JP2012086641A - Speed reducing and reversing device for ship - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed reducing and reversing device for ships capable of easily executing the maintenance of a PTO (Power Take-Off) shaft.SOLUTION: A gear unit for transmitting the power from a drive source includes an input shaft 31 for advance which receives the power from the drive source, an input gear 32 for advance which is fixed to the input shaft for advance, an input shaft 71 for retreat which extends parallel to the input shaft for advance, an input gear 72 for retreat which is fixed to the input shaft for retreat and engaged with the input gear for advance, an output gear, an output shaft which is fixed to the output gear, a clutch mechanism for transmitting the rotation of the input shaft for advance or the input shaft for retreat to the output gear, a PTO output gear 51 to which the rotational force of the input shaft for advance or the input shaft for retreat is transmitted, and a PTO output shaft 50 which is fixed to the PTO output gear. The PTO output gear and the PTO output shaft are provided outside a housing. An accommodation case 5 for accommodating the PTO output gear is mounted on an outer surface of the housing, and protruded outside from the accommodation case.

Description

The present invention relates to a deceleration reverse rotation device attached to a ship.

  Various types of marine deceleration reverse rotation devices have been proposed. For example, there is one described in Patent Document 1. In the reduction / reverse rotation device described in this document, an input shaft, a gear mechanism, and an output shaft are provided in a housing, and power from a drive source is transmitted in this order to a propeller attached to the output shaft. Further, a PTO (Power take-off) shaft is arranged in the housing so that the rotation of the input shaft is transmitted to the PTO shaft. A generator or the like is connected to the PTO shaft, and the rotation of the input shaft is used for power generation via the PTO shaft.

JP 2010-12832 A

  However, in the above apparatus, since the PTO shaft is disposed in the housing, it is necessary to disassemble the housing in order to perform maintenance of the PTO shaft, and there is a problem that workability is poor and labor is large.

  The present invention has been made to solve the above-described problem, and an object of the present invention is to provide a marine deceleration reverse rotation device that can easily perform maintenance of a PTO shaft.

  A marine speed reduction reverse rotation device according to the present invention includes a gear unit that transmits power from a drive source and a housing that houses the gear unit, and the gear unit is for forward movement that receives power from the drive source. An input shaft, a forward input gear fixed to the forward input shaft, a reverse input shaft extending parallel to the forward input shaft, and fixed to the reverse input shaft and meshes with the forward input gear A reverse input gear, an output gear, an output shaft fixed to the output gear, a propeller connected to the output shaft, and the rotation of the forward input shaft or the reverse input shaft are transmitted to the output gear. A clutch mechanism, a PTO output gear to which the rotational force of the forward input shaft or the reverse input shaft is transmitted, and a PTO output shaft fixed to the PTO output gear. The PTO output shaft is provided outside the housing, and a housing case for housing the PTO output gear is attached to the outer surface of the housing, and the PTO output shaft is rotatably supported by the housing case. And protrudes outward from the storage case.

  According to this configuration, since the PTO shaft and the PTO output gear are arranged in the storage case provided outside the housing, maintenance of the PTO shaft and the like can be performed by removing the storage case without disassembling the housing. It can be carried out. Therefore, the trouble of disassembling the housing can be saved and maintenance can be easily performed. Further, since the PTO shaft is outside the housing, there is no need to provide an installation space for the PTO shaft or a bearing in the housing, and the housing can be downsized. Furthermore, the PTO shaft can be shortened, and the weight of the apparatus can be reduced.

  For example, transmission to the PTO shaft can be performed using either the forward input shaft or the reverse input shaft. For example, when the forward input shaft is used, the forward input shaft protrudes from the housing. The PTO drive gear that meshes with the PTO output gear is fixed to the protruding portion, and the PTO drive gear can be stored in the storage case. In this way, the distance between the forward input shaft and the PTO shaft can be shortened, maintenance becomes easy, and cost can be reduced. The reverse input shaft can be configured as described above.

  Moreover, it can comprise so that lubricating oil may be supplied in a storage case, and it can also connect a storage case and a housing by the communicating path which returns lubricating oil from this storage case in a housing. If it does in this way, lubricating oil can be supplied to the members arrange | positioned in a storage case, for example, a PTO output gear, a PTO drive gear, etc.

  At this time, at least one of the forward input shaft and the reverse input shaft extends in the axial direction and passes through the lubricating oil supply passage through which oil passes, and at least one branching radially outward from the lubricating oil supply passage. Each of the branch paths can be formed. And it can comprise so that the lubricating oil discharged | emitted from a branch path may be supplied in a storage case. Since a plurality of branch paths can be formed, lubricating oil can be supplied to members such as bearings in the housing.

  The clutch mechanism can have various configurations. For example, the forward input shaft is inserted so as to be relatively rotatable, and the forward pinion that meshes with the output gear, and the axial direction of the forward pinion supported in the housing. A pair of first bearings attached at two locations, a forward hydraulic clutch capable of connecting the forward input gear and the forward pinion, and a reverse input shaft are inserted in a relatively rotatable manner, and an output gear Backward-moving pinion that meshes with the rearward-removing pinion, a pair of second bearings that are supported in the housing and attached at two locations in the axial direction of the reverse-traveling pinion, and a reverse-traveling input gear and a reverse-traveling pinion are connectable A clutch, and both the forward pinion and the reverse pinion can mesh with the output gear described above.

  According to the marine deceleration reverse rotation device according to the present invention, maintenance of the PTO shaft can be easily performed.

It is sectional drawing of the deceleration reverse rotation apparatus for ships which concerns on this embodiment. It is a side view of FIG. It is the sectional view on the AA line of FIG. It is the BB sectional view taken on the line of FIG. FIG. 2 is a partially enlarged view of FIG. 1. 1 is a hydraulic circuit diagram of a marine deceleration reverse rotation device according to the present embodiment.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, an embodiment of a marine deceleration reverse rotation device according to the invention will be described with reference to the drawings. 1 is a cross-sectional view of the speed reduction / reversal device, FIG. 2 is a side view of FIG. 1, and FIG. 3 is a cross-sectional view taken along line AA of FIG. In the present specification, the bow side of the hull is referred to as “front” and the stern side is referred to as “rear”. Further, the “left / right direction” or “width direction” means a direction from starboard to port or vice versa.

  As shown in FIGS. 1 to 3, this marine vessel deceleration reverse rotation device has a housing 2 attached to the rear end of the marine vessel body 1, and a gear that transmits power to the propeller in the housing 2. Unit is arranged. The ship body 1 houses an engine (not shown) and a flywheel 11 connected to the rotation shaft of the engine. The forward input shaft 31 is attached to the flywheel 11 via the elastic joint 12 and extends into the housing 2. The forward input shaft 31 protrudes rearward from the rear end portion of the housing 2, and a PTO drive gear 4 that transmits power to a PTO shaft 50 described later is attached to the protruding portion. The protruding portion and the PTO drive gear 4 are covered with a first hydraulic block (storage case) 5. The hydraulic block 5 is detachably attached to the rear end surface of the housing 2, and the oil pumped up by the hydraulic pump 81 from the oil reservoir 83 passes through the first hydraulic block 5 and moves forward as will be described later. It is supplied to the inside of the input shaft 31. This point will be described later. The forward input shaft 31 is supported by a bearing 311 attached to the front end wall of the housing 2 and a bearing 312 attached in the first hydraulic block 5.

  As shown in FIG. 1, the upper part in the housing 2 is divided into two parts, a front storage chamber 212 and a rear storage chamber 213, by an upper partition wall 211. In the forward input shaft 31, the forward input gear 32 is fixed to the portion disposed in the front storage chamber 212, and the forward pinion 33 is disposed in the portion disposed in the rear storage chamber 213. It is attached so that it can rotate freely. That is, the forward pinion 33 can rotate relative to the forward input shaft 31. The front end portion and the rear end portion of the advance pinion 33 are supported by bearings 331 and 332 attached to the upper partition wall 211 and the rear end wall of the housing 2. A forward hydraulic clutch 34 is provided between the forward input gear 32 and the forward pinion 33 to connect the two. The hydraulic clutch 34 is a known wet multi-plate clutch, and includes an inner drum 341 splined to the front end of the forward pinion 33 and an outer drum 342 integrally formed with the forward input gear 32. . A plurality of clutch disks fixed to the inner drum 341 are arranged in gaps between a plurality of pressure plates fixed to the outer drum 342, and these disks and the plates are brought into close contact with each other by pressing of the hydraulic piston. , Power is transmitted.

  An output shaft 6 extending in the front-rear direction is disposed below the housing 2. The rear end portion of the output shaft 6 protrudes from the rear end of the housing 2, and a propeller (not shown) is attached to the protruding portion via a bracket 61. The output shaft 6 is rotatably supported by a thrust bearing 62 provided on the front end wall of the housing 2 and a bearing 63 provided on the rear end wall of the housing 2. An output gear 64 is fixed to the rear portion of the output shaft 6, and the output gear 64 meshes with the forward pinion 33. As a result, power from the engine is transmitted to the propeller.

  As shown in FIG. 2, the housing 2 includes three members arranged in the vertical direction, that is, an upper housing member 21, an intermediate housing member 22, and a lower housing member 23. The upper partition wall 211 at the top of the housing described above is attached inside the upper housing member 21. The lower housing member 23 is formed in a cup shape that accommodates the lower half of the output shaft 6, and the bottom portion is an oil reservoir 83 of lubricating oil. Further, arc-shaped support surfaces for supporting the bearings 62 and 63 are formed on the front and rear end walls of the lower housing member 23, respectively. The intermediate housing member 22 is formed on the frame side where the upper and lower portions are opened, and the lower end portion is formed horizontally so as to be fixed to the lower housing member 23, but the upper end portion is cut obliquely. It is formed as follows. An oblique edge (A-A line) constituting the upper end portion of the intermediate housing member 22 is formed so as to pass through the center of the forward input shaft 31 and the center of the reverse input shaft 71 described later. As shown in FIG. 2, the forward input shaft 31 is positioned substantially at the center in the left-right direction of the housing 2, but the backward input shaft 71 is disposed on the diagonally lower left side of the forward input shaft 31. This is because the reverse pinion 73 attached to the reverse input shaft 71 is engaged with the output gear 64 as described later. In other words, the forward input shaft 31 and the reverse input shaft 71 are each equidistant from the output shaft 6. On the other hand, the PTO shaft 50 is disposed on the opposite side to the reverse input shaft 71 across the forward input shaft 31 in the width direction. However, the forward input shaft 31 is arranged horizontally. This is because, as will be described later, the PTO shaft 50 is not disposed in the housing 2 but is disposed in the first hydraulic block 5 that is attached to the rear end portion of the housing 2 and extends in the width direction. .

  The intermediate housing member 22 will be further described. At the lower end of the intermediate housing member 22, arc-shaped support surfaces are formed on the front and rear end walls, and this support surface forms a circular through hole together with the support surface of the lower housing member 23. And the bearings 62 and 63 are arrange | positioned at this through-hole. As shown in FIG. 3, the intermediate housing member 22 is provided with a lower partition wall 221 extending in the width direction, and the lower partition wall 221 has a front bearing 331, a forward pinion 33 and a reverse pinion 73. An arcuate support surface on which 731 is disposed is formed. The lower partition wall 221 is disposed at a position corresponding to the upper partition wall 211 described above. In addition, arc-shaped support surfaces on which the rear bearings 332 and 732 on the rear side of the forward pinion 33 and the reverse pinion 73 are respectively disposed are formed on the rear portion of the upper end portion of the intermediate housing member 22. The upper partition wall 211 of the upper housing member 21 and the lower partition wall 221 of the intermediate housing member 22 are fixed as shown in FIG. In other words, the upper partition walls 211 and 221 are fixed by the bolts 25 between the two bearings 331 and 731 and at three portions on the side thereof. At this time, since the upper partition wall 211 of the upper housing member 21 has a height, a deep bolt hole 26 is formed in the upper housing member 21.

  Next, the upper housing member 21 will be described. The lower end portion of the upper housing member 21 is cut obliquely so as to be combined with the intermediate housing member 22. An arcuate support surface for supporting the bearings 331, 332, 731, 732 of the forward pinion 33 and the reverse pinion 73 is provided at the lower end portion of the upper partition wall 211 and the rear end portion of the upper housing member 21. Each is formed. The upper housing member 21 is attached with a hydraulic control unit 8 that incorporates a hydraulic circuit that controls clutch hydraulic oil. The hydraulic control unit 8 is equipped with a forward / reverse switching valve 84, a slow fitting valve 85, a relief valve 88, and the like that constitute a hydraulic circuit.

  Next, the reverse gear unit will be described. As shown in FIG. 3, the reverse gear unit is substantially the same as the forward mechanism described above. That is, a reverse input shaft 71 extending in parallel with the forward input shaft 31 is disposed inside the housing 2, and a reverse input gear 72 is fixed to a portion located in the front storage chamber 212. The reverse input gear 72 meshes with the forward input gear 32, and the reverse input gear 72 and the reverse input shaft 71 rotate as a unit by the rotation of the forward input gear 32. The rear end portion of the reverse input shaft 71 protrudes from the housing 2 similarly to the forward input shaft 31, and a hydraulic pump 81 including a gear pump is attached to the protruding portion. The rear end portion of the reverse input shaft 71 and the hydraulic pump 81 are covered with the second hydraulic block 9. Further, a reverse pinion 73 is rotatably inserted in a portion of the reverse input shaft 71 located in the rear storage chamber 213, and a front end portion and a rear end portion of the reverse drive pinion 73 are provided with a bearing 731. , 732 are supported in the housing 2. The reverse pinion 73 meshes with the output gear 64 described above. Further, between the reverse pinion 73 and the reverse input gear 72, a hydraulic clutch 74 similar to the above-described forward clutch is disposed.

  Next, the PTO (Power take-off) and the first hydraulic block 5 will be described. As described above, the first hydraulic block 5 houses the rear end portion of the forward input shaft 31 and the PTO drive gear 4, but further extends in the width direction and meshes with the PTO drive gear 4. 51 is stored. A PTO shaft 50 is fixed to the PTO output gear 51 and protrudes rearward from the first hydraulic block 5. Various devices such as a generator and a winch that are driven by utilizing the rotation can be attached to the PTO shaft 50 protruding rearward from the first hydraulic block 5. In addition, bearings 41 and 42 that support the PTO drive gear 4 and bearings 52 and 53 that support the PTO shaft 50 are disposed at the front end portion and the rear end portion of the first hydraulic block 5, respectively. Further, as shown in FIG. 1, two flow paths of the oil pumped up by the hydraulic pump 81, that is, the forward oil path 8 b and the lubricating oil path 8 e are formed inside the wall of the first hydraulic block 5. ing. The hydraulic oil is supplied from the hydraulic pump 81 through the oil passage inside the casing and the outside passage to the forward oil passage 8b via the joint 251. The forward oil passage 8b communicates with a hydraulic oil supply passage 313 in the input shaft 31, which will be described later, through an opening formed in the rear end portion of the forward input shaft 31, and supplies oil. Yes. Lubricating oil is also supplied to the lubricating oil passage 8 e in the hydraulic block 81 by the hydraulic pump 81. The lubricating oil path 8e communicates with a lubricating oil supply path 314, which will be described later, through an opening formed at the rear end of the forward input shaft 31 from the rear end side further than the forward oil path 8b. Oil is supplied from Although not shown, a similar flow path is formed in the second hydraulic block 9 so that oil is also supplied to the inside of the reverse input shaft 71.

  Next, the flow of the lubricating oil in this gear unit will be described with reference to FIG. FIG. 5 is an enlarged view of the forward input shaft and its vicinity. Here, the forward input shaft 31 will be described as an example. However, since the same structure is provided in the reverse input shaft 71, the description of the reverse input shaft 71 is omitted. First, two oil passages extending in the axial direction are formed inside the forward input shaft 31. One is a hydraulic oil supply path 313 to which hydraulic oil of the hydraulic clutch 34 is supplied, and the other is a hydraulic clutch 34, bearings 331 and 332 of the forward pinion 33, and a rear side of the forward input shaft 31. A lubricating oil supply path 314 supplies lubricating oil to the bearing 312. The lubricating oil supply path 314 is formed with five branch paths extending radially outward. More specifically, the first branch path 3141 extending to the hydraulic clutch 34, the second branch path 3142 extending near the front end of the forward pinion 33, the third branch path 3143 extending near the intermediate portion of the forward pinion 33, and the forward travel A fourth branch path 3144 extending near the rear end of the pinion 33 and a fifth branch path 3145 extending into the first hydraulic block 5 are formed. A plurality of branch paths 3141 to 3145 are provided along the circumferential direction of the forward input shaft 31.

  A receiving portion 225 having an L-shaped cross section is formed along the support surface at the upper end of the lower partition wall 221 of the intermediate housing member 22. The receiving portion 225 is attached to the front storage chamber 212 side, and prevents lubricating oil falling from above from flowing to the storage chamber 212 side and guides it to the bearing 331 side. A receiving portion 215 having a similar structure is also provided along the support surface of the upper partition wall 211 of the upper housing member 21. Accordingly, circular receiving portions 225 and 215 are formed over the entire circumference of the support surface on which the bearing 331 is disposed. Further, the inner drum 341 of the hydraulic clutch 34 is formed with a through hole 3411 at a position corresponding to the second branch portion 3142, and the lubricant discharged from the second branch portion 3142 is passed through the through hole of the inner drum 341. It flows down to the receiving part 225 via 3411.

  The first hydraulic block 5 and the bearing 312 of the input shaft 31 are positioned on the rear end side of the forward pinion 33 with a gap. The lubricating oil discharged from the fourth branch passage 3144 passes through the gap between the forward pinion 33 and the hydraulic block 5 and is supplied to the bearing 332 on the rear end side of the forward pinion 33. The lubricating oil is configured to flow to the bearing 332 side by blocking the rearward path by the hydraulic block 5. Further, the fifth branch passage 3145 supplies lubricating oil into the first hydraulic block 5, and the lubricating oil is supplied to the bearings 41 and 42 of the PTO drive gear 4 and the bearings 52 and 53 of the PTO shaft 50. To supply. The lubricating oil supplied into the first hydraulic block 5 flows into the housing 2 via a communication passage 57 formed below the internal space of the hydraulic block 5. In the housing 2, it flows downward through a flow path 229 formed in the rear end wall of the intermediate housing member 22, lubricates the bearing 63 behind the output shaft 6, and then returns to the oil sump 83. Yes. The communication passage 57 is provided with a throttle 59. When the pressure of the lubricating oil stored in the first hydraulic block 5 exceeds a predetermined level, the throttle 59 is opened to lubricate the housing 2 from the first hydraulic block 5. Oil is flowing.

  Subsequently, the supply of lubricating oil from the third branch path 3143 will be described. The third branch path 3143 is formed near the center in the axial direction of the forward pinion 33. On the inner peripheral surface of the pinion 33, a concave shape extending in the circumferential direction is provided at a position corresponding to the third branch path 3143. An oil reservoir 335 is formed. The oil reservoir 335 is formed with a communication passage 336 penetrating radially outward so that lubricating oil can be supplied to the tooth bottom of the pinion 33.

  Next, the supply of hydraulic oil will be described with reference to FIG. FIG. 6 is a diagram illustrating a hydraulic oil supply circuit of the reduction / reverse rotation device according to the present embodiment.

  As shown in FIG. 6, the pressure oil pumped up from the oil reservoir 83 by the hydraulic pump 81 via the filter 82 passes through the oil supply path 8 a and passes through the forward hydraulic oil path 8 b or through the forward / reverse switching valve 84. It is sent to the reverse hydraulic fluid passage 8c. A shift lever 841 is attached to the forward / reverse switching valve 84, and the spool of the forward / reverse switching valve 84 is moved by operating the shift lever 841, so that the forward / reverse position and the neutral position are switched. Then, by this pressure oil, the forward hydraulic clutch 34 or the reverse hydraulic clutch 74 is connected, and either propulsion rotational force in the front or rear direction is transmitted to the propeller.

  The hydraulic circuit is provided with a loosely fitted valve 85 for preventing the forward or reverse hydraulic clutches 34, 74 from being suddenly connected when the forward / reverse switching valve 84 is switched. And the loose insertion valve 85 is provided on the branch path 8d branched from the oil supply path 8a, and becomes a kind of pressure regulating valve. The branch path 8d is provided with an oil cooler 87 and a relief valve 88 through which the pressure oil that has passed through the loose fitting valve 85 passes, and between the oil cooler 87 and the relief valve 88, each hydraulic clutch 34, A lubricating oil passage 8e through which the lubricating oil after being used at 74 passes is connected. The hydraulic pressure released from the loosely fitted valve 85 to the lubricating oil passage 8e is limited to a predetermined low pressure by the relief valve 88. Further, as described above, the lubricating oil passage 8e is connected to the lubricating oil supply passages 314 and 714 of the forward input shaft 31 and the reverse input shaft 71.

  Next, the operation of this hydraulic circuit will be described. As shown in FIG. 6, when the forward / reverse switching valve 84 is in the neutral position, no pressure oil is supplied to the back chamber of the loosely fitted valve 85. At this time, the spool of the loose insertion valve 85 is largely retracted, and has the same function as the relief valve having a low relief pressure. A part of the pressure oil supplied from the hydraulic pump 81 is released from the loose insertion valve 85 to the lubricating oil passage 8e through the oil cooler 87.

  When the shift lever 841 is operated to switch the forward / reverse switching valve 84 to the forward or reverse position, the hydraulic oil starts to flow into the forward hydraulic fluid passage 8b or the reverse hydraulic fluid passage 8c. At the same time, hydraulic oil is press-fitted into the back chamber of the loose insertion valve 85 through the oil passage. As a result of this press-fitting, the spool of the loose insertion valve 85 moves forward, the relief pressure is gradually increased, the lubricating oil passage 8e is gradually closed, and the forward hydraulic fluid passage 8b or the reverse hydraulic fluid passage 8c is reflected as a reflective action. Is gradually increased. In this way, the clutches 34 and 74 are prevented from being suddenly engaged by gradually increasing the hydraulic pressure. Finally, the clutches 34 and 74 are completely pressed at a high pressure to completely transmit power.

  Next, the operation of the deceleration reverse rotation device configured as described above will be described. First, the power from the engine is transmitted in the order of the forward input shaft 31, the forward input gear 32, the reverse input gear 72, and the reverse input shaft 71, even when the forward / reverse switching valve 84 is in the neutral position. Is spinning. As described above, when the shift lever 841 is disposed at the forward movement position, the hydraulic oil is supplied to the forward hydraulic clutch 34 via the forward / reverse switching valve 84, and the forward input gear 32 and the forward pinion 33 are connected. Is done. Thus, power from the forward input shaft 31 is transmitted to the output gear 64 via the forward pinion 33, and the propeller rotates in the forward direction. At the same time, the rotation of the forward input shaft 31 is transmitted to the PTO shaft 50 via the PTO drive gear 4 and the PTO output gear 51, and the PTO shaft 50 rotates. Thereby, a device such as a generator attached to the PTO shaft 50 is driven. At this time, since the hydraulic oil is not supplied to the reverse hydraulic clutch 74, no power is transmitted to the reverse pinion 73, and only the output gear 64 is rotated. On the other hand, when the shift lever 841 is disposed at the reverse drive position, hydraulic oil is supplied to the reverse hydraulic clutch 74 via the forward / reverse switching valve 84, and the reverse input gear 72 and the reverse pinion 73 are connected. Thereby, power is transmitted from the reverse input shaft 71, the reverse pinion 73 rotates, and the propeller rotates in the reverse direction. At this time, since the hydraulic oil is not supplied to the forward hydraulic clutch 34, power is not transmitted to the forward pinion 33, and only the output gear 64 is rotated. However, since the forward input shaft 3 continues to rotate, the PTO shaft 50 rotates as long as power from the engine is transmitted.

  Subsequently, oil supply will be described. When the reverse input shaft 71 rotates, the hydraulic pump 81 attached to the rear end portion is also driven to suck up oil from the oil reservoir 83. In addition to being supplied to the above-described hydraulic oil circuit, this oil is also supplied from the flow paths of the hydraulic blocks 5 and 9 to the lubricating oil supply paths of the input shafts 31 and 71. The oil supplied to the lubricating oil supply path is supplied to the tooth bottoms of the pinions 33 and 73, the bearings, the hydraulic blocks 5 and 9 through the branch paths, and acts as lubricating oil.

  As described above, according to the present embodiment, the PTO shaft 50 and the PTO output gear 51 are arranged in the first hydraulic block 5 provided outside the housing 2, so that the housing 2 can be disassembled without disassembling the housing 2. By removing the first hydraulic block 5 from the housing 2, maintenance of the PTO shaft 50 and the like can be performed. Therefore, the trouble of disassembling the housing 2 can be saved and maintenance can be easily performed. Further, since the PTO shaft 50 is outside the housing 2, it is not necessary to provide an installation space for the PTO shaft 50, a bearing, or the like inside the housing 2, and the housing 2 can be downsized. Furthermore, the PTO shaft 50 can be shortened, and the weight of the apparatus can be reduced.

  As mentioned above, although one Embodiment of this invention was described, this invention is not limited to the said embodiment, A various change is possible unless it deviates from the meaning. For example, in the above-described embodiment, the PTO shaft 50 is driven by projecting the rear end portion of the forward input shaft 31 from the housing 2 and disposing it in the first hydraulic block 5. Can be disposed in the same hydraulic block as the PTO shaft 50 to drive the PTO shaft 50. In the above embodiment, the PTO shaft 50 is arranged in the first hydraulic block 5, but the PTO shaft 50, the PTO output gear 51, a transmission gear from any one of the input shafts, etc. are used as the storage case. If it can be accommodated, its form is not particularly limited.

2 Housing 31 Advance input shaft 32 Advance input gear 33 Advance pinion 34 Advance hydraulic clutch 4 PTO drive gear 5 First hydraulic block (storage case)
50 PTO shaft 51 PTO output gear 6 Output shaft 64 Output gear 71 Reverse input shaft 72 Reverse input gear 73 Reverse pinion 74 Reverse hydraulic clutch

Claims (5)

A gear unit for transmitting power from the drive source;
A housing for housing the gear unit,
The gear unit is
A forward input shaft that receives power from the drive source;
A forward input gear fixed to the forward input shaft;
A reverse input shaft extending parallel to the forward input shaft;
A reverse input gear fixed to the reverse input shaft and meshing with the forward input gear;
Output gear,
An output shaft fixed to the output gear;
A propeller connected to the output shaft;
A clutch mechanism for transmitting the rotation of the forward input shaft or the reverse input shaft to the output gear;
A PTO output gear to which the rotational force of the forward input shaft or the reverse input shaft is transmitted;
A PTO shaft fixed to the PTO output gear;
With
The PTO output gear and the PTO shaft are provided outside the housing,
A storage case for storing the PTO output gear is attached to the outer surface of the housing,
The marine deceleration reverse rotation device, wherein the PTO shaft is rotatably supported by the storage case and protrudes from the storage case. The forward input shaft or the reverse input shaft protrudes from the housing, and a PTO drive gear that meshes with the PTO output gear is fixed to the protruding portion.
The marine deceleration reverse rotation device according to claim 1, wherein the PTO drive gear is stored in the storage case. It is configured so that lubricating oil is supplied into the storage case,
3. The marine deceleration reverse rotation device according to claim 1, wherein the storage case and the housing communicate with each other through a communication path that returns the lubricating oil from the storage case into the housing. In at least one of the forward input shaft and the reverse input shaft, there is a lubricating oil supply passage extending in the axial direction and through which oil passes, and at least one branch branched radially outward from the lubricating oil supply passage. Roads are formed,
The marine vessel deceleration reverse rotation device according to claim 3, wherein the lubricating oil discharged from the branch path is configured to be supplied into the storage case. The clutch mechanism is
The forward input shaft is inserted so as to be relatively rotatable, and the forward pinion meshes with the output gear; and
A pair of first bearings supported in the housing and attached at two locations in the axial direction of the advance pinion;
A forward hydraulic clutch capable of connecting the forward input gear and the forward pinion;
The reverse input shaft is inserted so as to be relatively rotatable, and the reverse pinion meshes with the output gear;
A pair of second bearings supported in the housing and attached at two locations in the axial direction of the reverse pinion;
A reverse hydraulic clutch capable of connecting the reverse input gear and the reverse pinion;
With
The marine deceleration reverse rotation device according to any one of claims 1 to 4, wherein the forward pinion and the reverse pinion are both meshed with the output gear.

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