JP3962664B2 - Stern tube bearing and manufacturing method thereof - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
  The present invention is used for a propeller bearing having an oil supply groove and an oil supply hole on a bearing inner surface of a ship, and a stern tube bearing having a taper boring process or a slope boring process, or a stern pipe having a static pressure pocket. The present invention relates to a bearing and a manufacturing method thereof.
[0002]
[Prior art]
  FIG. 5 shows a stern structure of a ship in which stern tube bearings are used. A stern tube bearing 1 is installed at the stern of the hull 6, and the propeller shaft 2 passes through the stern tube bearing 1 and the hull stern. The hull stern portion is sealed by a stern tube sealing device 3 to prevent inflow of seawater into the ship and outflow of lubricating oil used in the bearing into the sea. A propeller 4 is mounted on the stern side end of the propeller shaft 2. A rudder 5 is installed on the hull 6 on the stern side of the propeller 4.
  In the stern structure as described above, when the weight of the propeller 4 is large, the propeller shaft 2 is bent by the own weight of the propeller 4, and the propeller shaft 2 is easily hit by one side on the stern side of the stern tube bearing 1. Further, when the ship turns, a large force is generated in the flow of seawater flowing into the propeller 4 due to the interaction between the shape of the rudder 5 and the hull 6 and the propeller shaft 2 moves to the stern tube. It was easy to hit on the stern side of the bearing 1. Therefore, conventionally, the inner surface shape of the stern side of the stern tube bearing has been devised in order to reduce the per unit contact in the gravity direction, the horizontal direction, or the combined direction thereof. An example is described below.
[0003]
  FIG. 6 shows a stern tube bearing in which the bearing inner surface is tapered from the middle of the bearing surface 16 on the bow side so that the tapered bearing surface 9 expands toward the stern side. (A) is sectional drawing which follows an axial center line, (b) is the side view seen from C. This process is called taper boring. The tapered boring is provided in the axial direction L ′ on the stern side of the stern tube bearing 1 and on the entire circumference. R₂Is the radius of curvature of the bearing surface and R₁Is the radius of curvature of the tapered bearing surface, and the center of curvature is C_eMatch. By performing the taper boring process, the diameter of the taper bearing surface 9 increases corresponding to the inclination of the propeller shaft 2 which is bent toward the stern side, so that the outer peripheral surface of the propeller shaft 2 and the taper bearing surface 9 are increased. Can be secured toward the stern side. As a result, it is possible to alleviate the one-side hit on the stern side.
[0004]
  FIG. 7 shows the same radius of curvature R as the bearing inner surface.₂Thus, it is a stern tube bearing whose inner surface is processed into a slope shape from the middle of the bearing surface 16 on the bow side. (A) is sectional drawing which follows an axial center line, (b) is the side view seen from D. This process is called slope boring. The slope boring is provided in the range of the stern side axial direction L ′ of the stern tube bearing 1 and on the lower half surface. ε is the center of curvature C of the bearing surface 16 at the stern end of the stern tube bearing 1._eAnd the center of curvature C of the slope bearing surface 10₂And the distance.
  By applying the slope boring process, in particular, when a heavy weight propeller 4 is mounted, the slope bearing surface 10 from the shaft center line of the bearing corresponds to the inclination of the propeller shaft 2 which is bent toward the stern side. Therefore, the clearance between the outer peripheral surface of the propeller shaft 2 and the slope bearing surface 10 can be secured toward the stern side. As a result, it is possible to alleviate the one-side hit on the stern side.
[0005]
  FIG. 8 shows a stern tube bearing in which a hydrostatic pocket 11 for supporting the propeller shaft 2 with hydraulic pressure is provided on the inner surface of the bearing. (A) is a longitudinal cross-sectional view, (b) is a side view seen from E.
  The static pressure pocket 11 is connected to a high-pressure oil supply pipe 12 that communicates with the outer peripheral surface of the stern tube bearing 1, a high-pressure pipe 13 is connected from the outer peripheral surface, and a pump 15 is connected via a control valve 14. . The hydraulic pressure is applied from the pump 15 to the static pressure pocket 11 and the lubricating oil in the static pressure pocket 11 is supplied to the bearing surface to support the load on the propeller shaft and to reduce the contact of the propeller shaft 2 with each other.
  In the stern tube bearing shown in any of FIGS. 6 to 8, the oil supply grooves 7 are provided in the axial direction on both side surfaces inside the bearing, and a plurality of oil supply holes 8 are formed in each oil supply groove. Yes. Lubricating oil is supplied from the oil supply hole 8 to the oil supply groove 7 during ship operation. The lubricating oil spreads in the axial direction along the oil supply groove 7 and enters the gap between the propeller shaft and the bearing inner surface, and spreads around the entire inner circumference of the bearing as the propeller shaft rotates, thereby providing a lubricating function between the propeller shaft and the bearing inner surface. Fulfill. As a result, thermal damage to the propeller shaft or the bearing inner surface is prevented.
[0006]
  A bearing device using hydraulic pressure is disclosed in Patent Document 1 (Japanese Patent Laid-Open No. 8-091292). In this publication, a plurality of oil supply holes are provided over the entire inner circumference of the bearing, and a static pressure is applied in a low rotation region of the propeller shaft to ensure a bearing load capacity.
  Further, in Patent Document 2 (Japanese Patent Laid-Open No. 6-321185), in a contra-rotating propeller bearing structure, a large number of oil supply pipes are provided inside a bearing that supports a propeller inner shaft, and the mouths of the pipes are provided. A bearing device that is open over the entire inner circumference of the bearing is disclosed. The bearing itself also rotates in the direction opposite to the propeller inner shaft. At this time, the oil supply system is configured so that oil is supplied when the oil supply pipeline inside the rotating bearing comes to the lower surface of the bearing device, and the bearing in the gravity direction with a large propeller shaft load is formed. Ensures surface lubrication.
  Propeller shaft bearings are described in detail in Non-Patent Document 1 (“Class 1 Marine Engine Mechanic Instruction Manual” (Japan Foundation Business Results Library, Japan Marine Engine Maintenance Association, 1996)).
[0007]
[Patent Document 1]
  JP-A-8-091292
[Patent Document 2]
  JP-A-6-321185
[Non-Patent Document 1]
  First-class marine engine mechanic instruction manual (Nippon Foundation Business Results Library, Japan Marine Engine Maintenance Association, 1996)
[0008]
[Problems to be solved by the invention]
  The stern tube bearings related to the prior art described above have the following problems. Usually, the design of the stern tube bearing is performed assuming a static state when the propeller shaft and the propeller are installed. Therefore, the contact of the propeller shaft with the stern tube bearing due to the weight of the propeller shaft and the propeller can be dealt with by setting the bearing clearance and the installation angle of the bearing with respect to the hull. However, when a fluid force is generated along with the turning at the time of marine vessel operation, the direction in which one hits is changed depending on the operating state, so that it is difficult to cope with adjustment of the installation angle of the bearing at the time of design. In particular, in the case of a ship equipped with a propeller that rotates at high speed, the load that the propeller receives is greater in the horizontal direction due to the fluid force than in the direction of gravity. Therefore, since the deflection of the propeller shaft increases in the horizontal direction, it is necessary to support the propeller shaft load on the stern side.
[0009]
  In the case of the bearing device shown in Patent Document 1 and Patent Document 2 or the taper boring process shown in FIG. 6 for the above conditions, when the taper angle is optimized in accordance with the fluid force at the time of ship turning, The angle is excessive as compared with the contact per piece due to the weight of the propeller shaft and the propeller when the ship goes straight. Therefore, a portion with a thin oil film thickness is formed inside the stern side end portion of the bearing, the lubrication of the bearing becomes insufficient, and the bearing or the propeller shaft may be thermally damaged. Further, in the case of the bearing devices shown in Patent Document 1 and Patent Document 2, when the slope boring process shown in FIG. 7 is performed and when the static pressure pocket shown in FIG. 8 is provided, the load in the gravity direction between the propeller shaft and the propeller is reduced. However, it cannot cope with the horizontal load caused by the hydrodynamic force when the ship turns.
[0010]
  In view of the shortcomings of the prior art, the present invention provides a stern tube bearing that supports a propeller shaft of a ship and is provided with an oil groove and an oil hole in the axial direction of the inner surface of the bearing, and in the gravitational load between the propeller shaft and the propeller. By coping with both the horizontal load and the horizontal load caused by the hydrodynamic force when turning the ship, thermal damage to the bearing or propeller shaft can be prevented, thereby reducing the maintenance work frequency and work cost of the stern tube bearing. The purpose is to provide a stern tube bearing with a reduced stern tube bearing and a compact stern tube bearing.
[0011]
[Means for Solving the Problems]
  In order to solve the problem, the present invention as claimed in claim 1,
  In a stern tube bearing that supports a propeller shaft of a ship and has an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove.TheOn the stern side of the bearing,It has a bearing surface formed by a taper boring in which the bearing inner surface is machined into a taper shape spreading from the middle of the bearing surface on the bow side, and the center of curvature C of the taper boring ₃ The axial center position C of the stern tube bearing _e Set upward fromA stern tube bearing is proposed.
  According to the first aspect of the present invention, when a horizontal load is applied during turning of the ship, the propeller shaft load is evenly applied in the axial direction to the bearing surface of the bearing. It can be evenly distributed on the surface. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0012]
  The invention according to claim 2 is the stern tube bearing according to claim 1, wherein the bearing clearance bus 18 on the inner surface of the bearing and the bearing clearance bus 18 on the bearing surface formed by the taper boring are made to coincide. Propose.
  According to the invention described in claim 2, in addition to claim 1, for the load in the gravity direction when the ship is stationary or going straight, the bearing is inclined and installed in the hull and the bearing clearance is set. When a horizontal load is applied when turning a ship, the propeller shaft load is equally applied to the taper-bored bearing surface of the bearing in the axial direction. Can be evenly distributed. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0013]
  The invention described in claim 3A stern tube bearing that supports a propeller shaft of a ship and includes an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove, and a bearing surface formed by slope boring on the stern side of the bearing Provided,
  Furthermore,The radius of curvature of the bearing surface formed by slope boring is made the same as the radius of curvature of the inner surface of the bearing, and the center of curvature of the bearing surface formed by the slope boring is removed from the shaft center of the bearing and provided at two locations. We propose a stern tube bearing characterized by
  According to the third aspect of the invention, in addition to the first aspect, with respect to the load in the gravity direction when the ship is stationary or straight, the bearing is inclined and installed in the hull and the bearing clearance is set. If a horizontal load is applied when turning the ship, the propeller shaft load is evenly applied in the axial direction to the slope-bored bearing surface of the bearing. Can be evenly distributed. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0014]
  Claim7Or8The invention according to any one of the claims relates to a method for manufacturing a stern tube bearing according to any one of claims 1 to 3.
  Claim7The invention described inIn a method for manufacturing a stern tube bearing that supports a propeller shaft of a ship and includes an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove.BoringsurfaceCenter of curvatureTheThe radius of curvature of the machining is set larger than the radius of curvature of the bearing at the stern side end of the bearing, fixed at a position removed from the center of curvature of the bearing.As well asThe taper boring is performed by feeding the boring tool in the axial direction and setting it to become smaller until it matches the radius of curvature of the bearing toward the bow side.YouA method of manufacturing a stern tube bearing is proposed.
  Claim8The invention described inIn a method for manufacturing a stern tube bearing that supports a propeller shaft of a ship and includes an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove.Curvature radius of boringTheSame as the radius of curvature of the bearing, the center of curvature of the machining is set off the shaft center at the stern end of the bearingAs well asSet to move in the radial direction until it coincides with the axial center position of the bearing as it goes to the bow side, and the slope boring is performed by sending the boring tool in the axial direction.YouA method of manufacturing a stern tube bearing is proposed.
[0015]
  Claim7Or8According to the invention described in any one of the above, the inner surface of the bearing is tapered in a direction in which the propeller shaft is expected to come into contact with one another due to the load in the gravity direction when the ship is stationary or straight ahead and the horizontal load when the ship is turning. Since boring can be performed, even when the gravity direction load and the horizontal direction load are applied to the propeller shaft, the propeller shaft load is equally applied in the axial direction of the bearing. Can be evenly distributed. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0016]
  According to a fourth aspect of the present invention, there is provided a stern tube bearing that supports a propeller shaft of a ship and includes an oil supply groove and an oil supply hole that communicates with the oil supply groove in an axial direction of the bearing inner surface.More than oneEstablish a static pressure pocketFurther, the static pressure pocket is provided on the side surface and the lower surface, and the position of the static pressure pocket provided on the side surface is arranged on the stern side of the position of the static pressure pocket provided on the lower surface.A stern tube bearing is proposed.
  According to the invention described in claim 4, the hydraulic pressure applied to the static pressure pocket provided in the bearing with respect to the load in the gravitational direction when the ship is stationary or going straight and against the horizontal load when the ship is turning. Since the propeller shaft can be supported, it is possible to prevent the propeller shaft from coming into contact with each other. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0017]
  This bookAccording to the invention, it is provided by the hydraulic pressure applied to the static pressure pocket provided on the lower surface for the load in the gravitational direction when the ship is stationary or going straight, and on the side surface for the horizontal load when the ship is turning. Since the propeller shaft can be supported by the hydraulic pressure applied to the static pressure pocket, it is possible to prevent the propeller shaft from coming into contact with each other. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0018]
  MoreAccording to the present invention,The effectIn addition, the static pressure provided on the stern side is more suitable for the horizontal load when turning the ship, especially when the horizontal load when turning the ship is greater than the load in the gravity direction when the ship is stationary or straight. Since the propeller shaft can be supported by the hydraulic pressure applied to the pocket, it is possible to prevent the propeller shaft from coming into contact with each other. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0019]
  Claim5Or6The invention according to claim 1 proposes a stern tube bearing characterized in that, in the invention according to any one of claims 1 to 3, a static pressure pocket is provided on the stern side inner surface of the stern tube bearing.
  Claim5In the above, a static pressure pocket is provided from the lower surface of the bearing toward the side surface on the stern side. Also preferably the claim6As described above, the installation position of the static pressure pocket on the side surface is preferably arranged closer to the stern side than the installation position of the static pressure pocket on the lower surface.
  Claim5Or6According to the invention described in claim 1, in addition to any one of claims 1 to 3, the hydraulic pressure is applied to the static pressure pocket provided in the bearing.thingCan support the propeller shaft, so that the bearing can be designed compactly. As a result, it is possible to reduce the manufacturing cost of the stern tube bearing, save the installation space of the bearing, and reduce the maintenance work cost.
[0020]
DETAILED DESCRIPTION OF THE INVENTION
  Hereinafter, the present invention will be described in detail with reference to the embodiments shown in the drawings. However, the dimensions, materials, shapes, relative positions, and the like of the components described in this embodiment are not intended to limit the scope of the present invention only to the description unless otherwise specified. It is just an example.
[0021]
(Embodiment 1)
  Fig.1 (a) is explanatory drawing which shows the structure of the stern tube bearing which concerns on Embodiment 1 of this invention, (a) is sectional drawing which follows an axial center line, (b) is the side view seen from A. .
  In FIG. 1 (a), a flange 17 is machined at the stern side end of a cylindrical stern tube bearing 1, and the stern tube bearing 1 is transferred to the stern tube sealing device 3 or the hull 6 (see FIG. 5). Used for fixing. Oil supply grooves 7 are machined on opposite side surfaces of the bearing surface 16, and a plurality of oil supply holes 8 are drilled into the oil supply grooves 7 so as to communicate with the outer peripheral surface of the stern tube bearing 1. An oil supply pipe (not shown) is connected to the oil supply hole 8, and lubricating oil for lubricating the propeller shaft 2 and the bearing surface 16 is supplied.
[0022]
  Each symbol in FIG. 1 indicates the following. L is the total axial length of the stern tube bearing 1, R_eIs the radius of curvature of the bearing surface 16, R₃Indicates the radius of curvature of the tapered boring at the stern end, and L ′ indicates the axial length of the taper boring. Where R₃> R_eIt is. Further, the propeller shaft 2 indicated by a solid line shows a state in which the propeller shaft center deviates from Ce due to gravity during ship navigation and horizontal load during ship turning. The propeller shaft 2 indicated by a one-dot chain line indicates an initial position when the propeller shaft 2 is attached to the stern tube bearing 1 in the previous period, that is, the propeller shaft center position and the shaft center position Ce of the stern tube bearing 1 coincide with each other. It shows how it is.
[0023]
  In this embodiment, the center of curvature C of the taper boring₃The axial center position C of the stern tube bearing 1_eIt was set off from above. The distance to be removed upward was the distance at which the bearing clearance bus 18 of the bearing surface 16 and the bearing clearance bus 18 of the tapered bearing surface 9 matched at the stern side end of the stern tube bearing 1. By performing such taper boring, the radius of curvature of the bearing surface of the stern side lower surface of the stern tube bearing 1 is R._eAnd the radius of curvature is R as it goes from the lower surface to both side surfaces.₃A taper bearing surface 9 is formed which gradually increases until. However, the taper boring should be done up to the oil groove 7 on both sides and not on the upper half, so the radius of curvature of the bearing surface on the upper half is R_eIt is.
  As described above, the load in the direction of gravity between the propeller shaft 2 and the propeller 4 when the ship is stationary or straight ahead can be handled by tilting the stern tube bearing 1 and setting the bearing clearance. When a horizontal load is applied when turning the ship, the propeller shaft load is evenly applied in the axial direction to the tapered bored bearing surface of the bearing, so the lubricating oil film pressure is applied to the bearing surface. Can be evenly distributed. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0024]
  The taper boring method will be described below. In the stern tube bearing 1, a bearing surface 16, an oil supply groove 7, and an oil supply hole 8 are processed in advance. Next, the bearing 1 is placed on a large rotary table so that the axis of the bearing 1 is perpendicular to the table surface, and the shaft center C of the bearing 1 is set._eAnd the table so that the center of rotation coincides. At this time, it installs so that the bow side end surface of this bearing may contact | connect this table surface. Next, the processing tool held at the stern side end of the bearing 1 is applied to the inner surface of the bearing, and the large rotary table is rotated to cut the inner surface of the bearing and advance the taper boring process.
  Here, taper boring curvature center position C₃Is set to be shifted from the rotation center position of the table. The cutting distance is determined according to the taper boring curvature radius and taper angle designed in advance. The taper angle is an angle formed by the bearing surface 16 and the tapered bearing surface 9. The axial length L ′ for forming the taper boring is determined by the angle and the radius of curvature of the taper boring.
  Here, when taper boring is applied to the half surface of the stern tube bearing, for example, when it is applied to the lower half surface of the bearing, as shown in FIG. The end position is the opposite oil groove 7. By setting the start position and the end position of cutting to the oil supply groove 7, it is possible to secure a space between the contact and escape of the processing tool.
[0025]
(Embodiment 2)
  FIG. 2 is an explanatory view showing a configuration of a stern tube bearing according to Embodiment 2 of the present invention, and shows a view of the stern tube bearing as viewed from the stern side end.
  The flange 17, the oil supply groove 7, and the oil supply hole 8 are processed in the cylindrical stern tube bearing 1 as in the first embodiment.
  Each symbol in FIG. 2 indicates the following. The same symbols as those in FIG. R₂Indicates the radius of curvature of the bearing surface 16 and the slope boring, C₂Is the center of curvature of the slope boring, and ε is the C₂And axis center C of stern tube bearing 1_eAnd the distance.
[0026]
  In the present embodiment, the curvature center position C of the slope boring applied to the stern tube bearing 1.₂Axis center C of stern tube bearing 1_eFrom the left and right side sides, the two were removed and set. By processing in this way, the radius of curvature of the bearing surface at the stern side end of the stern tube bearing 1 is R.₂However, as it goes from the lower surface to both side surfaces, the axial center C_eDistance from bearing surface to maximum R₂It becomes longer to + ε and constitutes the slope bearing surface 10. However, the slope boring is made up to the oil groove 7 on both sides and not on the upper half, so the radius of curvature of the bearing surface on the upper half is R₂It is.
  As described above, the load in the direction of gravity between the propeller shaft 2 and the propeller 4 when the ship is stationary or going straight can be handled by tilting the stern tube bearing 1 and setting the bearing clearance. If a horizontal load is applied when the ship is turning, the propeller shaft load is evenly applied in the axial direction to the bearing surface on which the slope boring of the bearing is performed. Can be evenly distributed. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0027]
  The slope boring method will be described below. In the stern tube bearing 1, a bearing surface 16, an oil supply groove 7, and an oil supply hole 8 are processed in advance. Next, the bearing 1 is placed on a large rotary table so that the axis of the bearing 1 is perpendicular to the table surface, and the shaft center C of the bearing 1 is set._eAnd the table so that the center of rotation coincides. At this time, it installs so that the bow side end surface of this bearing 1 may contact | connect this table surface. Next, the large rotary table is inclined with respect to the cutting direction. A processing tool held at the stern side end of the bearing 1 is applied to the inner surface of the bearing, and the large rotary table is rotated to cut the inner surface of the bearing and advance the slope boring process.
  Where slope boring radius of curvature R₂Is the radius of curvature R of the bearing surface 16 of the bearing 1.₂Same as As shown in FIG. 2, the angle at which the large rotary table is inclined with respect to the cutting direction is the center of curvature C of the slope bearing surface 10 at the stern side end of the bearing 1.₂Axis center C_eIs determined from the distance ε shifted from the axial distance of the slope bearing surface 10 designed in advance.
[0028]
(Embodiment 3)
  FIG. 3 is an explanatory view showing a configuration of a stern tube bearing according to Embodiment 3 of the present invention, and is a cross-sectional view taken along the axial center line of the stern tube bearing.
  The flange 17, the oil supply groove 7, and the oil supply hole 8 are processed in the cylindrical stern tube bearing 1 as in the first embodiment.
  In this embodiment, a static pressure pocket 11 is provided on the stern side bearing surface 16 of the stern tube bearing 1, a high pressure oil supply pipe 12 communicating with the outer peripheral surface of the stern tube bearing 1 is drilled there, and further, high pressure piping is provided. 13 and a control valve 14 were connected to the pump 15 by piping. Here, the static pressure pocket 11 has a substantially rectangular opening in the bearing surface 16, and is constructed from the lower surface of the stern tube bearing 1 toward both side surfaces on the stern side. During the operation of the ship, the lubricating oil is pressurized to the static pressure pocket 11 using the pump 15 to support the load on the propeller shaft 2. The degree of pressurization is adjusted by the opening degree of the control valve 14 corresponding to the increase or decrease of the load.
[0029]
  Since the static pressure pockets 11 are provided on both side surfaces on the stern side from the bearing lower surface, the load in the gravity direction between the propeller shaft 2 and the propeller 4 when the vessel is stationary or going straight, and the horizontal load of the vessel turning On the other hand, since the propeller shaft can be supported by adjusting the hydraulic pressure of the lubricating oil applied to the static pressure pocket, it is possible to prevent the propeller shaft from coming into contact with one another. In particular, when the propeller 4 that rotates at a high speed is used, the size per piece when a horizontal load is applied is likely to be larger than when a load in the gravity direction is applied. That is, since the propeller shaft 2 is greatly bent in the horizontal direction, the maximum pressure of the oil film is necessary on the side surface close to the stern. Therefore, by providing the static pressure pocket 11 closer to the side surface, the restoring force against the deflection of the propeller shaft 2 can be increased. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0030]
(Embodiment 4)
  4A and 4B are explanatory views showing the configuration of a stern tube bearing according to Embodiment 4 of the present invention. FIG. 4A is a cross-sectional view taken along the axial center line of the stern tube bearing, and FIG. is there.
  The flange 17, the oil supply groove 7, and the oil supply hole 8 are processed in the cylindrical stern tube bearing 1 as in the first embodiment.
  In this embodiment, a lower surface static pressure pocket 11a is provided on the lower surface on the stern side of the stern tube bearing 1, and a side surface static pressure pocket 11b is provided on both side surfaces on the stern side, and the stern tube bearing 1 is provided in each static pressure pocket. A high-pressure oil supply pipe 12 communicating with the outer peripheral surface was drilled, and further connected to a pump 15 via a high-pressure pipe 13 and a control valve 14. Here, the static pressure pockets 11 a and 11 b have a substantially rectangular opening having a long side in the circumferential direction of the stern tube bearing 1 on the bearing surface 16.
[0031]
  With this configuration, the lubricant is pressurized by the pump 15 to the static pressure pockets 11a and 11b, and the load in the horizontal direction is mainly applied to the lower surface static pressure pocket 11a with respect to the load in the gravity direction. In contrast, the propeller shaft 2 is supported mainly by the hydraulic pressure applied to the side surface static pressure pocket 11b. The degree of pressurization is adjusted by the opening degree of each control valve 14 corresponding to the increase or decrease of each load.
  Since the static pressure pockets 11a and 11b are provided independently on the bearing lower surface and both side surfaces on the stern side, with respect to the load in the direction of gravity between the propeller shaft 2 and the propeller 4 when the vessel is stationary or straight ahead The hydraulic pressure of the lubricating oil applied to the static pressure pocket 11a provided on the lower surface of the bearing is adjusted, and the hydraulic pressure of the lubricating oil applied to the static pressure pocket 11b provided on both sides is adjusted with respect to the horizontal load when the ship turns. Thus, the propeller shaft can be supported, so that the propeller shaft can be prevented from coming into contact with each other.
[0032]
  In particular, when the propeller 4 that rotates at a high speed is used, the size per piece when a horizontal load is applied is likely to be larger than when a load in the gravity direction is applied. That is, since the propeller shaft 2 bends more largely in the horizontal direction than in the direction of gravity, the maximum pressure of the oil film is required on the side surface near the stern. Therefore, by providing the static pressure pocket 11 closer to the side surface on the stern side, it is possible to increase the restoring force against the deflection of the propeller shaft 2.
  Furthermore, a compact stern tube bearing can be manufactured if the position, number, opening size, depth, etc. of the static pressure pocket are designed in accordance with the axial load assumed during ship operation. This is because, like a taper boring, a slope boring, and a static pressure pocket having an angle in the circumferential direction, a certain amount of structural size is not required for the function to function. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced. Furthermore, since a compact stern tube bearing can be manufactured, it is possible to reduce the manufacturing cost of the bearing, save the installation space of the bearing, and reduce the maintenance work cost.
[0033]
(Embodiment 5)
  The fifth embodiment of the present invention (not shown) has a structure in which the first embodiment is combined with the third or fourth embodiment. Or it is set as the structure which combined Embodiment 2 and Embodiment 3 or Embodiment 4. FIG.
  In addition to the taper boring described in the first embodiment or the slope boring described in the second embodiment, the static pressure pocket 11 is provided, and the hydraulic pressure of the lubricating oil applied to the static pressure pocket 11 is adjusted. The range of the magnitude of the axial load that 1 can deal with widens. Therefore, if the stern tube bearing 1 has the same size, the shaft load that can be handled becomes large. If the shaft load is the same, the bearing can be made compact. As a result, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced. Furthermore, since a compact stern tube bearing can be manufactured, it is possible to reduce the manufacturing cost of the bearing, save the installation space of the bearing, and reduce the maintenance work cost.
[0034]
【The invention's effect】
  As described above, claims 1 to 3 and claims7Or8According to the invention, since one or both of the taper boring and the slope boring is provided on the stern side of the stern tube bearing and the center of curvature thereof is set off from the shaft center of the bearing, the horizontal load is applied when the ship turns. Is applied, the propeller shaft load is evenly applied in the axial direction to the bearing surface of the bearing, and the lubricant film pressure can be evenly distributed over the bearing surface. Thereby, generation | occurrence | production of the thermal damage of a bearing or a propeller shaft can be prevented, and it contributes to the reduction of the maintenance work frequency and work cost of a stern tube bearing.
[0035]
  Further, according to the invention of claim 4, since the static pressure pockets are provided which are communicated from the lower surface of the stern side inner surface of the stern tube bearing toward the both side surfaces of the stern side, the gravity direction when the ship is stationary or when traveling straight The propeller shaft can be supported by the hydraulic pressure applied to the static pressure pockets provided in the bearings against the load and the horizontal load at the time of turning of the ship, and the propeller shaft can be prevented from hitting one side. Thereby, generation | occurrence | production of the thermal damage of a bearing or a propeller shaft can be prevented, and it contributes to the reduction of the maintenance work frequency and work cost of a stern tube bearing.
[0036]
  Claims4According to the invention, since the plurality of static pressure pockets are provided on the stern side inner surface of the stern tube bearing, the hydraulic pressure applied to the static pressure pocket provided on the lower surface with respect to the load in the gravity direction when the ship is stationary or straight ahead In addition, since the propeller shaft can be supported by the hydraulic pressure applied to the static pressure pocket provided on the side surface with respect to the horizontal load at the time of turning the ship, it is possible to prevent the propeller shaft from hitting one side. Thereby, the occurrence of thermal damage to the bearing or the propeller shaft can be prevented, and the maintenance work frequency and work cost of the stern tube bearing can be reduced.
[0037]
  Claims5Or6According to the invention, in the invention according to any one of claims 1 to 3, the hydrostatic pocket is provided on the stern side inner surface of the stern tube bearing, and preferably on the side surface on the stern side from the lower surface of the bearing. Since the static pressure pockets are provided, and preferably, a plurality of static pressure pockets are provided, and the installation position of the static pressure pockets on the side surface is disposed closer to the stern side than the installation position of the static pressure pockets on the lower surface. The propeller shaft can be supported by a method of applying hydraulic pressure to the static pressure pocket, and the bearing can be designed compactly. Thereby, the manufacturing cost of the stern tube bearing can be reduced, the installation space of the bearing can be saved, and the maintenance work cost can be reduced.
[0038]
[Brief description of the drawings]
FIG. 1 is an explanatory diagram showing a configuration of a stern tube bearing according to a first embodiment of the present invention.
FIG. 2 is an explanatory diagram showing a configuration of a stern tube bearing according to a second embodiment of the present invention.
FIG. 3 is an explanatory diagram showing a configuration of a stern tube bearing according to a third embodiment of the present invention.
FIG. 4 is an explanatory diagram showing a configuration of a stern tube bearing according to a fourth embodiment of the present invention.
FIG. 5 is an explanatory view showing a configuration of a rear part of a hull in which a stern tube bearing is installed.
FIG. 6 is an explanatory view showing a prior art of a stern tube bearing.
FIG. 7 is an explanatory view showing a prior art of a stern tube bearing.
FIG. 8 is an explanatory view showing a prior art of a stern tube bearing.
[Explanation of sign]
  1 Stern tube bearing
  9 Tapered bearing surface
10 Slope bearing surface
11 Static pressure pocket
11a Underside static pressure pocket
11b Side static pressure pocket
16 Bearing surface
18 Bearing clearance busbar

Claims (8)

In a stern tube bearing that supports a propeller shaft of a ship and has an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove, on the stern side of the bearing, from the middle of the bearing surface on the bow side it has a bearing surface formed by the processed taper boring the bearing inner surface diverging tapered that it has set off upward curvature center position C ₃ of the tapered borehole from the axial center position C _e of the stern tube bearing Stern tube bearing featured.   The stern tube bearing according to claim 1, wherein a bearing clearance bus bar on the inner surface of the bearing and a bearing clearance bus bar on a bearing surface formed by the tapered boring are matched. A stern tube bearing that supports a propeller shaft of a ship and includes an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove, and a bearing surface formed by slope boring on the stern side of the bearing Provided,
Further, the radius of curvature of the bearing surface formed by the slope boring is made the same as the radius of curvature of the bearing inner surface, and the center of curvature of the bearing surface formed by the slope boring is removed from the shaft center of the bearing and provided at two locations. ship tail tube bearing you, characterized in that the. In a stern tube bearing that supports a propeller shaft of a ship and has an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove , a plurality of static pressure pockets are provided on the inner surface of the stern side of the bearing , Further , the stern tube bearing is characterized in that the static pressure pocket is provided on the side surface and the lower surface, and the position of the static pressure pocket provided on the side surface is arranged on the stern side of the position of the static pressure pocket provided on the lower surface . The stern tube bearing according to any one of claims 1 to 2 , wherein a static pressure pocket is provided on a stern side inner surface of the bearing from a lower surface of the bearing toward a stern side surface. The stern tube bearing according to claim 4, wherein the installation position of the static pressure pocket on the side surface is arranged closer to the stern side than the installation position of the static pressure pocket on the lower surface on the inner surface of the stern side of the bearing.   In a method for manufacturing a stern tube bearing that supports a propeller shaft of a ship and has an oil supply groove in the axial direction of the bearing inner surface and an oil supply hole that communicates with the oil supply groove, the center of curvature of the boring surface is the curvature of the bearing. The radius of curvature of the machining is set larger than the radius of curvature of the bearing at the stern end of the bearing and coincides with the radius of curvature of the bearing toward the bow side. A method for manufacturing a stern tube bearing, wherein taper boring is performed by feeding a boring tool in an axial direction.   In a manufacturing method of a stern tube bearing that supports a propeller shaft of a ship and has an oil supply groove and an oil supply hole that communicates with the oil supply groove in the axial direction of the inner surface of the bearing, the curvature radius of boring is defined as the curvature radius of the bearing. As the same, the center of curvature of the machining is set off the shaft center at the stern end of the bearing, and is moved in the radial direction until it coincides with the shaft center position of the bearing toward the bow side. A method for manufacturing a stern tube bearing, characterized in that slope boring is performed by setting and sending a boring tool in an axial direction.

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