WO2009087832A1 - 二重反転プロペラ式舶用推進装置 - Google Patents
二重反転プロペラ式舶用推進装置 Download PDFInfo
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- WO2009087832A1 WO2009087832A1 PCT/JP2008/071643 JP2008071643W WO2009087832A1 WO 2009087832 A1 WO2009087832 A1 WO 2009087832A1 JP 2008071643 W JP2008071643 W JP 2008071643W WO 2009087832 A1 WO2009087832 A1 WO 2009087832A1
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- shaft
- rotating
- lubricating oil
- outer shaft
- counter
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/162—Special parts or details relating to lubrication or cooling of the sealing itself
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/38—Apparatus or methods specially adapted for use on marine vessels, for handling power plant or unit liquids, e.g. lubricants, coolants, fuels or the like
- B63H21/386—Apparatus or methods specially adapted for use on marine vessels, for handling power plant or unit liquids, e.g. lubricants, coolants, fuels or the like for handling lubrication liquids
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/02—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing
- B63H23/10—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/02—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing
- B63H23/10—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit
- B63H23/12—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit allowing combined use of the propulsion power units
- B63H23/16—Transmitting power from propulsion power plant to propulsive elements with mechanical gearing for transmitting drive from more than one propulsion power unit allowing combined use of the propulsion power units characterised by provision of reverse drive
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H5/00—Arrangements on vessels of propulsion elements directly acting on water
- B63H5/07—Arrangements on vessels of propulsion elements directly acting on water of propellers
- B63H5/08—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller
- B63H5/10—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller of coaxial type, e.g. of counter-rotative type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H5/00—Arrangements on vessels of propulsion elements directly acting on water
- B63H5/07—Arrangements on vessels of propulsion elements directly acting on water of propellers
- B63H5/08—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller
- B63H5/10—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller of coaxial type, e.g. of counter-rotative type
- B63H2005/106—Arrangements on vessels of propulsion elements directly acting on water of propellers of more than one propeller of coaxial type, e.g. of counter-rotative type with drive shafts of second or further propellers co-axially passing through hub of first propeller, e.g. counter-rotating tandem propellers with co-axial drive shafts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/321—Bearings or seals specially adapted for propeller shafts
- B63H2023/323—Bearings for coaxial propeller shafts, e.g. for driving propellers of the counter-rotative type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/321—Bearings or seals specially adapted for propeller shafts
- B63H2023/325—Thrust bearings, i.e. axial bearings for propeller shafts
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts
- B63H2023/342—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts comprising couplings, e.g. resilient couplings; Couplings therefor
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/34—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts
- B63H2023/346—Propeller shafts; Paddle-wheel shafts; Attachment of propellers on shafts comprising hollow shaft members
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H23/00—Transmitting power from propulsion power plant to propulsive elements
- B63H23/32—Other parts
- B63H23/321—Bearings or seals specially adapted for propeller shafts
Definitions
- the present invention relates to a counter-rotating propeller marine propulsion device.
- a counter-rotating propeller is a propeller that achieves high propeller efficiency by recovering rotational energy flowing out from the front propeller to a propulsion force after being recovered by the propeller that rotates in the opposite direction to the front propeller.
- a marine propulsion device equipped with a counter-rotating propeller is referred to as a “counter-rotating propeller marine propulsion device”.
- a contra-rotating propeller marine propulsion device is disclosed, for example, in Patent Document 1 below.
- FIG. 1 As a conventional example of a counter-rotating propeller marine propulsion device, a “counter-rotating propeller device” disclosed in Patent Document 1 is shown in FIG.
- a rear propeller 101 is attached to a rear end portion of an inner shaft 102 connected to a main engine (not shown).
- the front propeller 103 is attached to a rear end portion of an outer shaft 104 connected to a reversing gear (not shown), and the front propeller 101 and the rear propeller 103 are driven to reverse each other.
- the weight of the inner shaft 102 is supported by a front inner bearing 105 mounted on the inner surface of the outer shaft 104 and a rear inner bearing 106 mounted in the boss of the rear propeller 101.
- the weight applied to the outer shaft 104 is the hull 113.
- the front and rear inner shaft seal devices 109 and 110 and the front and rear outer shaft seal devices 111 and 112 are provided. Is provided.
- the seal part of the front inner shaft sealing device (hereinafter referred to as the counter rotating front sealing device) generates heat by rotational sliding.
- the rear side (stern side) of the counter-rotating front seal device is wet due to the counter-rotating lubricant, but the front side (bow side) is in a dry state and is very hot. For this reason, wear of the counter-rotating front seal device is severe, which is a factor that shortens the life of the counter-rotating front seal device.
- the present invention has been made in view of the above problems, and can reduce the heat generated on the front side of the counter-rotating front seal device, thereby extending the life of the counter-rotating front seal device. It is an object of the present invention to provide a lubrication system for a counter-rotating seal.
- the contra-rotating propeller marine propulsion device of the present invention employs the following technical means.
- the present invention has a hollow outer shaft attached to the hull with a front propeller attached to the rear end, and a rear propeller attached to the rear end to be supported rotatably inside the outer shaft.
- a counter-rotating front bearing provided between the outer shaft and the outer shaft and spaced apart in the axial direction for rotatably supporting the inner shaft with respect to the outer shaft;
- a first counter-rotating rear bearing and a first lubricating oil provided to the front of the counter-rotating front bearing and the rear of the counter-rotating rear bearing and supplied to the counter-rotating front bearing and the counter-rotating rear bearing, respectively.
- a counter-rotating propeller marine propulsion including a counter-rotating front seal device and a counter-rotating rear seal device for preventing leakage, and rotating the front propeller and the rear propeller in opposite directions by a rotational drive source
- the outer shaft is a counter-rotating front seal
- second lubricating oil may be a dedicated lubricating oil supplied only to the inside of the outer shaft intermediate shaft as long as it is a lubricating oil supplied to the inside of the outer shaft intermediate shaft. It may be a lubricating oil used for the purpose of lubrication. In the present embodiment, “lubricating oil 45” corresponds to the second lubricating oil.
- the second lubricating oil is supplied to the counter-rotating front seal device by the second lubricating oil being supplied and accumulated inside the outer intermediate shaft by the lubricating oil supply means.
- the outer shaft intermediate shaft has a configuration that can be divided into a plurality of portions in the radial direction.
- the second lubrication is accumulated on the outer intermediate shaft by having a circular opening on the front side of the outer intermediate shaft and functioning as a weir.
- An oil amount adjusting unit for adjusting the amount of oil is provided, and the second lubricating oil is supplied from the front side through the circular opening to the inside of the outer shaft intermediate shaft, and the second lubricating oil is supplied to the inside of the outer shaft intermediate shaft.
- Lubricating oil sticks to the inner peripheral surface of the outer shaft intermediate shaft by centrifugal force when rotating together with the outer shaft intermediate shaft to form a hollow cylindrical shape, and the opening diameter of the circular opening is the double inversion
- An amount of the second lubricating oil that can supply the second lubricating oil to the front seal device is set to accumulate in the outer shaft intermediate shaft, and the second amount corresponding to the storage capacity of the outer shaft intermediate shaft is exceeded. Lubricating oil is discharged from the circular opening.
- the amount of the second lubricating oil accumulated in the outer shaft intermediate shaft by the oil amount adjusting unit provided on the front side of the outer shaft intermediate shaft causes the second reversal front seal device to perform the second lubrication. It is automatically adjusted to a certain amount that can supply oil.
- the second lubricating oil is accumulated to a level necessary for supplying the second lubricating oil to the counter rotating front sealing device, and the overflow is automatically Therefore, it is possible to construct a lubricating structure that can automatically control the storage amount without using a complicated liquid level control mechanism.
- the contra-rotating propeller marine propulsion device has the same driving force as the rotational driving source and the rotational driving force of the driving device.
- An output shaft for an outer shaft provided rotatably in a core shape and a power transmission device for outputting from the output shaft for the inner shaft, and the output shaft for the outer shaft and the intermediate shaft of the outer shaft are connected via a gear coupling
- the second lubricating oil is supplied to the inside of the outer shaft intermediate shaft through the meshing portion of the gear coupling, and the second lubricating oil that exceeds the storage capacity of the outer shaft intermediate shaft is The gas is discharged from the lower meshing portion of the gear coupling through a circular opening.
- the second lubricating oil is supplied to the inside of the outer intermediate shaft through the meshing portion of the gear coupling.
- the lubricating oil for lubricating the gear coupling can be used as the second lubricating oil supplied to the counter-rotating front seal device as it is.
- the meshing portion of the gear coupling functions as a supply port and a discharge port for the second lubricating oil, there is no need to provide a dedicated supply port and a discharge port for supplying and discharging the second lubricating oil.
- the power transmission device is a gear transmission mechanism and houses the output shaft for the outer shaft and the output shaft for the inner shaft.
- a hood that covers the gear coupling and communicates with the interior of the housing is provided on the rear side of the housing, and the second lubricating oil is supplied to the gear coupling from the housing side.
- the second lubricating oil is supplied to the gear coupling from the housing side of the power transmission device. For this reason, a lubricating oil supply system for supplying lubricating oil to the outer intermediate shaft can be shared with the power transmission device.
- the contra-rotating propeller marine propulsion device of the present invention there is an excellent effect that the life of the counter-rotating front seal device can be extended by reducing the heat generation on the front side of the counter-rotating front seal device. can get.
- FIG. 1 is a schematic plan view of a contra-rotating propeller marine propulsion device according to a first embodiment of the present invention.
- FIG. 3 is an enlarged plan view of the periphery of the counter-rotating front seal device and the gear coupling in FIG. 2.
- FIG. 3 is an enlarged side view of the periphery of the counter-rotating front seal device and gear coupling in FIG. 2.
- It is a schematic plan view of the contra-rotating propeller marine propulsion device according to the second embodiment of the present invention.
- FIG. 2 is a schematic plan view of the contra-rotating propeller marine propulsion device 10A according to the first embodiment of the present invention.
- a counter-rotating propeller marine propulsion device 10 ⁇ / b> A (hereinafter sometimes simply referred to as “propulsion device”) includes an outer shaft 11 to which a front propeller 13 is attached and an inner shaft to which a rear propeller 15 is attached. 12, a driving device 30 that is a rotational driving source of the outer shaft 11 and the inner shaft 12, and a power transmission device 20 ⁇ / b> A that transmits the rotational driving force of the driving device 30 to the outer shaft 11 and the inner shaft 12.
- the outer shaft 11 is a hollow component, and an outer shaft main body 11a installed through the stern tube 3 provided in the hull 2 and an outer shaft sleeve connected and fixed to the tip of the outer shaft main body 11a.
- the shaft coupling 11b includes a hollow outer shaft intermediate shaft 11c connected and fixed to the distal end portion of the outer shaft sleeve shaft coupling 11b.
- a front bush 5 and a rear bush 6 are provided between the stern tube 3 and the outer shaft main body 11a, so that the outer shaft 11 is rotatably supported by the hull 2.
- the stern tube lubricating oil is supplied into the stern tube 3 from a stern tube lubricating oil supply device (not shown).
- a stern tube seal device 7 on the bow side is provided on the end surface of the stern tube 3 on the bow side.
- a stern side stern tube seal device 8 is provided on the stern side end surface of the stern tube 3. ing.
- a front propeller 13 is attached to the rear end of the outer shaft 11.
- the front propeller 13 has a boss 13a at the center, and the bow side end face of the boss 13a and the stern side end face of the outer shaft 11 are connected and fixed by connecting means such as bolts.
- the inner shaft 12 is a hollow component, and a rear propeller 15 is attached to the rear end portion and is supported rotatably inside the outer shaft 11.
- the rear propeller 15 has a boss 15 a at the center, is fitted to the rear end of the inner shaft 12 at the boss 15 a, and is fixed to the inner shaft 12 by a propeller nut 39.
- a front radial bearing 35 and a rear radial bearing 36 are installed to rotatably support the inner shaft 12 with the outer shaft 11.
- the front radial bearing 35 is disposed between the outer sleeve sleeve joint 11 b and the inner shaft 12
- the rear radial bearing 36 includes the boss 13 a of the front propeller 13 and the inner shaft 12. It is arranged between.
- the arrangement positions of the front radial bearing 35 and the rear radial bearing 36 are not limited to the positions described above, and may be, for example, between the front end portion and the rear end portion of the outer shaft 11 and the inner shaft 12.
- a counter-rotating thrust bearing 40 that receives the thrust load of the outer shaft 11 and transmits it to the inner shaft 12 is disposed.
- the counter rotating thrust bearing 40 is provided inside the boss 13 a of the front propeller 13. More specifically, an annular recess 14 is formed between the boss of the front propeller 13 and the outer shaft 11, and a counter rotating thrust bearing 40 is provided in the annular recess 14.
- the counter rotating thrust bearing 40 may be a tilting pad type thrust bearing, for example.
- the outer shaft 11 and the boss 13a of the front propeller 13 and the inner shaft 12 are doubled as a first lubricant.
- the reversal lubricating oil is supplied from a counter-reversing lubricating oil supply device (not shown).
- a counter-rotating front seal device 37 is disposed on the bow side end surface of the sleeve shaft joint 11b for the outer shaft, and on the stern side end surface of the boss 13a of the front propeller 13.
- a counter-rotating rear seal device 38 is arranged.
- the second drive device 32 includes a first drive device 31 that is a rotation drive source of the outer shaft 11 and a second drive device 32 that is a rotation drive source of the inner shaft 12.
- the first drive device 31 and the second drive device 32 may be a main engine such as a gas turbine engine or a diesel engine, or may be an electric motor.
- an electric motor for example, one or a plurality of gas turbine generators or diesel generators can be mounted in an engine room and used as a power source.
- the outer shaft 11 and the inner shaft 12 are driven by independent drive sources (the first drive device 31 and the second drive device 32), respectively, so that one of the drive sources (for example, the first drive device 31) should be used. ) Can be continued by driving the front propeller 13 or the rear propeller 15 by the other drive source (for example, the second drive device 32).
- the power transmission device 20A employed in the configuration example of FIG. 2 is configured to transmit the rotational driving force of the first driving device 31 and the second driving device 32 to the outer shaft 11 and the inner shaft 12 independently.
- This is a counter-rotating gear transmission device.
- the power transmission device 20 ⁇ / b> A includes a housing 21, and includes an outer shaft transmission mechanism 18 ⁇ / b> A and an inner shaft transmission mechanism 18 ⁇ / b> B inside the housing 21.
- the outer shaft transmission mechanism 18A and the inner shaft transmission mechanism 18B are both constituted by a gear transmission mechanism.
- the outer shaft transmission mechanism 18A is arranged coaxially with the output shaft 31a of the first driving device 31 and is coaxial with the outer shaft 11 and the outer shaft input gear 22 to which the driving force from the first driving device 31 is inputted.
- a hollow outer output main gear 24 that transmits a rotational driving force to the outer shaft 11, and an outer intermediate shaft disposed between the outer shaft input gear 22 and the outer shaft output main gear 24.
- a small gear 23 is arranged coaxially with the output shaft 31a of the first driving device 31 and is coaxial with the outer shaft 11 and the outer shaft input gear 22 to which the driving force from the first driving device 31 is inputted.
- a hollow outer output main gear 24 that transmits a rotational driving force to the outer shaft 11, and an outer intermediate shaft disposed between the outer shaft input gear 22 and the outer shaft output main gear 24.
- a small gear 23 is arranged coaxially with the output shaft 31a of the first driving device 31 and is coaxial with the outer shaft 11 and the outer shaft input gear 22 to which the driving force from the first driving
- the output shaft 31a of the first drive unit 31 and the outer shaft input gear 22 are connected via a gear coupling 33a so as to be able to absorb errors during installation and changes in the shaft center due to displacement of the hull 2.
- the number of outer intermediate small gear 23 is one, but there may be a plurality.
- the inner shaft transmission mechanism 18B is arranged coaxially with the output shaft 32a of the second drive device 32, and receives the drive force from the second drive device 32, and the outer shaft output main gear.
- An inner shaft output main gear 29 that is inserted through the hollow portion 24 and coaxially disposed with the inner shaft 12 and transmits a rotational driving force to the inner shaft 12, an inner shaft input gear 27, and an inner shaft
- An intermediate small gear for inner shaft 28 disposed between the output main gear 29 and the inner main gear 29;
- the output shaft of the second drive device 32 and the inner shaft input gear 27 are connected via a gear coupling 33b so as to absorb errors during installation and changes in the axis due to the displacement of the hull 2.
- there is one intermediate small gear 28 for the inner shaft but a plurality of intermediate small gears 28 may be provided.
- the inner shaft output main gear 29 and the inner shaft 12 are connected and fixed by a sleeve shaft joint 26 for inner shaft.
- an inner shaft thrust bearing 41 that receives a thrust load from the inner shaft 12 (a load combining the thrust load of only the inner shaft 12 and the thrust load of only the outer shaft 11) and transmits it to the hull 2 is disposed. ing.
- the inner shaft thrust bearing 41 is provided on the bow side portion of the housing 21 of the power transmission device 20. For this reason, the thrust load from the inner shaft 12 is supported by the hull 2 via the housing 21.
- the arrangement position of the inner shaft thrust bearing 41 is not limited to the above-described position as long as the thrust load from the inner shaft 12 can be transmitted to the hull 2. Therefore, as long as it is on the bow side of the output main gear 24 for the outer shaft, it may be inside the housing 21 or outside the housing 21.
- both the outer shaft transmission mechanism 18A and the inner shaft transmission mechanism 18B are gear transmission mechanisms, but one or both are other transmission mechanisms (belt transmission mechanism, chain transmission mechanism, etc.). Also good.
- the outer shaft transmission mechanism 18A and the inner shaft transmission mechanism 18B are housed in the single housing 21, but may be housed in separate housings 21.
- the outer shaft output main gear 24 and the outer shaft 11 are connected via a hollow flexible shaft joint 19.
- the flexible shaft joint 19 is a gear coupling 19A
- the output shaft 24 for the outer shaft is connected and fixed to the bow side of the gear coupling 19A
- the intermediate shaft 11c of the outer shaft is the gear coupling 19A. It is fixedly connected to the stern side. Accordingly, the rotational driving force of the outer shaft output main gear 24 is transmitted to the outer shaft main body 11a via the gear coupling 19A, the outer shaft intermediate shaft 11c, and the outer shaft sleeve joint 11b.
- the thrust load of the outer shaft 11 is received by the inner shaft 12 by the counter rotating thrust bearing 40, and the thrust in which the outer shaft 11 and the inner shaft 12 are combined by the thrust bearing 41 for the inner shaft.
- the load is received by the hull 2, and the rotational force of the output main gear 24 for the outer shaft is transmitted to the outer shaft 11 via a gear coupling 19 ⁇ / b> A that is a flexible shaft joint 19.
- the thrust load of the outer shaft 11 is not transmitted directly to the hull 2, but is transmitted to the hull 2 only through the inner shaft 12, and the deflection of the shaft center is allowed by the flexible shaft joint 19, The influence of the hull displacement on the axis of the outer shaft 11 can be eliminated.
- the flexible shaft joint 19 may be a flange-type flexible shaft joint or a roller chain shaft joint, but a gear coupling 19A having a high allowable transmission torque and capable of allowing not only angular displacement but also axial displacement is suitable. .
- the present invention is not limited to the above-described configuration in which the outer shaft output main gear 24 and the outer shaft 11 are connected via the flexible shaft joint 19, and the outer shaft output main gear 24 and the outer shaft 11 are fixed shafts.
- the structure connected with a joint may be sufficient.
- FIG. 3 and 4 are enlarged views of the periphery of the counter-rotating front seal device 37 and the gear coupling 19A in FIG. 2, FIG. 3 is a schematic plan view, and FIG. 4 is a schematic side view.
- the contra-rotating front seal device 37 includes a hollow liner 37a attached to the inner shaft 12, and is fixed to the outer shaft 11 side and is slidable with respect to the liner 37a. And a seal ring 37b fitted in The counter-rotating rear seal device 38 has the same configuration.
- the gear coupling 19A employed in the configuration example of FIGS. 3 and 4 includes a first inner cylinder 19a provided on the bow side, a second inner cylinder 19b provided on the stern side, and a first inner cylinder 19a. And an outer cylinder 19c surrounding the first inner cylinder 19b, and the rotational driving force of the output main gear 24 for the outer shaft absorbs axial displacement, angular displacement and parallel displacement of the shaft center, and the outer shaft 11 To the side.
- a gear coupling 19A composed of two inner cylinders 19a, 19b and one outer cylinder 19c is employed, but a gear cup composed of one inner cylinder and one outer cylinder. A ring may be employed. Also with this form of gear coupling, axial displacement and angular displacement of the shaft center can be absorbed.
- the first driving device 31 when the first driving device 31 is rotationally driven, the driving force is transmitted to the outer shaft 11 via the outer shaft transmission mechanism 18A, the gear coupling 19A, and the like before being attached to the outer shaft 11.
- the propeller 13 rotates.
- the second driving device 32 when the second driving device 32 is driven to rotate, the driving force is transmitted to the inner shaft 12 via the inner shaft transmission mechanism 18B and the inner shaft sleeve shaft joint 26, and is attached to the inner shaft 12 after the propeller. 15 rotates.
- the front propeller 13 and the rear propeller 15 are rotated in opposite directions by rotating the outer shaft 11 and the inner shaft 12 in opposite directions.
- the rotational direction of the first and second drive units 31 and 32 for rotating the front propeller 13 and the rear propeller 15 in opposite directions depends on the configuration of the power transmission device 20, but the configuration example of FIG. In this case, if the rotation directions of the output shafts of the first driving device 31 and the second driving device 32 are opposite to each other, the front propeller 13 and the rear propeller 15 rotate in opposite directions.
- lubricating oil 45 is supplied into the housing 21 to lubricate the outer shaft transmission mechanism 18A, the inner shaft transmission mechanism 18B, and the gear coupling 19A.
- the lubricating oil 45 is supplied into the housing 21 by the lubricating oil supply device 50.
- the lubricating oil supply device 50 includes a lubricating oil tank 51 that stores the lubricating oil 45, an oil supply pipe 52 that guides the lubricating oil 45 in the lubricating oil tank 51 to the housing 21, a lubricating oil pump 53 that is provided on the oil supply pipe 52, A first recovery pipe 54 for returning the lubricating oil 45 in the housing 21 to the lubricating oil tank 51 and a second recovery pipe 55 for returning the lubricating oil 45 in the hood 21a described later to the lubricating oil tank 51 are provided. It is also possible to connect the downstream end of the second recovery pipe 55 to an intermediate part of the first recovery pipe 54.
- a hood 21a covering the gear coupling 19A is provided on the stern side of the housing 21.
- the housing 21 and the hood 21a communicate with each other, and the lubricating oil 45 is supplied from the housing 21 side to the gear coupling 19A in the hood 21a.
- the hood 21 a may be formed integrally with the housing 21 or may be configured as a separate part from the housing 21.
- an oil drain plate 42 having a circular central opening is provided in the hood 21a in the vicinity of the outer periphery of the first inner cylinder 19b of the gear coupling 19A. Yes.
- the gear coupling 19A is effectively lubricated. Further, since the labyrinth structure is formed by the oil drain plate 42 and the annular convex portion 43, leakage of the lubricating oil 45 from the gear coupling 19A side to the engine room side is effectively prevented.
- Two annular convex portions 43 protruding outward in the radial direction and extending over the entire circumference in the circumferential direction are provided apart from each other in the axial direction on the outer periphery of the second inner cylinder 19b.
- the oil drain plate 42 is disposed so that the inner peripheral end of the circular central opening is inserted between the two annular convex portions 43. With this configuration, the lubricating oil 45 is prevented from leaking from the gear coupling 19A side to the engine room side.
- Three or more annular protrusions 43 are provided apart in the axial direction, and two or more oil drain plates 42 are provided in the axial direction, and the inner peripheral edge of the circular central opening of each oil drain plate 42 is an annular protrusion.
- the oil leakage prevention function may be further enhanced by being configured so as to be inserted between 43.
- the outer shaft intermediate shaft 11 c is provided so as to surround the counter rotating front seal device 37, and the lubricating oil 45 accumulates inside the outer shaft intermediate shaft 11 c, thereby causing the counter rotating front portion.
- Lubricating oil 45 is supplied to the sealing device 37.
- the outer intermediate shaft 11c has a configuration that can be divided into a plurality of parts in the radial direction so as to perform maintenance of the accessory parts (such as the counter-rotating front seal device 37) of the inner shaft 12. The number of divisions may be two or more.
- between the divided pieces of the outer shaft intermediate shaft 11c is liquid-tightly sealed by a seal member so that the lubricating oil 45 does not leak to the outside.
- An oil amount adjusting unit 48 is provided on the front side of the outer shaft intermediate shaft 11c to adjust the amount of the lubricating oil 45 accumulated in the outer shaft intermediate shaft 11c by having a circular opening 48a and functioning as a weir.
- the lubricating oil 45 is supplied from the front side through the circular opening 48a into the outer shaft intermediate shaft 11c.
- the oil amount adjusting portion 48 may be integrally formed with the outer shaft intermediate shaft 11c, may be a separate part from the outer shaft intermediate shaft 11c, or may be a part of the gear coupling 19A.
- the lubricating oil 45 is applied to the meshing portion of the gear coupling 19A (in this embodiment, the outer cylinder 19c and the first inner cylinder 19a indicated by reference numeral A in FIG. 4). Between the gear coupling 19A and the inner shaft 12, and enters and accumulates in the outer intermediate shaft 11c. The lubricating oil 45 accumulated in the outer shaft intermediate shaft 11c rotates together with the outer shaft intermediate shaft 11c, and sticks to the inner surface of the outer shaft intermediate shaft 11c by the centrifugal force at that time to form a hollow cylindrical shape.
- the opening diameter of the circular opening 48a of the oil amount adjusting unit 48 is such that the amount of the lubricating oil 45 that can supply the lubricating oil 45 to the counter rotating front sealing device 37 (specifically, the front side of the seal ring 37b) is the outer shaft. It is set to accumulate inside the intermediate shaft 11c. That is, the lubricating oil 45 is accumulated up to the level indicated by the symbol H on the inner peripheral surface (liquid level) of the hollow cylindrical shape. As a result, the front side of the counter-rotating front seal device 37 (seal ring 37b) is wetted by the lubricating oil 45. Lubricating oil 45 that exceeds the storage capacity of the outer intermediate shaft 11c is discharged from the circular opening 48a.
- the lubricating oil 45 discharged from the circular opening 48a returns to the gear coupling 19A side and engages at the lower portion of the gear coupling 19A (in this embodiment, the outer cylinder 19c, the first inner cylinder 19a and the second inner cylinder 19b). ) Through the second recovery pipe 55 and returned to the lubricating oil tank 51.
- the lubricating oil 45 supplied to the housing 21 by the lubricating oil supply device 50 is supplied to the inside of the outer intermediate shaft 11c via the gear coupling 19A. Therefore, the lubricating oil supply device 50 has a function as lubricating oil supply means for supplying the lubricating oil 45 as the second lubricating oil into the outer shaft intermediate shaft 11c.
- the lubricating oil 45 cannot be supplied to the outer shaft intermediate shaft 11c simply by supplying the lubricating oil 45 to the outer shaft. Therefore, in this case, the lubricating oil 45 is supplied into the housing 21 by providing a rotary joint at an appropriate part (for example, the outer periphery of the outer shaft intermediate shaft 11c) and connecting the oil supply pipe 52 to the rotary joint. It is good also as a lubricating oil supply means for the outer-shaft intermediate shaft 11c mentioned above.
- the lubricating oil system of the lubricating oil supply means for the outer intermediate shaft 11c may be a separate system from the lubricating oil supply device 50 shown in FIG.
- the lubricating oil 45 as the second lubricating oil is supplied and accumulated in the outer shaft intermediate shaft 11c by the lubricating oil supply means, whereby the counter-rotating front seal device 37 (seal Lubricating oil 45 is supplied to the front side of the ring 37b). Accordingly, the front side of the counter-rotating front seal device 37 is made wet by the lubricating oil 45, so that heat generation can be reduced and the life of the counter-rotating front seal device 37 can be extended.
- the outer shaft intermediate shaft 11c has a configuration that can be divided into a plurality of portions in the radial direction. Maintenance of the front seal device 37 and the like can be easily performed.
- the amount of the lubricating oil 45 accumulated inside the outer shaft intermediate shaft 11c is reduced by the oil amount adjusting portion 48 provided on the front side of the outer shaft intermediate shaft 11c. It is automatically adjusted to a certain amount that can supply the lubricating oil 45 to the device 37. As a result, the lubricating oil 45 is stored up to a level necessary for supplying the lubricating oil 45 to the counter-rotating front seal device 37 simply by supplying the lubricating oil 45 to the outer intermediate shaft 11c, and the overflow is automatically Therefore, it is possible to configure a lubrication structure capable of automatically controlling the storage amount without using a complicated liquid level control mechanism.
- the lubricating oil 45 is supplied to the inside of the outer intermediate shaft 11c through the meshing portion of the gear coupling 19A. Therefore, the lubricating oil 45 for lubricating the gear coupling 19A can be used as the lubricating oil 45 supplied to the counter-rotating front seal device 37 as it is. Further, since the meshing portion of the gear coupling 19A functions as a supply port and a discharge port for the lubricating oil 45, there is no need to provide a dedicated supply port and a discharge port for supplying and discharging the lubricating oil 45.
- the lubricating oil 45 is supplied to the gear coupling 19A from the housing 21 side of the power transmission device 20A. For this reason, the lubricating oil supply system for supplying the lubricating oil 45 to the outer intermediate shaft 11c can be shared with the power transmission device 20A.
- FIG. 5 is a schematic plan view of a contra-rotating propeller marine propulsion device 10B according to the second embodiment of the present invention. This embodiment is different from the first embodiment with respect to the drive device 30 and the power transmission device 20B. Although FIG. 5 which shows this embodiment is simplified with respect to FIG. 2 which shows 1st Embodiment, about parts other than the drive device 30 and the power transmission device 20B, it is the same as 1st Embodiment.
- the power transmission device 20B rotates biaxially in directions opposite to each other with respect to a uniaxial rotational input. Is a counter-rotating transmission device. That is, the power transmission device 20B converts the rotational driving force of the driving device into the driving force in the rotation direction opposite to each other and transmits the driving force to the outer shaft 11 and the inner shaft 12, respectively.
- the output shaft for the outer shaft of the power transmission device 20B is transmitted to the outer shaft 11 through the gear coupling 19A as in the first embodiment.
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Abstract
Description
本発明は、二重反転プロペラ式舶用推進装置に関する。
二重反転プロペラは、前プロペラから流出する回転エネルギーを、前プロペラとは逆方向に回転する後プロペラで回収し推進力に変えることで、高いプロペラ効率が得られるようにしたプロペラシステムである。以下、二重反転プロペラを搭載した舶用推進装置を「二重反転プロペラ式舶用推進装置」と呼ぶ。二重反転プロペラ式舶用推進装置は、例えば、下記特許文献1に開示されている。
(1)本発明は、後端部に前プロペラが取り付けられ船体に回転可能に支持された中空状の外軸と、後端部に後プロペラが取り付けられ前記外軸の内部に回転可能に支持された内軸と、前記外軸と前記内軸との間に軸方向に間隔を置いて設けられ前記内軸を前記外軸に対して回転可能に支持するための二重反転前部軸受及び二重反転後部軸受と、二重反転前部軸受の前方及び二重反転後部軸受の後方にそれぞれ設けられ前記二重反転前部軸受及び前記二重反転後部軸受に供給される第1潤滑油の漏れを防止するための二重反転前部シール装置及び二重反転後部シール装置とを備え、回転駆動源により前記前プロペラと前記後プロペラとを互いに逆方向に回転させる二重反転プロペラ式舶用推進装置において、前記外軸は、二重反転前部シール装置を囲み前記回転駆動源側に連結された中空状の外軸中間軸を有しており、さらに、前記外軸中間軸の内部に第2潤滑油を供給する潤滑油供給手段を備え、該外軸中間軸の内部に第2潤滑油が溜まることで前記二重反転前部シール装置に第2潤滑油が供給される、ことを特徴とする。
ここで、上記の「第2潤滑油」は、外軸中間軸の内部に供給される潤滑油であれば、外軸中間軸の内部にのみ供給される専用の潤滑油でもよく、他の部位の潤滑を目的として使用される潤滑油であってもよい。本実施形態では、「潤滑油45」が第2潤滑油に該当する。
図3及び図4は、図2における二重反転前部シール装置37及びギヤカップリング19Aの周辺の拡大図であり、図3は模式平面図、図4は模式側面図である。
(1)本実施形態によれば、潤滑油供給手段によって外軸中間軸11cの内部に第2潤滑油としての潤滑油45が供給されて溜まることで、二重反転前部シール装置37(シールリング37b)の前側に潤滑油45が供給される。これにより、潤滑油45によって二重反転前部シール装置37の前側をウエット状態とすることで、発熱を軽減し、二重反転前部シール装置37の寿命を延ばすことができる
Claims (5)
- 後端部に前プロペラが取り付けられ船体に回転可能に支持された中空状の外軸と、後端部に後プロペラが取り付けられ前記外軸の内部に回転可能に支持された内軸と、前記外軸と前記内軸との間に軸方向に間隔を置いて設けられ前記内軸を前記外軸に対して回転可能に支持するための二重反転前部軸受及び二重反転後部軸受と、二重反転前部軸受の前方及び二重反転後部軸受の後方にそれぞれ設けられ前記二重反転前部軸受及び前記二重反転後部軸受に供給される第1潤滑油の漏れを防止するための二重反転前部シール装置及び二重反転後部シール装置とを備え、回転駆動源により前記前プロペラと前記後プロペラとを互いに逆方向に回転させる二重反転プロペラ式舶用推進装置において、
前記外軸は、二重反転前部シール装置を囲み前記回転駆動源側に連結された中空状の外軸中間軸を有しており、
さらに、前記外軸中間軸の内部に第2潤滑油を供給する潤滑油供給手段を備え、
前記外軸中間軸の内部に第2潤滑油が溜まることで前記二重反転前部シール装置に第2潤滑油が供給される、ことを特徴とする二重反転プロペラ式舶用推進装置。 - 前記外軸中間軸は半径方向に複数に分割可能な構成を備える請求項1記載の二重反転プロペラ式舶用推進装置。
- 前記外軸中間軸の前側に、円形開口を有し堰として機能することで当該外軸中間軸に溜まる第2潤滑油の量を調整する油量調整部が設けられ、前記第2潤滑油は前方側から前記円形開口を通って前記外軸中間軸の内部に供給され、
前記外軸中間軸の内部の前記第2潤滑油は、前記外軸中間軸とともに回転する際の遠心力によって前記外軸中間軸の内周面に張り付いて中空円筒形を成し、
前記円形開口の開口径は、前記二重反転前部シール装置まで第2潤滑油を供給可能な量の第2潤滑油が前記外軸中間軸の内部に溜まるように設定されており、
前記外軸中間軸の貯留容量を超える分の第2潤滑油は前記円形開口から排出される、請求項1記載の二重反転プロペラ式舶用推進装置。 - 前記二重反転プロペラ式舶用推進装置は、回転駆動源である駆動装置と、該駆動装置の回転駆動力を同芯状に回転可能に設けられた外軸用出力軸と内軸用出力軸から出力する動力伝達装置とを備え、
前記外軸用出力軸と前記外軸中間軸はギヤカップリングを介して連結されており、
前記第2潤滑油は前記ギヤカップリングの噛合い部を通って前記外軸中間軸の内部に供給され、前記外軸中間軸の貯留容量を超える分の第2潤滑油は前記円形開口を通って前記ギヤカップリングの下部の噛合い部から排出される、請求項3記載の二重反転プロペラ式舶用推進装置。 - 前記動力伝達装置は、歯車伝動機構であり、前記外軸用出力軸及び前記内軸用出力軸を収容するハウジングを有し、
該ハウジングの後側には前記ギヤカップリングを覆い前記ハウジングの内部と連通するフードが設けられ、
前記第2潤滑油は前記ハウジング側から前記ギヤカップリングに供給される、請求項4記載の二重反転プロペラ式舶用推進装置。
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US12/812,450 US8641463B2 (en) | 2008-01-09 | 2008-11-28 | Contra-rotating propeller marine propulsion device |
BRPI0822154-5A BRPI0822154A2 (pt) | 2008-01-09 | 2008-11-28 | Dispositivo de propulsão marítimo com propulsor de contra-rotação |
KR1020107013900A KR101255597B1 (ko) | 2008-01-09 | 2008-11-28 | 이중 반전 프로펠러식 선박용 추진 장치 |
EP08869777.6A EP2230172A4 (en) | 2008-01-09 | 2008-11-28 | Contra-rotating propeller marine propulsion device |
CN2008801244519A CN101909987B (zh) | 2008-01-09 | 2008-11-28 | 双反转螺旋桨式船用推进装置 |
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JP2008002512A JP5266543B2 (ja) | 2008-01-09 | 2008-01-09 | 二重反転プロペラ式舶用推進装置 |
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JP5266542B2 (ja) * | 2008-01-08 | 2013-08-21 | ジャパンマリンユナイテッド株式会社 | 二重反転プロペラ式舶用推進装置 |
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2008
- 2008-01-09 JP JP2008002512A patent/JP5266543B2/ja active Active
- 2008-11-28 KR KR1020107013900A patent/KR101255597B1/ko active IP Right Grant
- 2008-11-28 EP EP08869777.6A patent/EP2230172A4/en not_active Withdrawn
- 2008-11-28 US US12/812,450 patent/US8641463B2/en not_active Expired - Fee Related
- 2008-11-28 BR BRPI0822154-5A patent/BRPI0822154A2/pt not_active IP Right Cessation
- 2008-11-28 CN CN2008801244519A patent/CN101909987B/zh active Active
- 2008-11-28 WO PCT/JP2008/071643 patent/WO2009087832A1/ja active Application Filing
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JPS62181998A (ja) * | 1986-02-07 | 1987-08-10 | Eagle Ind Co Ltd | 船尾管への潤滑油供給方法 |
JPS6366400U (ja) * | 1986-10-21 | 1988-05-02 | ||
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Also Published As
Publication number | Publication date |
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JP2009161116A (ja) | 2009-07-23 |
EP2230172A4 (en) | 2017-01-11 |
US20110021095A1 (en) | 2011-01-27 |
EP2230172A1 (en) | 2010-09-22 |
CN101909987B (zh) | 2013-06-05 |
KR20100096197A (ko) | 2010-09-01 |
US8641463B2 (en) | 2014-02-04 |
JP5266543B2 (ja) | 2013-08-21 |
CN101909987A (zh) | 2010-12-08 |
BRPI0822154A2 (pt) | 2015-06-16 |
KR101255597B1 (ko) | 2013-04-16 |
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