of emergency such like power failure or the like. CONSTITUTION:High pressure discharge oil out of a lubricating oil pump 23 passes through a high pressure feed oil pipe 25, lubricating each bearing from a lubricating oil passage 18 and then it is put back to a lubricating oil tank 22 through a drain oil pipe 21. Branching off from this high pressure feed oil pipe 25, there is provided with an emergency feed oil pipe 26 which is connected to an accumulator 27, and a proper quantity of oil is stored against gas pressure inside a bladder 27a of the accumulator 27. When operation of the high pressure oil pump 23 is stopped by power failure or the like, lubricating oil is sent back to the high pressure feed oil pipe 25 with gas pressure out of the accumulator 27, and feed of lubricating oil to each bearing is continued in succession. Capacity of this accumulator 27 should be set to a feedable size during an interval of up to being selected to an emergency power source. Therefore, the feed of lubricating oil is still continued so that seizure or binding in the bearing is prevented from occurring.

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, in normal single-shaft ships, when oil lubrication by sliding bearings cannot be achieved, especially when the propeller weight is large and the bearing surface pressure is extremely high, or the propeller shaft rotates at low speed, etc., static Pressure bearings are used.

That is, a propeller shaft 1'' with a propeller 5' attached to its rear end is disposed so as to pass through the stern frame 6' and is supported by a bearing bushing 2' press-fitted into the stern frame 6'. A bearing metal (mainly white F metal) 3' is provided on the inner periphery of this bearing bush 2', and a pocket 8' is formed at the lowest end of the inner circumferential surface. A hydrostatic bearing is constructed by supplying high-pressure lubricating oil from a high-pressure oil pump (not shown) to ' through an oil supply pipe 7'.

The propeller shaft 1' is connected to a propulsion motor (not shown) and rotationally driven by the motor.

Further, the reference numeral 4° in the figure indicates a sealing device.

According to such a static pressure bearing, the propeller shaft 1' is bent by the weight of the propeller 5', and a pocket () (
High-pressure lubricating oil is supplied from the propeller shaft 1', which forces the propeller shaft 1' to levitate and lubricate it, thereby preventing problems such as uneven contact. .

Hydrostatic bearings as described above have conventionally been applied to marine counter-rotating propeller shaft systems. This is to create a counter-rotating bearing between the inner and outer rings that rotate at a constant speed, where oil film is not likely to form in principle, even in extremely low-speed one-sided contact42)
In the n-inverted propeller shaft system, as shown in Figure 3,
A tubular outer ring 12' supported by an outer ring bearing 16' and an inner ring 11' supported within the outer ring 12' are provided, and the inner ring 11' and outer ring 12' are driven to rotate in opposite directions. Ru. In such a counter-rotating propeller shaft system, a lubricating oil passage 13° is formed in the inner ring 11' to guide high-pressure lubricating oil from a hydraulic source (not shown), and the lubricating oil passage 13' is radially connected to the inner ring 11'. A plurality of holes 14 formed in
The inner ring 11 of these holes 14'
A hydrostatic bearing is constructed by tightening a small hole screw 15 having an orifice restricting function into the opening on the outer periphery. Here, in FIG. 3, the bearing metal and bearing bushing that constitute a part of the hydrostatic bearing are omitted from illustration.

In this type of hydrostatic bearing, high-pressure lubricating oil is supplied between the inner ring 11' and the outer ring 12' from a hydraulic power source (not shown) through the lubricating oil passage 13'' and the hole 14' to form the bearing. At the same time, lubrication is performed.

Normally, the inner sleeve 11' and the outer ring 12' are likely to come into contact at the lowest part due to deflection, as shown in Figure 3, so high-pressure lubricating oil must be reliably supplied to the vicinity of this lowest part. This is required. Therefore, a plurality of holes 14' are formed radially, and an extremely large amount of lubricating oil is supplied.

[Problem that the invention seeks to solve]

However, in the conventional bearing lubrication system for marine counter-rotating propellers as described in 14, the inner ring 11 is
Since the 1 unit is forcibly floated, if the supply of high pressure oil is stopped even for a short time, the inner ring 11 and the outer ring 12' will burn. This is generally done by a high-pressure oil pump driven by an electric motor, and if the regular and auxiliary generators on a ship stop at the same time for some reason, the ship's power supply will be lost and the high-pressure oil pump will also stop as a result. Therefore, even in the short time it takes to activate the emergency generator, the bearings may seize, making navigation impossible.

The present invention aims to solve these problems by activating the emergency generator after the ship's power is lost and temporarily supplying high-pressure oil until the ship's power is restored (usually for about 1 minute). To ensure that the bearing does not seize, ensure that it ends with the supply.
The purpose of the present invention is to provide a bearing lubrication device for marine propellers that secures the safety of coaxial bearings.

[Means for solving problems]

For this reason, the bearing lubricating device for a counter-rotating marine propeller of the present invention is provided on an inner ring, a bearing bushing arranged on the outer periphery of the inner ring, and a co-bearing bushing in a counter-rotating propeller shaft system installed at the stern of the ship. The hydrostatic bearing is comprised of a hydrostatic bearing made of bearing metal, and a tubular outer ring disposed around the outer periphery of the hydrostatic bearing, and high-pressure lubricating oil is supplied to the hydrostatic bearing via the inside of the inner ring. The lubricating oil supply system includes a lubricating oil pump that discharges high-pressure lubricating oil, and a high-pressure oil supply pipe that runs from the discharge port of the lubricating oil pump to the hydrostatic bearing. It is characterized by being constructed with an accumulator that is connected to an emergency oil supply pipe branching from a high-pressure oil supply pipe and capable of discharging high-pressure lubricating oil.

[For production]

In the bearing lubrication system for a counter-rotating marine propeller of the present invention described above, high-pressure lubricating oil is discharged from the accumulator from the time the ship's power is lost until the emergency generator is activated, and this lubricating oil is used for emergency purposes. It is supplied to the hydrostatic bearing via the oil supply pipe and high pressure oil supply pipe.

〔Example〕

Hereinafter, a bearing lubricating device for a counter-rotating marine propeller as an embodiment of the present invention will be explained with reference to the drawings. In a marine counter-rotating propeller to which IF is applied, a tubular outer ring 2 with a face-side propeller 4 at the rear end is used.
is disposed through the stern frame 16 and is supported by a bow outer ring bearing 12 and a stern outer ring bearing 13 interposed between the inner peripheral surface of the stern frame 16 and the outer peripheral surface of the outer ring 2. There is. Both of these bearings 12 and 13 are constructed as ordinary stern tube bearings.

Further, an inner ring 1 having a rear propeller 3 at the rear end and having an inner sleeve self-lubricating passage 18 passes through the outer ring 2 and is arranged concentrically with the outer ring 2, and is connected to the inner circumferential surface of the rear end of the outer ring 2. A stern inner ring bearing 11 is supported by a stern inner ring bearing 14 interposed between the outer peripheral surface of the inner ring 1 and a bow inner ring bearing 11 interposed between the front end inner peripheral surface of the outer ring 2 and the outer peripheral surface of the inner ring 1. Supported by

Each of these inner sleeve bearings 11, 14 is a hydrostatic bearing consisting of bearing bushes lla, 14a mounted on the outer periphery of the inner sleeve 1, and a bearing metal (not shown) provided on the outer periphery of each bearing bush 11a, 14a. Constructed as.

The inner ring 1 is connected to a reversing device (not shown), and the outer ring 2 is also connected to a reversing device (not shown) via an outer ring joint 10 and a split hollow shaft 9. It is connected to a main engine (not shown) via the reversing device, so that the propellers 3 and 4 can be rotated in opposite directions.

The outer ring sealing devices 6 and 7 are provided to close the gap between the stern frame 16 and the outer ring 2 on the outside and inside the ship, respectively, and the inner sleeve sealing devices 5 and 8 are installed on the outside and inside the ship, respectively. Each bearing bushing 14a, ll of the inner ring bearings 14 and 11 in
These sealing devices 5, 8 are provided to close the outer space between the outer ring 2 and the inner ring 1 at one end side of the outer ring 2.a. In addition to preventing relative axial movement of the inner ring 1 and the stan frame 16, it also prevents leakage of lubricating oil from the bearings 11 to 14.

In the device of this embodiment for lubricating the bearings of the marine contra-rotating propeller shaft system as described above, as shown in FIG.
At its bow end, it is connected to a high-pressure oil supply pipe 25 via a rotary ring (not shown), and in the vicinity of the inner ring bearing 11.14, the inner ring 1 is connected to the bearing bush 11.
A, 14a are connected to oil supply holes 19 which are formed radially in large numbers and communicate with the outer periphery of a bearing metal (not shown).

Further, the high-pressure oil supply pipe 25 is connected to a discharge port of a high-pressure oil pump 23 serving as a lubricating oil pump that discharges high-pressure lubricating oil from the lubricating oil tank 22, and the high-pressure lubricating oil from the high-pressure oil pump 23 is The inner sleeve bearing 11 as a static pressure bearing passes through the oil supply pipe 25, the inner ring self-oil supply passage 18, and the oil supply hole 19.
It is designed to reach 14.

Furthermore, in this embodiment, an emergency oil supply branching from the high pressure oil supply pipe 25! An accumulator 27 is connected to 26. This accumulator 27 stores lubricating oil at a required pressure so that high-pressure lubricating oil can be discharged in an emergency.During normal operation of the high-pressure oil pump 23, lubricating oil flows into the accumulator 27. An appropriate amount of gas is always stored against the gas pressure inside the plug 27a.

In this embodiment, the above-mentioned lubricating oil pump 23. High pressure oil supply pipe 25. Inner ring self-lubricating passage 18. A lubricating oil supply system is comprised of the oil supply hole 19°, the emergency oil supply pipe 26, the accumulator 27, and the like.

In addition, in the outer ring 2, in the vicinity between the bow side outer ring bearing 12 and the outer ring seal M7 (that is, on the other end side of each bearing bush lla and 14a of the inner ring bearings 11 and 14), there are inner and outer parts of the outer ring 2. In addition, an oil drain hole 20 is formed between the outer ring 2 and the inner ring 1 to allow lubricating oil to be discharged from the gap between the outer ring 2 and the inner ring 1. An oil drain pipe 21 is provided for discharging lubricating oil from a gap with the frame 16, and this oil drain pipe 21 is connected to a lubricating oil tank 22.

In addition, the bearing bundle 11a in the inner ring bearing 11.14
, 14a are provided with a plurality of oil drain grooves 11b and 14b, respectively, in order to guide the lubricating oil flowing out from the outside of the bearing metal toward the inner sleeve seal device 8 or 5 to the oil drain hole 20 side. It is formed.

In FIG. 1, reference numeral 15 indicates a rope guard, 17 indicates a rear bulkhead of the engine room, and 24 indicates a sod valve.

Since the bearing lubricating device for a marine counter-rotating propeller as an embodiment of the present invention is configured as described above, during normal operation of the high-pressure oil pump 23, the lubricating oil stored in the lubricating oil tank 22 is It is pressurized by the pump 23 and sent out from the high pressure oil supply pipe 25 to the inner ring self-lubricating passage 1 of the inner ring 1.
8. Outside of this, the lubricating oil is in the emergency oil supply pipe 2.
6 to the Achiemulator 27, and the appropriate Ii &? ff can be obtained.

In this way, the high-pressure lubricating oil supplied to the oil supply passage 18 flows from the bow to the stern within the oil supply passage 18, and flows from the numerous oil supply holes 19 to the bearing bushings of the inner ring bearings 11 and 14. , 14a and lubricates these inner ring bearings 11, 14.

and the bearing bush 11a of the inner sleeve bearing 11.14.

After lubricating these inner sleeve bearings 11.14, the high-pressure lubricating oil supplied to the outer circumference of each bearing bush 11a
, 14a, which flow toward the inner ring sealing device 8°5 at one end side, and the bearing bushing 11a.

It is divided into one that flows out to the other end side of 14a.

Here, the lubricating oil that has flowed out to the other end side of the latter bearing bushes 11a and 14a passes through the gap between the outer ring 2 and the inner ring 1, and is discharged to the outside of the outer ring 2 from the oil drain hole 20 formed in the outer ring 2. be done.

In addition, the lubricating oil that has leaked into the former sealing devices 5 and 8 lubricates the same sealing devices 5 and 8, and then lubricates the bearing bushings lla and
An oil drain groove 11b is formed on the inner circumference of the oil drain groove 14a.

Since the lubricating oil is guided to the other end side of the bearing bushes lla and 14a through the lubricating oil 14b, this lubricating oil is also discharged from the oil drain hole 20 to the outside of the outer ring 2 together with the latter lubricating oil.

As described above, remove the outer ring 2 from the gap between the outer ring 2 and the inner ring 1.
The lubricating oil discharged to the outside lubricates the outer ring sealing device 7 and the outer ring bearing 12, and then is discharged to the lubricating oil tank 22 through the oil drain pipe 21.

On the other hand, in the event that the onboard power supply is lost and the high-pressure oil pump 23 is stopped, high-pressure lubricating oil will be discharged from the accumulator 27 from the time the power is lost until the emergency generator is activated and the high-pressure oil pump 23 is restarted. , emergency oil supply pipe 26. High pressure oil supply W25. The oil is supplied to the inner ring bearings 11 and 14 as hydrostatic bearings through the oil supply passage 18 in the inner sleeve and the oil supply hole 19, respectively.

That is, when the supply of lubricating oil from the high-pressure oil pump 23 to the accumulator 27 is interrupted, the plug 27a in the accumulator 27 expands due to the gas inside it, and the lubricating oil with the required pressure is delivered to the accumulator 27. The waste is completely discharged.

Here, the capacity of the accumulator 27 is the amount of lubricating oil required until the emergency generator is activated, the onboard power supply is restored, and the high-pressure oil pump 23 is restarted to supply high-pressure oil. Nippon Kaiji Kyokai rules require that the emergency generator restore the ship's power within 45 seconds, so it would take about one minute.

Of course, this time can be set longer by increasing the capacity of the accumulator 27.

As described above, according to the bearing lubrication device for a marine counter-rotating propeller of this embodiment, the emergency generator is activated after the ship's power is lost until the ship's power is restored (the high-pressure oil pump 23 is restarted). Since high pressure oil is supplied from the accumulator 27 to the inner ring bearings 11.14 as static pressure bearings, seizing of these inner sleeve bearings 11.14 is reliably prevented and safety and reliability as a static pressure bearing are maintained. This greatly improves performance.

Furthermore, since the high-pressure lubricating oil between the inner ring 1 and the outer ring 2 is reliably discharged, the inner ring bearing 11.
14, a static pressure bearing can now be used without causing damage to the sealing device 5.8, and the inner sleeve bearing 11.14 always (even during low speed rotation) regardless of the one-sided contact angle or bearing load. It becomes possible to form an oil film.

Therefore, seizure due to uneven contact, etc. can be reliably prevented, and the lubrication performance in the shaft system of the counter-rotating propeller is improved. In addition, there is no need to increase the shaft diameter of the inner ring 1 in order to improve uneven contact, and the shaft diameter can be kept below the rule diameter, so the entire counter-rotating propeller shaft system can be easily and With its low cost and compact configuration, it can also contribute to improving propeller performance.

In this embodiment, a hydrostatic bearing is used in which the bearing bushes lla, 14a are mounted on the outer periphery of the inner ring 1 and lubricating oil is supplied to the outer periphery of the bearing bushes lla, ], 4a. The present device is similarly applied to a hydrostatic bearing in which a bushing is attached to the inner periphery of the outer ring 2 and lubricating oil is supplied to the inner periphery of the bearing bushing.

〔Effect of the invention〕

As detailed above, in the bearing lubrication device H for a marine contra-rotating propeller of the present invention, in the contra-rotating propeller shaft system provided at the stern, the bearing lubrication device H is arranged on the inner sleeve and on the outer periphery of the inner ring. The hydrostatic pressure bearing consists of a bearing bushing and a bearing metal provided on the bearing bushing, and a tubular outer ring disposed around the outer periphery of the hydrostatic bearing. The lubricating oil supply system includes a lubricating oil pump that discharges high-pressure lubricating oil, and a lubricating oil supply system that supplies high-pressure lubricating oil to the hydrostatic bearing from the discharge port of the lubricating oil pump. In addition to being equipped with a high-pressure oil supply pipe leading to
It has a simple structure consisting of an accumulator that is connected to an emergency oil supply pipe that branches from the same high-pressure oil supply pipe and can discharge high-pressure lubricating oil, so even if the ship's power supply is lost, the Until the emergency generator starts up and the ship's power is restored, high-pressure oil is supplied from the accumulator to the hydrostatic bearings, which reliably prevents seizure of the hydrostatic bearings and ensures that the hydrostatic bearings are fully powered. It can be safely and reliably used in counter-rotating propeller shaft systems.

In addition, by using hydrostatic bearings, the inner ring shaft diameter can be kept below the rule diameter, making it possible to configure the entire counter-rotating propeller shaft system compactly and at low cost, improving propeller performance. There are also significant advantages.

[Brief explanation of drawings]

FIG. 1 is a schematic vertical sectional view showing a bearing lubricating device for a contra-rotating marine propeller as an embodiment of the present invention, and FIG.
The figure is a longitudinal cross-sectional view showing a hydrostatic bearing in a normal single-shaft ship, and the tjSs figure is a cross-sectional view showing a main part of a conventional bearing lubricating device for a marine counter-rotating propeller using a hydrostatic bearing. 1. Inner ring, 2. Outer ring, 3. Rear propeller, 4.
Front propeller, 5. Seal device for inner ring, 6.7. Seal device for outer ring, 8. Seal device for inner ring, 9. Hollow shaft split in two, 10. Outer ring joint, 11. Inner ring on bow side. Bearing (static pressure bearing), lla... Bearing bushing, 1111...
・Drain groove, 12... Bow side outer ring bearing (stern tube bearing), 1
3... Stern side outer ring bearing (stern tube bearing), 14... Stern side inner ring bearing (static pressure bearing), 14a... Bearing pusher l, 14
b... Oil drain groove, 15... Rope guard, 16... Stun frame, 17... Rear bulkhead of engine room, 18... Oil supply passage in inner ring, 19... Oil supply hole, 20... Oil drain hole, 21・・・
Oil drain pipe, 22...Lubricating oil tank, 23...High pressure oil pump as a lubricating oil pump, 24...Check valve, 25...High pressure oil supply pipe, 26...Emergency oil supply pipe, 27...Accumulator, 27a ...bladder. Sub-Agent Patent Attorney Yoshihiko Iinuma Figure 2 Figure 3

Claims (1)

[Claims] In a counter-rotating propeller shaft system installed at the stern, a hydrostatic bearing includes an inner ring, a bearing bush provided on the outer periphery of the inner ring, and a bearing metal provided on the bearing bush;
A tubular outer ring disposed around the outer circumference of the hydrostatic bearing, and a lubricating oil supply system that supplies high-pressure lubricating oil to the hydrostatic bearing via the inside of the inner ring. The system includes a lubricating oil pump that discharges high-pressure lubricating oil, a high-pressure oil supply pipe that runs from the discharge port of the lubricating oil pump to the above-mentioned static pressure bearing, and is connected to an emergency oil supply pipe that branches from the high-pressure oil supply pipe. 1. A bearing lubricating device for a counter-rotating marine propeller, comprising an accumulator capable of discharging high-pressure lubricating oil.