JP5037374B2 - Lubrication structure of counter rotating seal device - Google Patents

Description

  The present invention relates to a lubricating structure for a counter rotating seal device.

  The contra-rotating propeller is a propeller system that obtains high propeller efficiency by collecting rotational energy flowing out from the front propeller with a propeller that rotates in the opposite direction to the front propeller and converting it into propulsion. Hereinafter, 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 in, for example, Patent Document 1 below.

  As a conventional example of the contra-rotating propeller marine propulsion device, a “counter-rotating propeller device” disclosed in Patent Document 1 is shown in FIG. In the contra-rotating propeller device 100 of FIG. 9, the rear propeller 101 is attached to the rear end portion of the inner shaft 102 connected to the 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. Are supported by a front outer bearing 107 and a rear outer bearing 108 attached to the rear. In order to prevent the lubricating oil supplied to the bearings 105 to 108 from flowing out of the ship or into the ship, 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.

Japanese Patent Laid-Open No. 7-10085

  In the contra-rotating propeller, the seal portion of the front inner shaft seal device (hereinafter referred to as the counter-rotating front seal 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 is a counter-rotating seal that can extend the life of the counter-rotating front seal device by reducing the heat generation on the front side of the counter-rotating front seal device. It is an object of the present invention to provide a lubricating structure for an apparatus.

In order to solve the above problems, the lubricating structure of the counter-rotating seal device of the present invention employs the following technical means.
(1) In the present invention, a hollow outer shaft having a front propeller attached to the rear end portion, and a rear propeller attached to the rear end portion so as to be rotatable inside the outer shaft via a counter rotating bearing portion. A counter-rotating front seal device for preventing leakage of the first lubricating oil provided to the counter-rotating bearing portion provided in front of and behind the counter-rotating bearing portion, and a supported inner shaft. A counter-rotating seal device in a counter-rotating propeller marine propulsion device that rotates the front propeller and the rear propeller in opposite directions by a rotational drive source, A hollow outer shaft intermediate shaft that forms part of the outer shaft and surrounds the contra-rotating front seal device, and is fixed to the front end portion of the outer shaft intermediate shaft at the rear end portion, and surrounds the inner shaft, A hollow ring that can be divided into a plurality of pieces in the radial direction; A hollow gear coupling coupled to the front end of the empty ring and having an outer diameter smaller than the inner diameter of the outer shaft intermediate shaft; and a lubricating oil supply means for supplying a second lubricating oil into the outer shaft intermediate shaft; The gear coupling has a first ring gear fixed to the drive source side, a second ring gear fixed to the hollow ring, and an outer cylinder gear meshing with the first ring gear and the second ring gear. The second lubricating oil is supplied to the counter-rotating front seal device by collecting the second lubricating oil inside the outer shaft intermediate shaft.
Here, the above-mentioned “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.

According to the configuration of the present invention, the second lubricating oil is supplied to the counter rotating front sealing device by the second lubricating oil being supplied and accumulated inside the outer shaft intermediate shaft by the lubricating oil supply means. Thereby, by making the front side of the counter-rotating front seal device wet with the second lubricating oil, it is possible to reduce heat generation and extend the life of the counter-rotating front seal device. When maintaining parts (such as a counter-rotating front seal device), the hollow ring is disassembled, and the gear coupling is moved back and forth to enable access to parts requiring maintenance, making maintenance easy. can do. In this case, since the outer diameter of the gear coupling is smaller than the inner diameter of the outer intermediate shaft, the inner portion of the inner shaft covered by the gear coupling can be moved rearward to the inner intermediate shaft. Can be exposed greatly. Therefore, for example, when there is a maintenance-needed part such as a sleeve shaft joint for an inner shaft in a portion exposed when the gear coupling is moved rearward, it can be easily maintained.
Also, the outer shaft intermediate shaft is not disassembled during maintenance, and the disassembled is a hollow ring that can be formed relatively short. If the hollow ring is short, the length of the sealing material (such as an O-ring) provided in the divided parts The manufacturing cost can be reduced because it is easy to form a groove for mounting a sealing material that requires high-precision processing. In addition, since the hollow ring is a short part, the number of connecting parts (bolts and the like) required for assembly can be reduced, so that assembly after maintenance is easy.

(2) In the lubricating structure of the counter rotating seal device according to (1), preferably, the hollow ring has a circular opening and functions as a weir so that the amount of the second lubricating oil accumulated on the outer shaft intermediate shaft 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 inside the outer shaft intermediate shaft is The hollow shaft is attached to the inner peripheral surface of the outer shaft intermediate shaft by centrifugal force when rotating together with the outer shaft intermediate shaft, and the opening diameter of the circular opening is the counter-rotating front seal device The amount of the second lubricating oil that can supply the second lubricating oil is set so as to be accumulated in the outer intermediate shaft, and the second lubricating oil that exceeds the storage capacity of the outer intermediate shaft is It is discharged from the circular opening.

  According to said structure, the quantity of the 2nd lubricating oil which accumulates inside an outer-shaft intermediate shaft by the hollow ring which is an oil quantity adjustment part is a fixed quantity which can supply 2nd lubricating oil to a counter-rotating front seal device Will be adjusted automatically. As a result, only by supplying the second lubricating oil to the outer intermediate shaft, 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, the storage amount can be automatically controlled without using a complicated liquid level control mechanism.

(3) In the lubricating structure of the counter rotating seal device according to the above (1), preferably, the counter rotating propeller marine propulsion device has the same driving force as that of the rotational driving source and the rotational driving force of the driving device. An outer shaft output shaft provided rotatably in a core shape and a power transmission device that outputs from the inner shaft output shaft, and the second lubricating oil passes through the meshing portion of the gear coupling and the outer shaft The second lubricating oil supplied to the inside of the intermediate shaft and exceeding the storage capacity of the outer shaft intermediate shaft passes through the circular opening and is discharged from the lower meshing portion of the gear coupling.

  According to the above configuration, the second lubricating oil is supplied to the inside of the outer intermediate shaft through the meshing portion of the gear coupling. For this reason, 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. Further, since 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.

(4) In the lubricating structure of the counter-rotating seal device according to (3), preferably, the power transmission device is a gear transmission mechanism, and a housing that houses the output shaft for the outer shaft and the output shaft for the inner shaft. And a hood that covers the hollow ring and the gear coupling and is detachably attached to the housing and can be divided into a plurality of pieces in the radial direction.

  According to the above configuration, since the hollow ring and the gear coupling are covered by the hood, the second lubricating oil can be prevented from scattering. Also, the hood is detachable from the housing and can be divided into multiple parts in the radial direction. By removing, maintenance can be easily performed.

(5) In the lubricating structure of the counter-rotating seal device according to (4), preferably, the hood communicates with the inside of the housing inside, and the second lubricating oil is fed from the housing side to the gear. Supplied to the coupling.

  According to said structure, 2nd lubricating oil is supplied to a gear coupling from the housing side of a 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.

  According to the lubricating structure of the counter-rotating seal device of the present invention, it is possible to extend the life of the counter-rotating front seal device by reducing the heat generation on the front side of the counter-rotating front seal device. can get.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted. In the following description, “bow side” and “front side” have the same meaning, and “stern side” and “rear side” have the same meaning.

  FIG. 1 is a schematic plan view of a counter-rotating propeller marine propulsion device 1 provided with a lubricating structure 10 for a counter-rotating seal device according to an embodiment of the present invention. In FIG. 1, a counter-rotating propeller marine propulsion device 1 (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 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. The outer shaft intermediate shaft 11 c is arranged so as to surround the counter-rotating front seal device 37.

  A front bush 5 and a rear bush 6 are provided between the stern tube 3 and the outer shaft main body 11 a, whereby the outer shaft 11 is rotatably supported by the hull 2. In order to lubricate the front bush 5 and the rear bush 6, the stern tube lubricating oil is supplied into the stern tube 3 from a stern tube lubricating oil supply device (not shown).

  In order to prevent leakage of the stern tube lubricating oil to the engine room side, a stern tube stern tube seal device 7 is provided on the end surface of the stern tube 3 on the bow side. In order to prevent leakage of the stern tube lubricating oil in the stern tube 3 to the seawater side and intrusion of seawater into the stern tube 3, 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 portion 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 part, and a rear propeller 15 is attached to the rear end portion thereof and is rotatably supported inside the outer shaft 11. The rear propeller 15 has a boss 15 a at the center, is fitted to the rear end portion of the inner shaft 12 at the 15 a boss, and is fixed to the inner shaft 12 by a propeller nut 39.

  In the propulsion device 1, in order to rotatably support the inner shaft 12 by the outer shaft 11, a front radial bearing 35 and a rear radial bearing 36, which are counter-rotating bearing portions, are installed. In the configuration example of FIG. 1, the front radial bearing 35 is disposed between the sleeve shaft joint 11 b for the outer shaft and the inner shaft 12, and the rear radial bearing 36 is formed between the front propeller 13 boss and the inner shaft 12. Arranged between.

  In the propulsion device 1, a counter rotating thrust bearing 40 that receives a thrust load of the outer shaft 11 and transmits it to the inner shaft 12 is disposed. In the configuration example of FIG. 1, the counter rotating thrust bearing 40 is provided inside the boss 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.

  In order to lubricate the front radial bearing 35, the rear radial bearing 36 and the counter-rotating thrust bearing 40, 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). In order to prevent the counter-rotating lubricant from leaking out, 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 drive device 30 employed in the configuration example of FIG. 1 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. In the case of 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.

  Thus, 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 20 employed in the configuration example of FIG. 1 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. More specifically, the power transmission device 20 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. In the configuration of FIG. 1, both the outer shaft transmission mechanism 18A and the inner shaft transmission mechanism 18B are gear transmission mechanisms.

  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. And a small gear 23.

  The output shaft 31a of the first driving device 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 axial center due to displacement of the hull 2. In FIG. 1, the number of the 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 input gear 27 for the inner shaft are connected via a gear coupling 33b so as to be able to absorb errors during installation and changes in the axis due to displacement of the hull 2. In FIG. 1, 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.

  In the propulsion device 1, an inner shaft thrust bearing 41 that receives a thrust load from the inner shaft 12 (a load obtained by combining a thrust load of only the inner shaft 12 and a thrust load of only the outer shaft 11) and transmits it to the hull 2 is disposed. ing. In the configuration example of FIG. 1, 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.

A hollow ring 48 is connected and fixed to the bow side of the outer intermediate shaft 11c. A hollow gear coupling 19 is connected to the bow side of the hollow ring 48. An output main gear 24 for the outer shaft is connected and fixed.
With the above configuration, the rotational driving force of the output main gear 24 for the outer shaft is transmitted to the outer shaft main body 11a via the gear coupling 19, the hollow ring, the outer shaft intermediate shaft 11c, and the outer sleeve coupling 11b. The

  In the propulsion device 1 having the above-described configuration, 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 inner shaft thrust bearing 41. A 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 the gear coupling 19. As a result, the thrust load of the outer shaft 11 is not transmitted directly to the hull 2, but is transmitted only to the hull 2 via the inner shaft 12, and the shaft coupling is allowed to be misaligned by the gear coupling 19. The influence of the hull displacement on the axis of the outer shaft 11 can be eliminated.

  The arrangement position of the inner shaft thrust bearing 41 described above is not limited to the position described above 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.

  In the configuration example of FIG. 1, 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.

In the configuration example of FIG. 1, the outer shaft transmission mechanism 18 </ b> A and the inner shaft transmission mechanism 18 </ b> B are housed in a single housing 21, but may be housed in separate housings 21.
In the configuration example shown in FIG. 1, a driving mechanism of a system that outputs a biaxial rotation with respect to a biaxial rotational input is adopted as a driving system of the contra-rotating propeller. You may employ | adopt the drive mechanism of the system which outputs the rotation of the biaxial which rotates to an opposite direction.

  2 and 3 are enlarged views of the periphery of the outer intermediate shaft 11c, the hollow ring 48, and the gear coupling 19 in FIG. 1, FIG. 2 is a schematic plan view, and FIG. 3 is a schematic side view.

  2 and 3, the contra-rotating front seal device 37 includes a hollow liner 37a attached to the inner shaft 12 and a rotary slide that is fixed to the outer shaft 11 side and is slidable relative to the liner 37a. And a seal ring 37b fitted in The counter-rotating rear seal device 38 has the same configuration.

  The outer shaft intermediate shaft 11 c is a hollow cylindrical part surrounding the counter-rotating front seal device 37. The hollow ring 48 is a circular ring-shaped part having a central opening 48a. The outer shaft intermediate shaft 11c is not a part that can be divided in the radial direction, but the hollow ring 48 is a part that can be divided into a plurality of parts in the radial direction.

  4A and 4B are diagrams showing a configuration example of the hollow ring 48, where FIG. 4A is a side view and FIG. 4B is a front view. In the configuration example of FIG. 4, the hollow ring 48 has a structure that can be divided into two (in FIG. 4, it is divided into two vertically). A flange portion 49 is formed in each divided component, and the flange portion 49 is connected to each other by a connection fixing component such as a bolt. The mating surfaces of the divided parts are liquid-tightly sealed by a seal member (O-ring or the like) so that a later-described lubricating oil 45 does not leak to the outside.

  2 and 3, the gear coupling 19 includes an outer ring meshing with a first ring gear 19 a provided on the bow side, a second ring gear 19 b provided on the stern side, and the first ring gear 19 a and the first ring gear 19 b. The outer shaft output main gear 24 has a cylindrical gear 19c, and the gear formed on the outer periphery of the first ring gear 19a and the second ring gear 19b and the gear formed on the inner periphery of the outer cylindrical gear 19c mesh with each other. The rotational driving force is absorbed to the axial displacement, angular displacement and parallel displacement of the shaft center and transmitted to the outer shaft 11 side.

  The outer diameter of the gear coupling 19 (outer cylinder gear 19c) is smaller than the inner diameter of the outer intermediate shaft 11c. A front stopper 19d and a rear stopper 19e are provided at the front end and the rear end of the outer cylinder gear 11c, respectively, so that the axial movement of the outer cylinder gear 11c relative to the first ring gear 19a and the second ring gear 19b is limited within a certain range. Yes. The front stopper 19d and the rear stopper 19e can be removed during maintenance.

  With the above-described configuration, 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 19 and the like, before being attached to the outer shaft 11. The propeller 13 rotates. Further, 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.

  At this time, 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.

  As shown in FIG. 3, lubricating oil 45 is supplied into the housing 21 in order to lubricate the outer shaft transmission mechanism 18 </ b> A, the inner shaft transmission mechanism 18 </ b> B, and the gear coupling 19. 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.

2 and 3, a hood 21a for covering the hollow ring and the gear coupling is provided at the rear part of the housing. The inside of the housing 21 and the inside of the hood 21a communicate with each other, and the lubricating oil 45 is supplied from the housing 21 side to the gear coupling 19 in the hood 21a.
The hood 21a is detachably attached to the housing 21 and has a structure that can be divided into a plurality of pieces in the radial direction. When the hood 21a is removed from the housing 21, the hollow ring 48 and the gear coupling 19 are exposed.

  Thus, since the hood 21a surrounding the gear coupling 19 is provided and the lubricating oil 45 is supplied to the gear coupling 19, the gear coupling 19 is effectively lubricated and leakage of the lubricating oil is prevented.

  As shown in FIG. 3, the outer shaft intermediate shaft 11c is provided so as to surround the counter rotating front seal device 37, and the lubricating oil 45 is accumulated inside the outer shaft intermediate shaft 11c so that the counter rotating front portion Lubricating oil 45 is supplied to the sealing device 37.

  The hollow ring 48 is an oil amount adjusting unit that adjusts 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.

  In FIG. 3, when the gear coupling 19 is lubricated, the lubricating oil 45 is a meshing portion of the gear coupling 19 (in this embodiment, the outer cylinder gear 19c and the first ring gear 19a, which are indicated by the symbol A in FIG. Between the gear coupling 19 and the inner shaft 12, and between the hollow ring 48 and the inner shaft 12, and enters the outer shaft intermediate shaft 11c and accumulates. 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 is such that the amount of the lubricating oil 45 that can supply the lubricating oil 45 to the counter rotating front seal device 37 (specifically, the front side of the seal ring 37b) is within the outer shaft intermediate shaft 11c. It is set to accumulate. 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 19 side, and passes through a meshing portion (between the outer cylinder gear 19c, the first ring gear 19a, and the second ring gear 19b) of the lower portion of the gear coupling 19. The oil is discharged from the discharge port 46 and returned to the lubricating oil tank 51 through the second recovery pipe 55.

  In the present embodiment, the lubricating oil 45 supplied to the housing by the lubricating oil supply device 50 is supplied to the inside of the outer intermediate shaft 11 c via the gear coupling 19. 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.

  With reference to FIG. 2 and FIG. 5 to FIG. 7, the procedure in the case of maintaining the accessory parts of the inner shaft 12 will be described.

  When the hood 21a is removed from the housing 21 from the state of FIG. 2, the gear coupling 19 is exposed and the front stopper 19d and the rear stopper 19e can be accessed, so that the front stopper from the outer cylindrical gear 19c of the gear coupling 19 can be obtained. 19d and the rear stopper 19e are removed, and the outer cylinder gear 19c is moved to the bow side to obtain the state shown in FIG. Then, since the outer cylinder gear 19c is disengaged from the second ring gear 19b, it is accessed from the bow side of the second ring gear 19b, and the bolt that has fixed the second ring gear 19b to the hollow ring 48 is removed, whereby the second ring gear 19b. Is removed from the hollow ring 48.

  Next, the hollow ring 48 is removed from the outer intermediate shaft 11c, and the hollow ring 48 is disassembled and removed to obtain the state shown in FIG. Then, since the counter-rotating front seal device 37 can be accessed, the counter-rotating front seal device 37 can be maintained.

  When the sleeve coupling 26 for the inner shaft is inside the gear coupling 62 at the normal position (position shown in FIG. 2) as in the present embodiment, the outer cylinder gear 19c is moved from the state of FIG. Since the outer cylinder gear 19c is moved to the stern side to the position where it is inserted inside the outer intermediate shaft 11c and brought into the state of FIG. 7, the inner sleeve sleeve coupling 26 can be accessed. The sleeve shaft joint 26 can be maintained.

  When the maintenance of the parts requiring maintenance is completed as described above, the parts are attached and returned to the state shown in FIG.

According to the embodiment of the present invention described above, the following effects can be obtained.
(1) 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, thereby lubricating the front side of the counter-rotating front seal device 37 (seal ring 37b). Oil 45 is supplied. 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.

(2) The amount of the lubricating oil 45 accumulated inside the outer shaft intermediate shaft 11c is automatically set to a certain amount by which the lubricating oil 45 can be supplied to the counter-rotating front seal device 37 by the hollow ring 48 serving as an oil amount adjusting unit. Adjusted to 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, the storage amount can be controlled automatically without using a complicated liquid level control mechanism.

(3) Lubricating oil 45 is supplied into the outer shaft intermediate shaft 11 c through the meshing portion of the gear coupling 19. For this reason, the lubricating oil 45 for lubricating the gear coupling 19 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 19 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.

(4) Since the hollow ring 48 and the gear coupling 19 are covered with the hood 21a, scattering of the lubricating oil 45 can be prevented. Further, since the hood 21a is detachable from the housing 21 and can be divided into a plurality of parts in the radial direction, the hood 21a can be attached at the time of maintenance of the accessory parts (such as the counter-rotating front seal device 37) of the inner shaft 12. Maintenance can be easily performed by disassembling and removing from the housing 21.

(5) Since the lubricating oil 45 is supplied from the housing 21 side of the power transmission device 20 to the gear coupling 19, the lubricating oil supply system for supplying the lubricating oil 45 to the outer intermediate shaft 11c is referred to as the power transmission device 20. Can be shared.

(6) When maintaining the accessory parts (such as the counter-rotating front seal device 37) of the inner shaft 12, the hollow ring 48 is disassembled, and the gear coupling 19 is moved back and forth, so that maintenance is required. Can be accessed and maintenance can be performed easily. In this case, since the outer diameter of the gear coupling 19 is smaller than the inner diameter of the outer shaft intermediate shaft 11 c, the gear coupling 19 can be moved backward to the inside of the outer shaft intermediate shaft 11 c and is covered by the gear coupling 19. The portion of the inner shaft 12 that has been exposed can be greatly exposed. Therefore, when there is a maintenance-needed part such as the sleeve shaft joint 26 for the inner shaft in a portion exposed when the gear coupling 19 is moved rearward from the normal position as in the present embodiment, this is easily maintained. it can.

(7) Instead of eliminating the hollow ring 48 as in the reference example shown in FIG. 8, an outer shaft intermediate shaft 58 that is relatively long and can be divided into a plurality of portions in the radial direction, and a short gear coupling 59 are provided. It may be possible to perform maintenance by disassembling the outer shaft intermediate shaft 58 during maintenance, but in such a configuration, the seal material applied to the long outer shaft intermediate shaft 58 is long and highly accurate. Since it becomes difficult to form a groove for mounting a sealing material that requires this processing, the manufacturing cost increases. Moreover, since it is long, the number of connecting parts (bolts and the like) required for assembly increases, and assembly after maintenance is complicated. On the other hand, according to the present embodiment, the outer shaft intermediate shaft 11c is not disassembled during maintenance, and the disassembled portion is a hollow ring 48 that can be formed relatively short. If the hollow ring 48 is short, it is divided into its divided parts. Since the length of the sealing material to be provided can be shortened and the groove for mounting the sealing material can be easily formed, the manufacturing cost can be reduced. Moreover, since the hollow ring 48 is a short part, the number of connecting parts (bolts and the like) required for the assembly can be reduced, so that the assembly after the maintenance is easy.

  Although the embodiments of the present invention have been described above, the embodiments of the present invention disclosed above are merely examples, and the scope of the present invention is not limited to these embodiments. . The scope of the present invention is indicated by the description of the scope of claims, and further includes meanings equivalent to the description of the scope of claims and all modifications within the scope.

1 is a schematic plan view of a counter-rotating propeller marine propulsion device provided with a lubricating structure of a counter-rotating seal device according to an 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 the lubricating structure of the counter-rotating seal device according to the embodiment of the present invention. FIG. 3 is an enlarged side view of the periphery of a counter-rotating front seal device and a gear coupling in the lubricating structure of the counter-rotating seal device according to the embodiment of the present invention. It is a figure which shows the structure of the hollow ring in the lubrication structure of the counter-rotating sealing apparatus concerning embodiment of this invention. In the lubricating structure of the counter-rotating seal device according to the embodiment of the present invention, it is a first diagram for explaining the procedure in the case of maintaining the auxiliary components of the inner shaft. FIG. 7 is a second diagram illustrating a procedure for maintaining an accessory component of the inner shaft in the lubricating structure of the counter-rotating seal device according to the embodiment of the present invention. FIG. 10 is a third diagram illustrating a procedure for maintaining an accessory component of the inner shaft in the lubricating structure of the counter-rotating seal device according to the embodiment of the present invention. It is a figure which shows the lubrication structure of the counter-rotating sealing apparatus of a reference example. It is a figure which shows a prior art.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Counter-rotating propeller type marine propulsion device 2 Hull 3 Stern tube 5 Front side bush 6 Rear side bush 7 Bow side stern tube sealing device 8 Stern side stern tube sealing device 10 Lubricating structure 11 of counter rotating seal device 11 Outer shaft 11a Outer shaft Body 11b Outer shaft sleeve joint 11c Outer shaft intermediate shaft 12 Inner shaft 13 Front propeller 15 Rear propeller 19 Gear coupling 20 Power transmission device 21 Housing 21a Hood 30 Drive device 35 Front radial bearing 36 Rear radial bearing 37 Front seal device 38 Counter rotating rear seal device 40 Counter rotating thrust bearing 45 Lubricating oil (second lubricating oil)
46 discharge port 48 hollow ring 48a circular opening 50 lubricating oil supply device (lubricating oil supply means)
51 Lubricating oil tank 52 Oil supply pipe 53 Lubricating oil pump 54 First recovery pipe 55 Second recovery pipe

Claims (4)

A hollow outer shaft with a front propeller attached to the rear end, an inner shaft with a rear propeller attached to the rear end and rotatably supported inside the outer shaft via a counter-rotating bearing portion; A counter-rotating front seal device and a counter-rotating rear seal device provided respectively in front and rear of the counter-rotating bearing portion for preventing leakage of the first lubricating oil supplied to the counter-rotating bearing portion; Comprising a lubricating structure of a counter-rotating seal device in a counter-rotating propeller marine propulsion device that rotates the front propeller and the rear propeller in opposite directions by a rotational drive source,
A hollow outer shaft intermediate shaft that constitutes a part of the outer shaft and surrounds the counter-rotating front seal device;
A hollow ring that is fixed to the front end portion of the outer shaft intermediate shaft at the rear end portion, surrounds the inner shaft, and can be divided into a plurality of portions in the radial direction;
A hollow gear coupling coupled to the front end of the hollow ring and having an outer diameter smaller than the inner diameter of the outer shaft intermediate shaft;
Lubricating oil supply means for supplying a second lubricating oil into the outer shaft intermediate shaft,
The gear coupling has a first ring gear fixed to the drive source side, a second ring gear fixed to the hollow ring, and an outer cylinder gear meshing with the first ring gear and the second ring gear,
The second lubricating oil is stored in the outer shaft intermediate shaft, whereby the second lubricating oil is supplied to the counter-rotating front seal device ,
The hollow ring is an oil amount adjusting unit that adjusts the amount of second lubricating oil accumulated in the outer shaft intermediate shaft by having a circular opening and functioning as a weir, and the second lubricating oil is circular from the front side. Supplied to the inside of the outer shaft intermediate shaft through the opening,
The second lubricating oil inside the outer shaft intermediate shaft sticks to the inner peripheral surface of the outer shaft intermediate shaft by a centrifugal force when rotating together with the outer shaft intermediate shaft to form a hollow cylindrical shape,
The opening diameter of the circular opening is set so that the second lubricating oil in an amount capable of supplying the second lubricating oil to the counter-rotating front seal device is accumulated inside the outer shaft intermediate shaft,
A lubricating structure for a counter-rotating seal device, wherein the second lubricating oil exceeding the storage capacity of the intermediate shaft of the outer shaft is discharged from the circular opening . The contra-rotating propeller marine propulsion device includes a drive device that is a rotational drive source, an output shaft for an outer shaft and an output shaft for an inner shaft that are provided so that the rotational drive force of the drive device can be rotated concentrically. A power transmission device for outputting,
The second lubricating oil is supplied into the outer shaft intermediate shaft through the meshing portion of the gear coupling, and the second lubricating oil exceeding the storage capacity of the outer shaft intermediate shaft passes through the circular opening. 2. The lubricating structure for a counter-rotating seal device according to claim 1 , wherein the lubricating structure is discharged from a lower meshing portion of the gear coupling. The power transmission device is a gear transmission mechanism, and has a housing that houses the output shaft for the outer shaft and the output shaft for the inner shaft,
The lubricating structure for a counter-rotating seal device according to claim 2 , further comprising a hood that covers the hollow ring and the gear coupling and is detachably attached to the housing and can be divided into a plurality of pieces in the radial direction. The hood communicates with the inside of the housing inside the hood,
The lubricating structure for a counter-rotating seal device according to claim 3 , wherein the second lubricating oil is supplied to the gear coupling from the housing side.

Images