Contra-rotating bearing device for contra-rotating propeller

Abstract: A contra-rotating bearing device (T9) for a contra-rotating propeller comprises an outer shaft (1) having a front propeller, an inner shaft (2,23) which is fitted in the outer shaft (1), rotates in the direction opposite to the outer shaft (1) and has a rear propeller. A contra-rotating bearing is provided between the inner shaft (2,23) and the outer shaft (1). An oil feed port (28) is provided by forming a hollow portion on the inner shaft (2,23), and a plurality of radial oil feed holes (29) which are connected with the oil feed port (28) are formed. Lubrication oil which generates a static pressure load carrying capacity is fed from the inner shaft (2,23) to the inner peripheral face of the bearing (26) through the oil feed port (28) and the radial oil feed holes (29), a plurality of concavo-convex shaped portions (42) which generate a dynamic pressure load carrying capacity are formed on the inner peripheral face of the bearing (26) in the axial direction of the bearing, and circular portions (41B,41F) are provided on both ends of the concavo-convex shaped portions (42) provided in the axial direction of the bearing.

Description: The present invention relates to shafting for contra-rotating propellers and particularly to a contra-rotating bearing for such shafting. It is known to provide a contra-rotating propeller in which an outer shaft having a front propeller and an inner shaft fitted in the outer shaft and having a rear propeller are caused to rotate in mutually opposite directions in order to effectively untilize propeller propulsion energy. Recently, the contra-rotating propeller has been employed in order to enhance the propulsion efficiency of a ship propulsion system. For example, Fig. 1 is a partial broken side view showing a contra-rotating propeller according to the prior art, and Fig. 2 is a sectional view taken along the line E - E shown in Fig. 1. A contra-rotating propeller 100 includes a hollow outer shaft 102 having a front propeller 101, an inner shaft 104 provided in the outer shaft 102 and having a rear propeller 103, and a main engine 105 for causing the outer shaft 102 and the inner shaft 104 to rotate in mutually opposite directions. The outer shaft 102 has a cylindrical shape, and is rotatably provided on a stern portion 106 of a hull Y through an outer shaft bearing 107 and an outer shaft seal 108. The inner shaft 104 is provided inside the outer shaft 102 through a contra-rotating bearing 109 and an inner shaft seal 110 so as to rotate in the opposite direction. The hull Y is provided with a lubrication oil supply system 111 for supplying lubrication oil to the outer shaft 102, the inner shaft 104, the outer shaft bearing 107 and the contra-rotating bearing 109. A rudder horn 112 and a rudder plate 113 are opposed to the front propeller 101 and the rear propeller 103. In the contra-rotating propeller 100 having such a structure, an ordinary journal bearing mechanism can be employed as the outer shaft bearing 107 provided between the outer shaft 102 and the stern portion 106. In the contra-rotating bearing 109 which supports the inner shaft 104 that rotates in the outer shaft 102 in the opposite direction, particularly as shown in Fig. 2, however, in the case where the inner shaft 104 rotates clockwise and the contra-rotating bearing 109 such as a plain bearing which is fixed to the outer shaft 102 and the inner peripheral face thereof rotates counterclockwise, there is a possibility that lubrication oil cannot form an oil film between the outer peripheral face of the inner shaft 104 and the inner peripheral face of the contra-rotating bearing 109 if the outer shaft 102 and the inner shaft 104 rotate at almost equal speeds. For this reason, it becomes hard for the shafts 102 and 104 to perform hydrodynamic lubrication due to the oil film formation by the lubrication oil supplied from the lubrication oil supply system 111 when the inner shaft 104 and the outer shaft 102 rotate in mutually opposite directions at almost equal speeds as shown in a sectional view of Fig. 3 in which the contra-rotating bearing 109 is provided on the inner peripheral face of the outer shaft. Thus, there is a possibility that the ordinary bearing cannot display the bearing function. For this reason, in some bearings, a floating bush 114 is provided between the outer shaft 102 and the inner shaft 104 as shown in a sectional view of Fig. 4. And, the floating bush 114 is almost kept stationary between both shafts 102 and 104 so that an oil film is formed between the floating bush 114 and each of the inner shaft 104 and outer shaft 102 to form a contra-rotating bearing. In case of a hydrodynamic bearing using the floating bush 114, however, an oil film which can display the bearing function can be formed during ordinary operation, while the oil film is formed with difficulty during low-speed operation when entering and leaving a port so that metallic contact is sometimes caused on the bearing surface. Furthermore, the inner shaft 104 is bent easily by a cantilever support of the rear propeller 103 so that local contact may be caused on the rear end of the bearing. In some bearings, a tapered land (not shown) is formed on the inner face of the contra-rotating bearing 109 which supports the inner shaft 104, and a dynamic pressure is generated by a tapered portion of the tapered land to form an oil film so that the inner shaft 104 is lifted up. Also in the case where the tapered land is provided, however, a load carrying capacity generated by the dynamic pressure is small when causing the main engine 105 to start or rotate at a low speed. Consequently, the oil film becomes thinner. Thus, there is a possibility that the inner shaft 104 and the contra-rotating bearing 109 metallically comes in contact with each other on the bearing surface so that the contra-rotating bearing 109 is seized. As the prior art to solve the above-mentioned problems, "STERN TUBE BEARING SYSTEM OF CONTRA-ROTATING PROPELLER" (Japanese Examined Patent Publication No. 5-45479)which is based on a hydrostatic bearing as shown in a sectional view showing main parts of Fig. 5 has been disclosed, wherein an oil feed hole 116 is formed radially from a concentric hole 115 of the inner shaft 104, and a screw 117 having a small hole for orifice formation or capillary tube restriction is fitted in the oil feed hole 116 to eject high-pressure oil from the oil feed hole 116 toward the contra-rotating bearing surface between the inner shaft 104 and the outer shaft 102 or the contra-rotating bearing 109 so that a load carrying capacity is generated by a static pressure to lift up the inner shaft 104, thereby preventing the local contact of the inner shaft 104. In addition, a contra-rotating bearing has been disclosed in which a plurality of oil feed holes 116 which are radially provided and connected with both of the outer peripheral face of the inner shaft within a range L of the bearing surface of the inner shaft 104 and the concentric hole 115 provided on the core of the inner shaft 104, and the oil feed holes 116 are arranged in a plurality of lines in the longitudinal direction of the inner shaft as shown in sectional views of Figs. 6 (a) and (b). In case of above-mentioned contra-rotating bearing, however, the contra-rotating bearing 109 of the outer shaft 102 is circular bearing. For this reason, when the inner shaft 104 and the outer shaft 102 rotate in mutually opposite directions at equal speeds as described above, the circular bearing does not generate a load carrying capacity by the dynamic pressure of the lubrication oil theoretically. Consequently, in case of a high ratio of number of revolutions in which the inner shaft 104 and the outer shaft 102 (contrarotating bearing 109) rotate in mutually opposite directions at almost equal speeds, there is a possibility that an oil film is not formed but seizure is easily caused when the static pressure oil supply from the radial oil feed hole 116 is not performed due to blackout or the failure of an oil feeding pump of the lubrication oil supply system 111. In case of the high ratio of number of revolutions, the load carrying capacity generated by the dynamic pressure is insufficient as described above. For this reason, it is necessary to supply the lubrication oil from the radial oil feed hole 116 with a comparatively high static pressure. Consequently, the size of the lubrication oil supply system 111 becomes larger. Furthermore, a lot of oil feed holes 116 are provided on the inner shaft 104 to form the static pressure bearing. For this reason, the strength of the inner shaft 104 is sometimes lowered. In such a case, it is necessary to increase an inner shaft diameter in order to maintain the strength of the inner shaft. Consequently, a weight is increased and the size of a propulsion unit becomes larger. The present invention has been made in order to provide a contra-rotating bearing device for a contra-rotating propeller wherein a sufficient oil film is formed on the bearing surface of a contra-rotating bearing which supports an inner shaft in the contra-rotating propeller so that an excellent bearing function can be displayed. FR-A-1559502 discloses contra-rotating shafting for a contra-rotating propeller, said shafting comprising an outer shaft for driving a front propeller, an inner shaft which is fitted in the outer shaft and is rotatable in the direction opposite to the outer shaft for driving a rear propeller, and a contra-rotating bearing provided between the inner shaft and the outer shaft. The invention provides a contra-rotating shafting for a contra-rotating propeller, said shafting comprising an outer shaft for driving a front propeller, an inner shaft which is fitted in the outer shaft and is rotatable in the direction opposite to the outer shaft for driving a rear propeller, and a contra-rotating bearing provided between the inner shaft and the outer shaft, characterised in that an oil feed port and a plurality of radial oil feed holes connected with the oil feed port are provided in the innershaft for supplying lubrication oil from an external lubrication oil supply system to the inner peripheral face of the bearing to provide a static load carrying capacity, a plurality of concavo-convex shaped portions extending in the axial direction of the bearing for generating, in use, a dynamic pressure load carrying capacity are provided on the inner peripheral face of the bearing facing said inner shaft, and circular portions are provided at each end of the concavo-convex shaped portions. The concavo-convex shaped portions may comprise a tapered land or lobed bearing surface. Advantageously, the radial oil feed holes are provided backward in the axial direction of the bearing from a central position of the bearing by a distance of L/6 to L/4, where L is the length of the bearing. The total length of the circular portions may be L/48 to 24L/48, where L is the length of the bearing. The total length of the circular portions may be 2L/48 to 10L/48, where L is the length of the bearing. The embodiments hereinafter described provide a contra-rotating propeller in which: the contra-rotating bearing is lubricated using a small number of oil feed holes without reducing the strength of the inner shaft; lubrication oil having a pressure which is necessary within the range of the bearing surface of the inner shaft is supplied; a load carrying capacity is provided even during uniform contra-rotation in which an inner shaft and an outer shaft rotate in mutually opposite directions at almost equal speeds, or in a state close thereto; the inner shaft is supported with only the load carrying capacity generated by the dynamic pressure of the lubrication oil at high rotational speeds and the load carrying capacity is maintained at low rotational speeds, at which it is hard to generate a sufficient load carrying capacity by only the dynamic pressure, by increasing an oil feed pressure to add a static pressure component; and sufficient load carrying capacity is generated with a low oil feed pressure by using the non-circular shape of the contra-rotating bearing. In the described embodiments, the inner peripheral face of the contra-rotating bearing has a non-circular shape to generate a dynamic pressure together with the inner shaft and the non-circular shaped portion is enclosed by circular portions. Consequently, when the lubrication oil is supplied from the inside of the inner shaft to the surface of the contra-rotating bearing through the radial oil feed holes, a load carrying capacity which wholly approximates a uniform value in the axial direction of the contra-rotating bearing at a static pressure obtained by the lubrication oil fed from'the inside of the inner shaft in the direction of the contra-rotating bearing because the concave-convex portions such as tapered lands or lobed bearing surfaces which are formed on the inner peripheral face of the contra-rotating bearing have the non-circular shape. Since the non-circular portion of the contra-rotating bearing is enclosed by the circular portions provided at each end of the concavo-convex shaped portion, the lubrication oil stored in the concavo-convex shaped portion leaks out to the outside with difficulty so that the inner shaft can be supported effectively. Thus, it is possible to further enhance dynamic pressure performance and static pressure performance which forms an oil film to generate the load carrying capacity. The concavo-convex shaped portion is a tapered land or lobed bearing surface. Consequently, the load carrying capacity is generated by the dynamic pressure between the inner shaft and the contra-rotating bearing irrespective of the ratio of number of revolutions. Accordingly, it is not necessary to increase the static pressure applied from the radial oil feed holes. Thus, the load carrying capacity can be generated by the dynamic pressure positively and effectively, and the oil feeding pressure can be lowered. Consequently, inboard power can be saved because it is not necessary to perform static pressure oil feeding from a lubrication oil supply system or a low pressure is enough. Also in the case where the oil is not supplied during blackout so that the load carrying capacity cannot be generated by the static pressure or the front and rear propellers are brought into the free rotation state at a low speed and also in case of a high ratio of number of revolutions where the inner shaft and the outer shaft rotate at almost equal speed, the load carrying capacity can be generated by the dynamic pressure irrespective of the ratio of number of revolutions. Thus, the anti-seizure property can be enhanced more than in the structure of a circular bearing. The number of the concavo-convex shaped portions can be set to an optimum value on the conditions for usage of the bearing irrespective of the number of the radial oil feed holes. The radial oil feed hole are provided backward from a central position in the axial direction of the bearing by a distance of L/6 to L/4, L is the length of the bearing. Consequently, the effect of the static pressure oil supply can be enhanced. The length of the circular portions is L/48 to 24L/48, where L is the length of the bearing. Consequently, the load carrying capacity can be enhanced more by the dynamic pressure and static pressure of the lubrication oil. In particular, it is preferable that the length of the circular portion should be 2L/48 to 10L/48. In order that the invention may be well understood, some embodiments thereof, which are given by way of example only, will now be described with reference to the drawings, in which: Figure 1 is a partial broken side view showing a contra-rotating propeller according to the prior art; Figure 2 is a sectional view taken along the line E - E in Figure 1; Figure 3 is a sectional view showing a contra-rotating bearing device for a contra-rotating propeller according to the prior art; Figure 4 is a sectional view showing another contra-rotating bearing device for a contra-rotating propeller according to the prior art; Figure 5 is a sectional view showing main parts of a stern tube bearing for a contra-rotating propeller based on a static pressure circular bearing according to the prior art; Figure 6 is a view showing another contra-rotating bearing device for a contra-rotating propeller according to the prior art, wherein (a) is a side sectional view and (b) is a sectional view taken along the line F - F of (a); Figure 7 is a sectional view showing a contra-rotating propeller provided with a contra-rotating bearing according to an embodiment of the invention; Figure 8 is a sectional view taken along the line C - C shown in Figure 7; Figure 9 is a sectional view showing a curved taper face and a land face in Figure 8 more specifically; Figure 10 is a developed view showing a tapered land on the inner peripheral face of the contra-rotating bearing in Figure 9; Figure 11 is a sectional view showing a lobed bearing surface as another example of a contra-rotating bearing in accordance with another embodiment of the invention; Figure 12 is a developed view showing the lobed bearing surface on the inner peripheral face of the contra-rotating bearing in Figure 11; Figure 13 is a sectional view showing a preferred location of the oil feed section of the contra-rotating bearing device; Figure 14 is a sectional view taken along the line D - D in Figure 13; Figure 15 is a sectional view showing a possible modification to the contra-rotating bearing; Figure 16 is a chart showing the relationship between the number of revolutions of the inner shaft and a minimum oil film thickness (load carrying capacity); Figure 17 is a chart showing the relationship between the ratio of number of revolutions and the minimum oil film; Figure 18 is a diagram showing the relationship between the rear side land face and the front side land face and the oil film thickness wherein (a) is a sectional view showing the contra-rotating bearing and (b) is a chart showing the relationship of the oil film thickness; Figure 19 is a sectional view showing the case where the inner shaft is slightly eccentric to the contra-rotating bearing; Figure 20 is a chart showing the relationship between the ratio of number of revolutions and the oil film thickness. Embodiments of the present invention which takes note that a dynamic pressure is generated between an inner shaft and an inner peripheral face of a contra-rotating bearing which has a non-circular shape and the non-circular shaped portion of the contra-rotating bearing is enclosed by a circular portion will be described below. An example of contra-rotating propeller shafting provided with a contra-rotating bearing for a contra-rotating propeller according to the present invention will be described below. Like portions are given the same reference numerals as in the prior art arrangement of Figs. 1 to 6 described above, and will not be described again in detail. Fig. 7 is a sectional view showing contra-rotating propeller shafting 21 comprising a contra-rotating bearing device T9 according to the present invention. Fig. 8 is a sectional view taken along the line C - C of Fig. 7. As shown in Fig. 7, the contra-rotating propeller 21 includes an outer shaft 22 having a front propeller 101, and an inner shaft 23 having a rear propeller 103. The outer shaft 22 is cylindrical-shaped and is rotatably provided integrally with a front propeller boss 24 of the front propeller 101 and a coupling member 25 through an outer bearing 107. The inner shaft 23 is provided integrally with a rear propeller boss 27 of the rear propeller 103 through a contra-rotating bearing 26 inside the outer shaft 22 and rotatable in the direction opposite to the outer shaft 22. The contra-rotating bearing device T for a contra-rotating propeller is provided on the inner shaft 23 and contra-rotating bearing 26 portions. More specifically, a hollow portion is provided in the direction of the core of the inner shaft 23 to form an oil feed port 28 to which lubrication oil is supplied from a lubrication oil supply system 111 at a predetermined pressure. As shown in Fig. 8, a plurality of radial oil feed holes 29 in communication with the oil feed port are formed in a portion of the inner shaft 23 opposed to the contra-rotating bearing 26. In this example, there are eight radial oil feed holes 29 formed in a sectional portion perpendicular to the axial direction of the inner shaft 23. Thus, lubrication oil can be supplied to the bearing surface between the outer peripheral face of the inner shaft 23 and the inner peripheral face of the contra-rotating bearing 26. A part of the lubrication oil supplied to the bearing surface flows from a drain port 35 of a stern portion 106 to a tank (not shown) of the lubrication oil supply system 111 through an axial oil path 30 of the contra-rotating bearing 26, a cylindrical path 32 between a cylindrical member 31 for isolation and the inner shaft 23, a diametral communicating hole 33 of the cylindrical member 31 for isolation, an oil drain hole 34 of the outer shaft 22. The lubrication oil which is supplied to the bearing surface and flows in the direction of the cylindrical path 32 merges a part of the lubrication oil described above, and flows from the drain port 35 of the stern portion 106 to the tank through the cylindrical path 32, the diametral communicating hole 33 of the cylindrical member 31 for isolation, the oil drain hole 34 of the outer shaft 22. In the contra-rotating bearing T9 for a contra-rotating propeller shown in Fig. 8, a tapered land 42, in which a curved taper face 40 and a land face 41 are alternately provided, is formed at regular angles on the inner peripheral face of a contra-rotating bearing 26. The curved taper face 40 is formed like a recess by a circular arc having a curvature which is smaller than the curvature of the outer peripheral face of an inner shaft 23. The land face 41 is formed like a circle concentrically with the outer peripheral face of the inner shaft 23. Fig. 9 is a sectional view showing the curved taper face 40 and the land face 41 more specifically. A circle having a radius R2 is drawn around points spaced at equal central angles (8 points in Fig. 9) on a circumference having an optional radius R1 from the center of the contra-rotating bearing 26 to form the curved taper faces 40 and leave the land faces 41 on the inner peripheral face of the contra-rotating bearing 26. By optionally selecting and combining the radii R1 and R2, the curved taper face 40 having a predetermined shape and depth and the land face 41 having a predetermined length can be obtained. It is sufficient that an optimum value is selected for the number of tapered lands 42 depending on the conditions for usage of a bearing irrespective of the number of radial oil feed holes 29. A maximum depth H of the curved taper face 40 is R1 + R2 - (R + Cr), wherein a radius of the inner shaft 23 is represented by R and a clearance between the outer peripheral face of the inner shaft 23 and the inner peripheral face of the contra-rotating bearing 26 (radius clearance) is represented by Cr. The maximum depth H of the curved taper face 40 is sometimes changed slightly depending on the number of bearing pads, that is, the number of the tapered lands 42 and operating conditions, and approximates [(1.0 to 3.0) x a diameter (inner diameter) of the contra-rotating bearing 26 / 10000]. Fig. 10 is a developed view showing the inner peripheral face of the contra-rotating bearing 26. The curved taper faces 40 and the land faces (circular portions) 41 of the tapered lands 42 are alternately formed. A rear side land face 41B (SB on the left side of Fig. 10) and a front side land face 41F (SF on the right side of Fig. 10) are formed with a radius of about (R + Cr) as circumferential circular portions (land faces) having predetermined lengths over the circumference on the same peripheral face as the land face 41 on axial both end sides of the tapered land 42 (right and left sides shown in Fig. 10). The total of these lengths is represented by S. More specifically, the whole circumferential portion of the curved taper face 40 is enclosed by a pair of land faces 41 provided in the circumferential direction and the rear side land face 41B and the front side land face 41F provided in the axial direction on the inner peripheral face of the contra-rotating bearing 26 (a hatching portion shown in Fig. 10 indicates a circular portion, that is, a land face). Fig. 11 shows a contra-rotating bearing device T10 for a contra-rotating propeller according to another embodiment. The inner peripheral face of the contra-rotating bearing 26 is divided into equal parts (for example, 8 parts) and a concave portion is formed on the inner peripheral face between adjacent dividing lines 41L that define the equal parts. On a circumference having an optional radius R1 from the center of an inner shaft 23, two circles are further drawn with a radius R3 around two points, which are adjacent to each other, of points for division into equal central angles (8 portions in Fig. 11). These circular arcs and the inner peripheral face intersect and a lobed bearing surface 43 (concave portion) corresponding to the tapered land 42 is formed with a predetermined depth and shape between dividing lines 41L which are adjacent to each other. By optionally'selecting and combining the radii R1 and R3, the lobed bearing surface 43 having a predetermined shape and depth can be obtained. It is sufficient that the number of the lobed bearing surfaces 43 is set to an optimum value depending on the conditions for usage of a bearing irrespective of the number of radial oil feed holes 29. Fig. 12 is a developed view showing the inner peripheral face of the contra-rotating bearing 26 shown in Fig. 11, in which the lobed bearing surface 43 is formed in the circumferential direction. A rear side land face 41B (SB on the left side of Fig. 18) and a front side land face 41F (SF on the right side of Fig. 18) are formed with a radius of about (R + Cr) as circumferential circular portions (land faces) having predetermined lengths over the circumference on the same peripheral face as the land face 41 on axial both end sides of the lobed bearing surface 43 (right and left sides shown in Fig. 12) in the same manner as in Fig. 10. More specifically, the lobed bearing surface 43 has axial both ends enclosed by the rear side land face 41B and the front side land face 41F in the axial direction on the inner peripheral face of the contra-rotating bearing 26 (a hatching portion shown in Fig. 12 indicates a circular portion). For the total S (in the axial direction of the contra-rotating bearing 26) of the length SB of the rear side land face 41B and the length SF of the front side land face 41F described above in the inner peripheral direction of the contra-rotating bearing 26 shown in Figs. 10 and 12, 2L/48 to 10L/48 is suitable for an axial length L of the contra-rotating bearing 26 in consideration of the enhancement of dynamic pressure performance and static pressure performance by lubrication oil (which will be described below with reference to Fig. 18). As illustrated in Figures 13 and 14, an optimum position of an oil feeding section (defined by the oil feed holes 29) is generally backward from the central position of a contra-rotating bearing 26 by L/6 to L/4 (in the left direction of Fig. 13), which depends on the weight of a propeller (rear propeller 103) and the diameter of an inner shaft 23. By positioning the oil feeding section in this way, the static pressure oil supply can produce better effects. Fig. 15 is a sectional view showing has a greater inclination (rake) of the inner shaft 23 can be accommodated. If the relative angle of rake of the end of the contra-rotating bearing 26 with the inner shaft 23 is great, local contact is increased. For this reason, the state of relative rake can be relaxed by forming a horn-shaped rake portion 26A on the end of the contra-rotating bearing 26. The bearing function of the contra-rotating bearing for a contra-rotating propeller in will be described below: (a) Relationship between the number of revolutions of the inner shaft and minimum oil film thickness. Fig. 16 is a chart showing the relationship between the number of revolutions of the inner shaft 23 and a minimum oil film thickness (load carrying capacity). In Fig. 16 the line a represents "an allowable oil film thickness", the line b represents "a minimum oil film thickness obtained by a dynamic pressure load carrying capacity", the line c represents "a minimum oil film thickness obtained by "a (dynamic pressure and static pressure) load carrying capacity", and the line d represents "a dynamic pressure load carrying capacity underarea". When the inner shaft 23 and the contra-rotating bearing 26 rotate at a high speed (for example, a point E), the load carrying capacity is sufficiently generated by a dynamic pressure. Consequently, a necessary oil film thickness can be obtained. Thus, an oil feeding pressure can be reduced to the limit where a rise in temperature of lubrication oil is allowed. In Fig. 16, Max represents "a maximum number of revolutions". The "maximum number of revolutions" means the number of continuous maximum output rotations, that is, the number of revolutions obtained during rated output. When operating in the dynamic pressure load carrying capacity underarea d, that is, a low rotation area in which the load carrying capacity is insufficiently obtained by the dynamic pressure, control is performed so as to increase the load carrying capacity obtained by the static pressure. When operating for a long time in the vicinity of the number of revolutions in which an oil feeding pump (not shown) of a lubrication oil supply system 111 is turned ON/OFF, the oil feeding pump is always turned ON/OFF every time the number of revolutions is slightly changed on the meteorological conditions on the sea. For this reason, operation control is performed so as to draw hysteresis A-B-C-D-E when increasing the number of shaft revolutions and hysteresis E-D-F-B-A when decreasing the number of shaft revolutions as shown in Fig. 16. Thus, once the oil feeding pump is turned ON, it is not turned OFF even if the number of revolutions is slightly increased. (b) Relationship between the ratio of number of revolutions and a minimum oil film thickness Fig. 17 is a chart showing the relationship between the ratio of number of revolutions (the number of revolutions of an outer shaft / the number of revolutions of an inner shaft x 100) and a minimum oil film thickness (load carrying capacity), and the minimum oil film thickness obtained by a dynamic pressure load carrying capacity. In the chart, a line e represents "a circular bearing according to the prior art (Fig. 5)", a line f represents "a bearing without a circular portion on both ends and a line g represents "a contra-rotating bearing according to the invention having a circular portion 41B, 41F at its ends". In the case where the inner shaft 104 and the contra-rotating bearing are circular as shown in Fig. 5 according to the prior art, the operations of carrying lubrication oil by the inner shaft 104 and the contra-rotating bearing which rotate in mutually opposite directions are offset. Consequently, when the inner shaft 104 and the contra-rotating bearing rotate in mutually opposite directions at quite equal speeds so that the ratio of number of revolutions reaches 100 %, the load carrying capacity becomes zero. As shown in Figs. 9 and 11 according to the present invention, however, a plurality of concavo-convex shaped portions or non-circular shaped portions such as the tapered land 42 or the lobed bearing surface 43 are formed on the contra-rotating bearing 26. Consequently, even if the inner shaft 23 and the contra-rotating bearing 26 rotate in mutually opposite directions, a clearance is newly formed between the inner shaft 23 and the contra-rotating bearing 26 so that a load carrying capacity can newly be generated by a dynamic pressure with shaft rotation. As shown by a dotted line g of Fig. 17, accordingly, it is found that the circular bearing has a higher load carrying capacity generated by the dynamic pressure in an area where the ratio of number of revolutions is low, and the contra-rotating bearing 26 on which the tapered lands 42 or lobed bearing surfaces 43 are formed has the higher load carrying capacity generated by the dynamic pressure in an area where the ratio of number of revolutions is high, that is, a propeller propulsion efficiency is increased on the contra-rotating propeller shafting 21. In addition, the dotted line g illustrates that when a rear side land face 41B and a front side land face 41F are formed as shown in Figs. 10 and 12 the minimum oil film thickness obtained is greater than in a bearing where no side land faces 41B, 41F are provided in which use the minimum oil thickness is illustrated by the solid line f. More specifically, the concavo-convex shaped portion such as the tapered land 42 (Fig. 10) or the lobed bearing surface 43 (Fig. 12) is blocked in the axial direction of the contra-rotating bearing 26 by the rear side land face 41B and the front side land face 41F. Consequently, the lubrication oil is stored effectively in the concavo-convex shaped portion so that the generation efficiency of the load carrying capacity obtained by the dynamic pressure and the static pressure can be enhanced. (c) Relationship between the total length of the circular portions and an oil film thickness Fig. 18 shows the relationship between a total length S of the rear side land face 41B and the front side land face 41F and the oil film thickness, where S = SB + SF. Fig 18 (a) is a sectional view showing the contra-rotating bearing, wherein u represents the length of a concavo-convex shaped portion" and L represents "a bearing length". Fig 18 (b) is a chart showing the relationship between the total length of the circular portions and oil film thickness, wherein the line h represents the case of only a dynamic pressure", the line i represents "the case where the static pressure is added to the dynamic pressure", and the range j represents the enhancement of the oil film thickness. In the total length S, "0" represents a full tapered land having neither the land face 41B nor the land face 41F, and "1 = 48/48" represents a full circle having no concavo-convex portions. The ratio of number of revolutions of the contra-rotating bearing 26 (outer shaft) to the inner shaft 23 (the number of revolutions of the outer shaft / the number of revolutions of the inner shaft x 100) is 65 to 90 %. As shown in the chart (b), the oil film thickness has a maximum value within the range where the total length S is L/48 to 8L/48 for the axial bearing length L of the contra-rotating bearing 26 when the load carrying capacity is obtained by dynamic pressure only. In the case where static pressure is added, the oil film thickness has a maximum value within the range where the total length S is 4L/48 to 24L/48. Accordingly, the preferable range is L/48 (a length corresponding to a minimum value obtained in the case where only the dynamic pressure is applied) to 24L/48 (a length corresponding to a maximum value obtained in the case where the static pressure is added). In the case where only the dynamic pressure is applied as shown, the oil film thickness is reduced. If the maximum value is passed, the oil film thickness is reduced more. For this reason, it is more desirable that the total length S of the rear side land face 41B and the front side land face 41F usually has an intermediate value obtained by applying only the dynamic pressure and adding the static pressure, that is, 2.5L/48 to 16L/48. In order to keep the oil film thickness to some extent also in the case where only the dynamic pressure is applied, 2L/48 to 10L/48 is much more desirable in consideration of the great influence on the dynamic pressure side. (d) Relationship between a load carrying capacity and the oil feeding pressure of lubrication oil With reference to Figs. 19 and 20, a load carrying capacity obtained by the static pressure and the oil feeding pressure of lubrication oil will be described below. Fig. 19 is a sectional view in which the core of the inner shaft 23 is slightly eccentric to the contra-rotating bearing 26 in the same manner as in Figs. 8 and 9. Fig. 20 is a chart showing the relationship between the ratio of number of revolutions and the oil film thickness, and the load carrying capacity obtained by the dynamic pressure and the static pressure. In Fig. 20, the line m represents "an oil feeding pressure of 50 kg/cm2 according to the present invention", the line n represents "an oil feeding pressure of 50 kg/cm2 in the circular bearing (Fig. 5) according to the prior art", the line q represents "an oil feeding pressure of 25 kg/cm2 according to the present invention", and the line r represents "an oil feeding pressure of 25 kg/cm2 in the circular bearing (Fig. 5) according to the prior art". As shown in Fig. 19, the pressure of the contra-rotating bearing 26 is reduced to P1 on the lower face of the inner shaft 23 and to P2 on the upper face of the inner shaft 23 through a screw 17 having a small hole for orifice formation or capillary tube formation with respect to a supply pressure PS of the lubrication oil. If a spacing between the outer peripheral face of the inner shaft 23 and the inner peripheral face of the land face 41 portion of the contra-rotating bearing 26 is represented by H1 on the lower face and H2 on the upper face, H1 is equal to H2 when the centers of the inner shaft 23 and the contra-rotating bearing 26 correspond to each other and the resistance of the restriction of the screw 17 having a small hole is equal to the resistance of the restriction of the bearing clearance. Consequently, P1 is equal to P2 so that the load carrying capacity becomes zero. When the inner shaft 23 goes downward by an eccentricity k in the drawing, H1 is smaller than H2 and P2 is smaller than P1. Based on a differential pressure (P1 - P2), the load carrying capacity is generated. As shown in Fig. 20, accordingly, the inner shaft 23 having a non-circular shape such as the tapered land 42 or the lobed bearing surface 43 according to the present invention has a higher load carrying capacity generated by the dynamic pressure. Consequently, an equivalent load carrying capacity is obtained at a lower oil feeding pressure so that an oil film thickness can be kept. As compared with the circular bearing according to the prior art shown in Fig. 5, the oil feeding pressure can be reduced. In the described embodiments, a sufficient oil film is formed on the bearing surface of a contra-rotating bearing which supports the inner shaft of the contra-rotating propeller so that an excellent bearing function can be obtained, even when the inner shaft and the outer shaft rotate in mutually opposite directions at almost equal speeds. The contra-rotating bearing described is suitable for a large-sized contra-rotating propeller of a ship or the like. An excellent bearing function can be obtained in a contra-rotating bearing which supports an inner shaft of a contra-rotating propeller in which the inner shaft and the outer shaft rotate in mutually opposite directions, which is useful for a contra-rotating bearing device for a contra-rotating propeller of a ship in which a large-sized contra-rotating propeller requiring a great load carrying capacity is provided.

Claims: Contra-rotating shafting for a contra-rotating propeller, said shafting comprising an outer shaft (26) for driving a front propeller (101), an inner shaft (23) which is fitted in the outer shaft and is rotatable in the direction opposite to the outer shaft for driving a rear propeller (103), and a contra-rotating bearing provided between the inner shaft and the outer shaft, characterised in that an oil feed port (28) and a plurality of radial oil feed holes (29) connected with the oil feed port are provided in the innershaft for supplying lubrication oil from an external lubrication oil supply system (111) to the inner peripheral face of the bearing to provide a static load carrying capacity, a plurality of concavo-convex shaped portions extending in the axial direction of the bearing for generating, in use, a dynamic pressure load carrying capacity are provided on the inner peripheral face of the bearing facing said inner shaft, and circular portions (41B, 41F) are provided at each end of the concavo-convex shaped portions. Contra-rotating shafting as claimed in claim 1, wherein the concavo-convex shaped portions comprise a tapered land or lobed bearing surface. Contra-rotating shafting as claimed in claim 1 or 2, wherein the radial oil feed holes (29) are provided backward in the axial direction of the bearing from a central position of the bearing by a distance of L/6 to L/4, where L is the length of the bearing. Contra-rotating shafting as claimed in claim 1, 2 or 3, wherein the total length of the circular portions (41B, 41F) is L/48 to 24 L/48, where L is the length of the bearing. Contra-rotating shafting as claimed in claim 4, wherein the total length of the circular portions is 2L/48 to 10L/48, where L is the length of the bearing. A contra-rotating propeller comprising contra-rotating shafting as claimed in any one of the preceding claims and having a front propeller (101) on said outer shaft (26) and a rear propeller (103) on said inner shaft (23). A ship having a contra-rotating propeller as claimed in claim 6.

Inventors: ASHIDA SATOSHI, KEIRIMBO SATOSHI, MATSUDA MASAYASU, NAKAYAMA KIMIHIKO, NITTA KEIICHI, OHTA KAZUHIDE, OHTANI SHINICHI, SHIBUYA HIDEKI, ASHIDA, SATOSHI, KEIRIMBO, SATOSHI, MATSUDA, MASAYASU, NAKAYAMA, KIMIHIKO, NITTA, KEIICHI, OHTA, KAZUHIDE, OHTANI, SHINICHI, SHIBUYA, HIDEKI
Applicants: HITACHI SHIPBUILDING ENG CO, KAWASAKI HEAVY IND LTD, MITSUI SHIPBUILDING ENG, NIPPON KOKAN KK, SUMITOMO HEAVY INDUSTRIES, HITACHI ZOSEN CORPORATION, KAWASAKI JUKOGYO KABUSHIKI KAISHA, MITSUI ENGINEERING & SHIPBUILDING CO., LTD, NKK CORPORATION, SUMITOMO HEAVY INDUSTRIES, LTD.
Application year: 1995
Main classification: B63H23
IPC codes: F16C33, B63H23