JP3913262B1 - Oil supply device for rotating shaft - Google Patents

Abstract

In a lubrication device for a rotating shaft such as a thruster, when high pressure oil is fed from the propeller shaft end to a servo cylinder at the other end of the propeller shaft from the ship side, the amount of oil leakage can be reduced and lubrication can be efficiently performed. Is simplified, processing is easy, and cost can be reduced.
A portion of a knot rod 14 protrudes in a radial direction within a hollow shaft portion 23 slightly closer to the tip than a small diameter portion of a base end of a propeller shaft 8, and the shaft center portion of the knot rod 14 is projected from the outer peripheral surface of the base. A distal end that is drilled in the radial direction, passes through an axial center portion and reaches the distal end of the piston 13, and is connected to a distal-side radial oil passage 31 e that is drilled in the oil distribution member 31. The side oil passage 22 is formed in the distal end side chamber 23z of the hollow shaft center portion, and the base-side L-shaped oil passage 31f formed in the oil supply / distribution member 31 is connected to the hollow shaft center portion via the radial hole 29 of the propeller shaft 8. The base end side chambers 23 x communicated with each other, and the base end side chambers 23 z communicated with the radial holes 22 c of the propeller shaft 8.
[Selection] Figure 1

Description

  The present invention relates to a fueling device for refueling a thruster such as a side thruster or an azimuth thruster from a ship. More specifically, the present invention relates to a hydraulic cylinder chamber (servo cylinder chamber) of a variable pitch propeller lab attached to the tip of a propeller shaft. The present invention relates to an oil supply device for a rotary shaft capable of supplying front and rear high pressure oil.

  Conventionally, as shown in FIGS. 6 and 7, an oil supply device 50 for supplying pressure oil from the ship side to the servo cylinder chamber of the side thruster is mounted on the outer peripheral surface of the base end portion of the propeller shaft 8 and divided into front and rear. The outer peripheral surfaces of the two sleeves 51 and 51 are covered with a cylindrical cover body 52 and fixed to the gear case 3 with bolts 53 with an outward flange 52a provided integrally with the cover body 52. Three seal rings 58 are arranged between the inner peripheral surface of the split sleeve 51 and the outer peripheral surface of the propeller shaft 8, and O-rings 59 for preventing leakage of pressure oil are incorporated in the outer peripheral surfaces of the front and rear split sleeves 51. ing. Further, the pressure oil supply pipe 54 suspended from the Vessel A side has a structure in which the sleeve 51 is extended rearward in the axial direction, and the positions of the connection holes 52b and 51b of the cover body 52 and the sleeve 51 are slightly biased rearward. The bent pipe shape, that is, bent downward at the lower part, is screwed into the connection hole 52b of the cover body 52 via the pipe joint 55 and is secured. Further, the supply / discharge oil passages 60 and 61 for supplying the pressure oil to the servo cylinder chambers 12a and 12b provided at the tip of the propeller shaft 8 and returning the pressure oil in the servo cylinder chambers 12a and 12b have a transition through the hollow portion. The shaft 14 is provided near the outer periphery of the shaft 14 and the propeller shaft 8, but both oil passages extend from the base end to the tip, and the length of each oil supply / discharge oil passage 60, 61 is the entire length of the propeller shaft 8. It is close. The base end side of the sleeve 51 is supported by an annular holding plate 56 and fixed to the rear end of the cylindrical cover body 52 by a bolt 57, whereby the divided sleeves 51 and 51 are held and positioned. . The seal ring 58 is held by the split sleeve 51 and is in a floating state.

  Although there is no prior art in which oil is supplied from the axial end of the rotating shaft as described above, as a prior art related to an oil supply device for supplying oil to the central shaft oil passage of the rotating shaft from the middle of the rotating shaft, for example, marine two In the lubricating oil supply structure of the heavy reversing propeller, within the bearing surface range in the axial direction of the inner propeller shaft at the position where the oil drainage hole is provided in the shaft core of the inner propeller shaft and a plurality of bearings for supporting the inner propeller shaft are provided. An oil passage that communicates the outer surface of the inner propeller shaft and the oil drain hole is provided, and a plurality of oil supply grooves that communicate with the gap between the outer propeller shaft and the inner propeller shaft are provided in the axial direction of the outer surface of the bearing. An oil supply hole that communicates with the inner surface of the bearing from the groove and supplies lubricating oil into the range of the bearing surface of the outer surface of the inner propeller shaft is provided, and the position of the oil supply hole and the oil passage is set in the axial direction of the inner propeller shaft. It is provided so as to shift Fueling device structure for supplying lubricating oil has been proposed inward propeller shaft exterior surface (e.g., see Patent Document 1).

As another prior art, in an annular oil supply device for a rotary shaft for supplying oil into the rotary shaft or the central shaft oil passage of the rotary shaft from midway in the axial direction of the rotary shaft, The housing is provided to allow movement in the radial direction, the axial direction, and the circumferential direction, and the axial length is made longer than the radial thickness in the annular space with the rotating shaft on the inner peripheral side of the housing. The seal ring is interposed while allowing movement in all directions, and O-rings are attached to both ends of the outer peripheral surface of the seal ring in a gap with the inner peripheral surface of the housing, and the housing and the seal ring are connected in series. When a high-pressure oil is supplied from the outside of the housing to the inside of the rotary shaft or the central shaft oil passage of the rotary shaft, the high-pressure oil is supplied to the housing inner peripheral surface and the seal ring. An oil supply device has been proposed in which the gap between the inner peripheral surface of the seal ring and the outer peripheral surface of the rotary shaft is reduced by guiding the seal ring to the outer peripheral surface and pressing and deforming the seal ring toward the inner peripheral surface. (For example, refer to Patent Document 2).
JP-A-6-239294 (page 3 and FIGS. 1 to 3) JP-A-10-115399 (pages 3 to 5 and FIGS. 1 to 4)

However, the conventional oil supply apparatus described above and the oil supply apparatuses described in Patent Documents 1 and 2 have the following disadvantages. That is,
1) It is necessary to provide an oil supply / discharge oil passage on the outer peripheral side separately from the hollow shaft center of the propeller shaft. However, the length of the oil supply / discharge oil passage on the outer peripheral side is almost the same as the total length of the propeller shaft. This requires skill, takes time and increases costs.

  2) Since pressure oil is supplied and discharged from the base end of the propeller shaft, high accuracy is required for the finished dimensions and processing of the outer peripheral surface on which the oil distribution member is mounted. However, since the propeller shaft itself is large and has a long overall length, it is difficult to realize even if high precision machining and assembly are required at the base oil supply shaft.

  3) In the thruster that is the subject of the present invention, the pressure of the pressure oil introduced in response to the miniaturization has become very high from about 4 MPa to around 15 MPa. Since a curved pipe was used for the supply piping, there was a risk of bending due to a buckling load caused by high pressure oil. Even if bending does not occur, the deformation of the pipe causes the center position to shift back and forth above and below the pipe, so that an excessive pressing load acts on the oil supply device main body. In addition, the number of parts is large and it takes a long time to process and assemble the parts. In addition, since the double structure (in the radial direction) of the oil supply cover and split sleeve is adopted, the structure is complicated and the length of the components is relatively long. Since the outer diameter of the fuel tank is considerably large, the entire fueling device is enlarged, and the size of the thruster is reduced.

  4) Excessive load that mainly presses the three seal rings arranged on the inner peripheral surface side of the two split sleeves against the outer peripheral surface of the propeller shaft acts on each split sleeve, so that the contact portion of the seal ring wears out. Cheap. In addition, since the sleeve divided into two is used, it has low rigidity and is easily deformed, so that the gap increases, and there is a possibility that a gap is formed in the joint surface between the divided sleeves, and oil leaks from there. is there. Furthermore, for the same reason, the annular space (the radial dimension thereof) formed between the sleeve and the propeller shaft tends to be non-uniform.

  5) The prior arts described in Patent Documents 1 and 2 both relate to a variable pitch propeller oil supply device, and the structure of the oil supply device arranged at the end of the propeller shaft, like the thruster targeted by the present invention, is the structure. Is different.

  The present invention has been made in view of the above points, and in a rotating shaft oil supply device such as a thruster, the accuracy of processing and assembly can be improved, and high-pressure oil is supplied from the propeller shaft end to the propeller shaft other end side. It is an object to reduce the amount of oil leakage when supplying oil to the cylinder, to efficiently supply oil, to simplify the structure, to facilitate processing, and to reduce costs.

In order to solve the above-mentioned problems, the oil supply device for a rotating shaft according to the present invention includes: a) a variable pitch propeller boss provided at a tip of a hollow propeller shaft in a gear case, and a propeller boss in the propeller shaft from a base end portion of the propeller shaft. A rotary shaft oil supply device for supplying oil into the servo cylinder chamber via an oil supply distribution member, and b) reducing the diameter of the hollow shaft center portion of the propeller shaft at the base end portion compared to the front end side thereof, A knotting rod whose tip is integrally connected to a piston disposed in the servo cylinder chamber is inserted into the hollow shaft center portion of the propeller shaft from the tip side and penetrated to the base end side to project a part thereof. An annular groove is formed on the inner peripheral surface of the base end small diameter portion of the hollow shaft center portion, a seal ring is interposed, and the propeller pitch is changed by sliding the same rod rod in the axial direction via the piston. Configure to C) A portion of the knot rod is bulged in a radial direction in a hollow shaft portion slightly closer to the tip than the small diameter portion of the base end, and an annular groove is formed on the outer circumferential surface of the bulged annular piston portion. A seal ring is interposed, and the inside of the hollow shaft portion is separated into a distal end side chamber and a proximal end side chamber with the annular piston portion as a boundary. A feed oil discharge passage extending through the piston to the tip of the piston, and d) a tip-side oil passage connected to a tip-side radial oil passage bored in the oil distribution member is formed on the hollow shaft center portion. An L-shaped oil passage on the proximal end side bored in the oil supply / distribution member is communicated with the proximal end chamber of the hollow shaft portion, and the proximal end chamber is connected to the radial hole of the knotting rod. communicated, e) Floating a substantially cylindrical oil distribution member to the proximal end outer peripheral surface of the propeller shaft The oil distribution member is positioned so as to allow movement in all directions within a certain range, and f) project both sides of the outer peripheral surface of the oil distribution member in the radial direction, and Insert the lower end of the pressure oil supply pipe consisting of a pair of straight pipes (straight pipes) without a bend from the side of the ship. A distal-end radial oil passage communicating with the distal-end oil passage from the connection hole portion and a proximal-side L-shaped oil passage communicating with the proximal-end oil passage from the other connection hole portion are provided to the oil supply distribution member, respectively. It is characterized by being drilled .

  According to the oil supply device for a rotating shaft having the above configuration, it is necessary to provide a pair of long oil passages for supplying and discharging oil between the tip end and the base end portion of the propeller shaft, but one uses the hollow portion of the hollow propeller shaft. In addition, since the oil passage is made into the oil passage with the gap rod and the oil passage communicating with the oil passage is formed with the radial hole only on the base end side of the propeller shaft, it is long in the narrow portion of the propeller shaft as in the prior art. It is not necessary to process the oil passage, the processing becomes easy and the cost can be reduced.

If comprised as mentioned above , the structure will be simplified as an oil supply / distribution member having a substantially cylindrical shape, and all directions (axial direction and circumferential direction) with respect to the base end of the propeller shaft (opposite to the propeller boss) It is mounted so as to allow the movement of the oil within a certain range (in a floating state), so that the gap between the inner peripheral surface of the oil distribution member and the outer peripheral surface of the propeller shaft end is properly maintained over the entire circumference, about 15 MPa Even when supplying high-pressure oil, the amount of oil leakage can be reduced, the length of the oil distribution member can be shortened, and a straight pipe can be used for the pressure oil supply pipe from the ship side. The supply side is free from the risk of bending pressure (surface pressure acting) causing deformation of the pressure oil supply pipe by shifting the center position at the top and bottom of the pipe as in the past. Even if high-pressure oil is applied to Therefore, the oil supply distribution member does not have a pressing force due to high pressure oil, and the oil pressure distribution pipe does not have a pressing force due to the hydraulic pressure in the hydraulic circuit. Does not act, so the propeller shaft will not seize during rotation.

As described in claim 2, the proximal end portion of the propeller shaft that covered state of the oil supply distribution member, separate from the main body portion of the tip side propeller shaft, has a small outer diameter compared to the body portion circle It is formed as a tubular oil supply shaft, and an outward flange is integrally provided near the oil supply shaft tip, and the flange can be bolted to the base end surface of the main body portion to connect the oil supply shaft.

  With this configuration, unlike the processing of fine oil supply passages on a large propeller shaft, the oil passage is processed on a shaft dedicated to oil supply with a relatively small diameter and small size, so high-precision machining is possible. As a result, oil leakage and the like are less likely to occur, which is suitable for supplying high-pressure oil.

According to a third aspect of the present invention, it is preferable to line white metal on the inner peripheral surface of the oil supply / distribution member.

  By configuring in this way, the white metal has good conformability, the gap between the outer diameter of the propeller shaft end and the oil distribution member can be appropriately reduced, the contact pressure capability is increased, and the seizure prevention capability is increased. improves.

The oil supply device for a rotating shaft according to the present invention has the following excellent effects. That is,
-The oil passage in the longitudinal direction provided on the propeller shaft can be greatly shortened compared to the conventional one, processing becomes easier, and production costs can be reduced.

  ・ The structure of the oil distribution member, which is the main part of the oil supply device, is simple, the length is shorter than the conventional members, and it is mounted in a floating state around the end of the propeller shaft. The amount can be minimized.

  -Since a straight pipe (straight pipe) can be used for the pressure oil supply pipe, it is easy to manufacture, and even if high pressure oil of around 15 MPa is supplied, there is no risk of deformation load acting.

  -Since the push-down load from the pressure oil supply pipe does not act on the oil distribution member, there is no possibility that seizure will occur during the rotation of the propeller shaft.

  ・ Because the oil passage is processed into a short shaft with a relatively small diameter and small and lightweight dedicated for oil supply, high-precision processing and assembly are different from processing a fine oil supply passage on a large propeller shaft. It can be easily performed, oil leakage and the like are less likely to occur, and is suitable for supplying high-pressure oil.

  BEST MODE FOR CARRYING OUT THE INVENTION The best mode for carrying out a rotary shaft oiling apparatus according to the present invention will be described below with reference to the drawings.

  FIG. 1 is an overall schematic longitudinal sectional view showing a side thruster equipped with an embodiment of an oil supply apparatus of the present invention, FIG. 2 is an enlarged longitudinal sectional view of a part of FIG. 1, and FIG. 3 is a pair of pressure oil supply pipes ( It is a longitudinal cross-sectional view which shows the decomposition | disassembly state of a straight pipe), and a longitudinal cross-sectional view which shows the assembly state.

  The side thruster 1 is installed near the bottom of the main ship A such as a container ship or the bottom of the hull. In this example, the side thruster 1 is installed downward from the bottom of the main ship A as shown in FIG. The upper end of a gear case 3 having a substantially L-shaped cross section is fixed to the upper surface of the cylindrical duct 2, and the drive shaft 6 extending downward from the ship A side can be rotated into the gear case 3 by a pair of upper and lower bearings 4, 5. It is supported by. A bevel gear 7 is integrally provided at the lower end portion of the drive shaft 6, and a hollow propeller shaft 8 having a bevel gear 9 meshing with the bevel gear 7 is integrally provided in the middle of the longitudinal direction inside the gear case 3 by a pair of left and right bearings 10 and 11. Is rotatably supported. The propeller shaft 8 is integrally provided with an outward flange plate 8a at the tip, and the flange plate 8a is arranged in the vertical direction so as to close the tip opening 3a of the variable pitch propeller 12 so that the variable pitch propeller 12 is integrated. It is mounted for rotation. A cylindrical seal housing 16 is rotatably mounted on the outer peripheral surface of the propeller shaft 8 behind the flange plate 8a via a plurality of seal rings 17 from the base end portion of the seal housing 16. A flange 16 a integrally formed outward is in contact with the tip side bearing support portion 3 b of the gear case 3.

  The interior of the propeller boss 12 is formed in servo cylinder chambers 12a and 12b. A piston 13 is slidably arranged in the servo cylinder chambers 12a and 12b in the front-rear direction, and a knot rod 14 integrally connected to the piston 13 is provided. The hollow shaft center part 23 of the propeller shaft 8 is penetrated and the base end part 14b is protruded. An O-ring 18 is attached around the piston 13. Around the propeller boss 12, a plurality of variable propeller blades 15 are arranged at equal intervals in the circumferential direction, and each variable propeller blade 15 is configured to be a variable pitch propeller capable of changing the pitch angle by turning around the central axis in the radial direction. Has been. That is, as the piston 13 slides in the front-rear direction, the variable propeller blades 15 are simultaneously turned in one direction via the crank pin ring 19 to change the pitch angle. Each propeller blade 15 receives a rotational force from a drive shaft 6 that is rotated by a drive device (not shown) provided on the side of Vessel A to the propeller shaft 8 via bevel gears 7 and 9 and rotates together with the propeller boss 12. .

  On the other hand, the pitch angle of each propeller blade 15 is changed by supplying high-pressure oil to the servo cylinder chamber 12a or 12b from the Vessel A side, and the piston 13 slides in a specific direction (forward or backward), and the servo cylinder chamber 12a or 12b. The internal pressure oil is returned (discharged) to an oil tank (not shown) in Vessel A, which is performed via the oil supply device 20 according to the embodiment of the present invention.

  Here, the fueling device 20 will be described in detail.

  As shown in FIGS. 1 to 3, a supply / discharge oil passage 21 is continuously formed in the shaft center portion from the base portion of the transition rod 14 to the tip of the piston 13, and the shaft center portion extends from the outer peripheral surface of the base portion of the transition rod 14. A plurality (2 to 4) of supply / discharge oil passages 21 a are formed in the radial direction toward the supply / discharge oil passage 21. Further, a space between the inner peripheral surface of the hollow shaft center portion of the propeller shaft 8 and the outer peripheral surface of the knot rod 14 is formed in the supply / discharge oil passage 23, and the supply / discharge oil passage 23 of the hollow shaft center portion from the outer peripheral surface of the base end portion of the propeller shaft 8. A continuous oil supply / discharge oil passage 22 (22a, 22b, 22c) is formed in the radial direction, the axial direction, and the radial direction. An O-ring 24 is provided between the outer peripheral surface of the base end portion 14b of the variable rod 14 and the inner peripheral surface of the base end portion 23y whose diameter is reduced compared to the front end side in the oil supply / discharge passage 23 of the hollow shaft center portion of the propeller shaft 8. Is intervening. Further, a part of the outer peripheral surface bulges radially in the vicinity of the base end portion of the knot rod 14, and an O-ring 25 is provided between the swelled annular piston portion 14 a and the inner peripheral surface of the supply / discharge oil passage 23. Is intervening. The supply / discharge oil passage 23 of the piston shaft 8 is divided into a base end side oil passage 23x and a front end side oil passage 23z with the annular piston portion 14a (more precisely, the O-ring 25) as a boundary. In a state in which the knot rod 14 is slid to the tip end as much as possible, the supply / discharge oil passage 22 (22c) to the tip side oil passage 23z is slightly closer to the tip than the position of the annular piston portion 14a (more precisely, the O-ring 25). The position of the annular piston portion 14a (to be precise, the O-ring 25) is located on the distal side of the O-ring 24 in a state where the communicating portion (mouth) is provided and moved to the maximum proximal side. . A radial hole 29 that communicates with the base end side oil supply / discharge passage 23 x is provided on the base end side of the supply / discharge oil passage 22 of the propeller shaft 8.

  A substantially cylindrical oil distribution member 31 is allowed to move in all directions (axial direction and circumferential direction) in a floating state on the outer peripheral surface of the end portion (base end side) having the smallest outer diameter in the propeller shaft 8. It is attached to. Further, as shown in FIG. 3, a pair of left and right pressure oil supply pipes 32, 32 is provided, and each pressure oil supply pipe 32 is a straight pipe (straight) pipe without bending, and an outward flange 32a is provided at the upper end. In addition, a large-diameter oil supply hole 34 is continuously formed in the upper end portion of the gear case 3 and the upper end portion of the duct 2 in the vertical direction, and a small-diameter through hole 35 is formed in the lower gear case 3. The inner diameter of the oil supply hole 34 is slightly larger than the outer diameter of the flange 32 a, and the inner diameter of the through hole 35 is slightly larger than the outer diameter of the pressure oil supply pipe 32. Each pressure oil supply pipe 32 is inserted downward from the oil supply hole 34 and can be moved up and down, and is suspended by the upper end flange 32 a being engaged with the stepped portion 35 a at the upper end of the through hole 35. A pressure oil supply pipe 36 from the ship A is connected to the upper end of the oil supply hole 34 via a pipe joint 37. Further, the height of the oil supply hole 34 is set so that the lower end portion of the pressure oil supply pipe 32 is completely pulled out from a connection hole 31b of the oil supply distribution member 31 described later, so that the oil supply distribution member 31 is opposite to the variable pitch propeller boss 12. It is set so that it can be disassembled.

  The lower end of each pressure oil supply pipe 32 is closed, and this closed portion 32b is formed in a bulging portion that bulges in the radial direction. An annular groove 32c is formed around the upper portion of the closed portion 32b, and a radial hole is formed. 32 d communicates with a passage 32 e in the pressure oil supply pipe 32. Further, the upper portion of the annular groove 32c of the pressure oil supply pipe 32 is formed as a bulging portion 32f, and a stepped portion 32g is formed at the upper end of the bulging portion 32f.

  4 and 5 show an oil supply device 20 'according to another embodiment of the present invention. As shown in both drawings, the proximal end portion of the propeller shaft 8 on which the oil supply / distribution member 31 is mounted is used as the front-side propeller. A substantially circular oil supply shaft 26 having a smaller outer diameter than that of the main body portion 8 ′ is formed separately from the main body portion 8 ′ of the shaft 8, and an outward flange 26 a is provided near the tip of the oil supply shaft 26. Projected together. On the other hand, a recess 8a is provided in the central portion of the base end surface of the main body portion 8 'of the propeller shaft 8, and the inner diameter of the recess 8a is formed slightly larger than the outer diameter of the distal end portion 26b of the oil supply shaft 26. The front end portion 26b is inserted into the recess 8a, and at the same time the flange 26a is in contact with the base end surface of the main body portion 8 ', the flange 26a is fixed with the bolt 27, and the oil supply shaft 26 is fixed to the propeller shaft main body portion 8. It is connected to '. A constant gap is provided between the tip of the oil supply shaft 26 and the inner bottom of the recess 8 a, and the gap 8 b is configured as a radial oil passage (22 c) that constitutes a part of the oil supply / discharge oil passage 22. Further, an O-ring 28 is interposed between the outer peripheral surface of the tip end portion 26b and the inner peripheral surface of the recess 8a.

  On the other hand, as shown in FIG. 5, the oil supply / distribution member 31 is partially protruded from the outer peripheral surface to both sides, and a connecting hole portion 31 b penetrating in the vertical direction is formed in each of the protruding portions 31 a. The lower end portion of the pressure oil supply pipe 32 is fitted in each connection hole portion 31b, and O-rings 38 and 39 are interposed vertically with the annular groove 32c interposed therebetween. The substantially U-shaped jumping prevention plate 40 is screwed to the upper surface of the protruding portion 31a with the stepped portion 32g being locked. Further, a white metal 41 is lined on the inner peripheral surface of the oil supply / distribution member 31, and two front and rear annular grooves 31c and 31d are formed at positions corresponding to the oil supply / discharge oil passages 22a and 29 in the radial direction of the oil supply shaft 26, respectively. ing. Further, in the left and right connecting hole portions 31b, as shown in FIG. 5, radial holes 31e or L-shaped holes 31f are respectively drilled, and the L-shaped holes 31f are formed by the annular groove 31d and the propeller shaft 8 or the oil supply shaft 26. The base end side supply / discharge oil passage 29 is communicated with the base end side supply / discharge oil passage 23x, and the radial hole 31e passes through the annular groove 31c and the propeller shaft 8 or the supply / discharge oil passage 22 of the oil supply shaft 26. It communicates with the distal end side oil supply / discharge passage 23z.

  Further, as shown in FIG. 2 or FIG. 4, a part on the lower surface side of the oil supply / distribution member 31 protrudes downward to form the positioning piece 31j. A through hole 31k is provided at the center of the positioning piece 31j, and a positioning pin 42 with a head 42a having a diameter smaller than the opening diameter is loosely fitted into the through hole 31k, and is fixed to the base end side bearing support portion 3c. ing. With this configuration, the oil supply / distribution member 31 can slide within a certain range in the axial direction and the circumferential direction with respect to the propeller shaft 8 and can also move in the radial direction, and the outer peripheral surface of the end portion of the propeller shaft 8 and the white metal 41. The gap is maintained almost uniformly over the entire circumference.

  As described above, the oil supply device 20 that is a characteristic part of the present invention is configured. In addition, the base end of the lever 43 is attached to the end of the base end side protruding portion 14b of the transition rod 14, and the lever 43 is attached to the tip of the lever 43. The wire or chain 44 with one end fixed is guided to the Vessel A side via the upper and lower guide sprockets 45 and 46, and urged toward the Vessel A side by the spring 47. As a result, the movement amount relative to the reference position in the axial direction of the variable shaft 14 can be detected on the side of the ship A via the chain 44, that is, the pitch angle of the variable propeller blade 15 of the variable pitch propeller is fed back.

  Next, how to use the fueling device 20 of the present embodiment having the above-described configuration will be described.

  As shown in FIG. 1, the variable propeller blade 15 of the variable pitch propeller receives a driving force from the side of the ship A and the driving shaft 6 rotates, and is transmitted to the propeller shaft 8 via the bevel gears 7 and 9, so that the propeller shaft When 8 rotates, it rotates in the duct 2 and generates thrust.

  On the other hand, the pitch angle of each variable propeller blade 15 is changed by supplying high-pressure oil from the ship A side through one pressure oil supply pipe 32 and supplying the radial holes 31e of the oil supply distribution member 31, the propeller shaft 8 or the oil supply shaft 26. The oil is supplied to the servo cylinder chamber 12b behind the piston 13 through the oil discharge passage 22, the distal end side oil supply / discharge passage 23z, the outer peripheral surface of the variable rod 14 and the oil supply / discharge passage 23 of the hollow shaft center of the propeller shaft 8. As a result, the piston 13 slides in the tip direction (forward), and each variable propeller blade 15 turns about the radial axis to change the pitch angle. At this time, the pressure oil on the front end side in the servo cylinder chamber 12a passes through the supply / discharge oil passage 21, the supply / discharge oil passage 29 of the propeller shaft 8 or the oil supply shaft 26, and the L-shaped hole 31f to supply the other pressure oil. It is discharged from the pipe 32. Further, the change of the pitch angle of each variable propeller blade 15 in the reverse direction is such that the high pressure oil from the Vessel A side passes through the other pressure oil supply pipe 32, and the shaft centers of the L-shaped holes 31 f and 29 and the variable rod 14 are changed. By being supplied to the servo cylinder chamber 12a in front of the piston 13 through the supply / discharge oil passage 21, the piston 13 slides in the proximal direction, and each variable propeller blade 15 pivots in the opposite direction around the radial axis. The pitch angle changes. At this time, the pressure oil in the servo cylinder chamber 12b is discharged from one of the pressure oil supply pipes 32 passing through the front end side supply / discharge oil passages 23z, 23z, the supply / discharge oil passage 22 and the radial hole 31e.

  By the way, in the oil supply device 20 of the present embodiment, the distal end side 23z and the proximal end side are formed by the piston portion 14a formed by expanding the supply / discharge oil passage 23 of the hollow shaft center portion of the propeller shaft 8 on the proximal portion side of the shift rod 14. Since the propeller shaft 8 is provided with a short oil supply / discharge oil passage 22 communicating with the base end side oil supply / discharge oil passage 23z, the long oil supply / discharge oil passage as in the conventional case is processed. There is no need, the structure is simplified and the cost is reduced. In addition, since the structure is simplified by using the substantially cylindrical oil supply / distribution member 31, the position of the connection hole 31b is moved to the tip side as compared with the conventional device, so that a pair of left and right pressure oil is supplied. A straight pipe can be used for the pipe 32. Further, even if a pressing force by high pressure oil acts on each pressure oil supply pipe 32 as shown in FIG. 3 by making the connection hole portion 31b a through hole, the pressing force does not act on the oil supply distribution member 31. Further, the connection structure between the lower end portion of the pressure oil supply pipe 32 and the connection hole portion 31b of the oil supply distribution member 31 is devised.

  On the other hand, in the fueling device 20 ′ according to the second embodiment, the fueling shaft 26 is separated from the propeller shaft 8 and integrally connected to the main body portion 8 ′ as shown in FIGS. The processing of the supply / discharge oil passage 22 formed in the above becomes easier and the accuracy of processing and assembly is improved. Further, even if high pressure oil is supplied to the base end portion of the propeller shaft 8 or the outer peripheral surface of the oil supply shaft 26, no pressing force acts on the oil supply distribution member 31 via the pressure oil supply pipe 32. 31 is held in a floating state, and the gap between the base end portion of the propeller shaft 8 or the outer peripheral surface of the oil supply shaft 26 is always properly maintained, and the propeller shaft 8 or the oil supply shaft 26 does not seize during rotation.

  As mentioned above, although one Example was shown about the oil supply apparatus of this invention, it can implement as follows.

  Any apparatus that supplies oil to a rotating shaft such as a propeller shaft from one end can be applied without being limited to a thruster oil supply apparatus.

  Needless to say, the present invention can be applied not only to the side thruster oil supply device but also to the azimuth thruster oil supply device.

  The oil supply device of the present invention is suitable for a thruster that changes the pitch of a variable pitch propeller by supplying high-pressure oil of around 15 MPa, but can also be applied to a conventional oil supply device that supplies medium-pressure oil of about 4 to 10 MPa. .

  -Instead of lining the white metal 41 on the inner peripheral surface of the oil distribution member 31, other bearing metals can be lined.

  -Instead of providing the opening 31k in the positioning piece 31j, the positioning piece 31j can be made into a fork shape (C shape).

It is a whole outline longitudinal section showing a side thruster provided with an example of an oil supply device of the present invention. It is the longitudinal cross-sectional view which expanded a part of FIG. FIG. 3A is a longitudinal sectional view showing an exploded state of a pair of pressure oil supply pipes (straight pipes), and FIG. 3B is a longitudinal sectional view showing the assembled state. It is a general | schematic outline longitudinal cross-sectional view which shows the side thruster provided with the other Example of the oil supply apparatus of this invention. FIG. 6 is an overall schematic longitudinal sectional view showing a side thruster provided with another embodiment of the fueling device of the present invention in a state rotated by 90 ° from the state of FIG. 4. It is a whole general | schematic longitudinal cross-sectional view which shows the side thruster provided with the conventional oil supply apparatus. It is the longitudinal cross-sectional view which expanded a part of FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Side thruster 2 Duct 3 Gear case 3b * 3c Bearing support part 4 * 5 bearing 6 Drive shaft 7 * 9 Bevel gear 8 Propeller shaft 10 * 11 bearing 12 Variable pitch type propeller boss 12a * 12b Servo cylinder chamber 13 Piston 14 Variable rod 14a Annular Piston portion 14b Protrusion portion of the variable rod 14 15 Propeller blade 16 Seal housing 17 Seal ring 18, 24, 25, 38, 39 O-ring 19 Crank pin ring 20, 20 'Oil supply device 21, 22, 23 Supply / discharge oil passage 26 yen Tubular oil supply shaft 27 Bolt 28 O-ring 29 Radial hole 31 Oil supply distribution member 31b Connection hole 31e Radial hole 31f L-shaped hole 32 Pressure oil supply pipe 32a Flange 34 Oil supply hole 35 Through hole 32b Closed part 32c Annular groove 32d Radius Direction hole 32f bulge 40 Jumping prevention plate 41 White metal 42 Positioning pin 43 Lever 44 Chain A Vessel

Claims (3)

A rotary shaft oil supply device comprising a variable pitch propeller boss at a distal end of a hollow propeller shaft in a gear case, and supplying oil from a base end portion of the propeller shaft into a servo cylinder chamber in the propeller lab through an oil supply distribution member,
A hollow shaft center portion of the propeller shaft, the diameter of the proximal end portion of which is smaller than that of the distal end side thereof, and a knot rod having a distal end integrally connected to a piston disposed in the servo cylinder chamber, Inserted into the hollow shaft center portion of the propeller shaft from the distal end side, penetrates to the proximal end side and protrudes partly, and forms an annular groove on the inner peripheral surface of the proximal small diameter portion of the hollow shaft center portion to seal A ring is interposed, and the propeller pitch is configured to change by sliding the same rod rod in the axial direction via the piston,
A portion of the knot rod is bulged in a radial direction within a hollow shaft portion slightly closer to the tip than the small diameter portion at the base end, and an annular groove is formed on the outer peripheral surface of the bulged annular piston portion to form a seal ring. The hollow shaft center portion is separated into a distal end side chamber and a proximal end side chamber with the annular piston portion as a boundary, and the axial center portion of the knotting rod passes through the radial direction and the axial center portion from the outer peripheral surface of the base portion. Drilling a supply / discharge oil passage leading to the tip of the piston,
A distal-side oil passage connected to a distal-side radial oil passage drilled in the oil-distribution member is formed in the distal-side chamber of the hollow shaft center portion, and a proximal-side L-shape bored in the oil-distribution member. An oil passage is communicated with each of the proximal end chambers of the hollow shaft portion, and the proximal end chamber is communicated with a radial hole of the knotting rod,
A substantially cylindrical oil distribution member is mounted on the outer peripheral surface of the base end portion of the propeller shaft in a floating state, and the oil distribution member is positioned to allow movement in all directions within a certain range.
Both ends of the outer peripheral surface of the oil distribution member are projected in the radial direction, the connection holes are provided through the projections, and the lower end of the pressure oil supply pipe comprising a pair of straight pipes suspended from the ship side is provided. A proximal end that is inserted into each corresponding connection hole, communicates from one connection hole to the distal oil passage, and communicates from the other connection hole to the proximal oil passage. An oil supply device for a rotating shaft , wherein a side L-shaped oil passage is formed in each of the oil supply distribution members . The base end portion of the propeller shaft that covers the oil distribution member is formed as a tubular oil supply shaft that is separate from the main body portion of the front propeller shaft and has a smaller outer diameter than the main body portion. 2. The oil supply device for a rotary shaft according to claim 1 , wherein an outward flange is integrally provided near the shaft tip, and the oil supply shaft is connected by bolting the flange to a base end surface of the main body portion . 3. The oil supply device for a rotating shaft according to claim 1 , wherein white metal is lined on an inner peripheral surface of the oil supply distribution member .

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