REVERSING BEARING DEVICE FOR DOUBLE REVERSING PROPELLER

Abstract: A hollow poriton is defined in the axis of an inner shaft (2) to form a center oil feed passage (3), and a plurality of oil feed ports (4) penetrating through an outer peripheral surface of the inner shaft (2) from this center oil feed passage (3) are aligned radially within the range (L) of a bearing surface of the inner shaft (2). An oil groove (5) in an axial direction, inclusive of an opening (4a) of each oil feed hole (4) on the inner shaft surface side, is disposed on the inner shaft outer peripheral surface. In this way, a reversing bearing device for double reversing propeller for driving the inner shaft (2) and the outer shaft (2) in mutually opposite directions is constituted. A plurality of concavoconvex portions are formed on the inner peripheral surface of the reversing bearing in place of the oil groove in the axial direction of the bearing, and complete circle portions are disposed at both end portions of the concavoconvex portions in the axial direction so as to constitute a reversing bearing device for double reversing propeller. In these bearing devices, a sufficient oil film is formed on the bearing face of the reversing bearing in the rotation range where the inner shaft and the outer shaft rotate in mutually opposite directions at a substantially equal speed, and a satisfactory bearing function can be obtained.

Description: The present invention relates to a contra-rotating bearing device for a contra-rotating propeller. Conventionally, a contra-rotating propeller has been known 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 utilize 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. 9 is a partial broken side view showing a contra-rotating propeller according to the prior art, and Fig. 10 is a sectional view taken along the line E - E shown in Fig. 9. 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. 10, 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 (Fig. 11) 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 prior art bearings, a floating bush 114 is provided between the outer shaft 102 and the inner shaft 104 as shown in a sectional view (Fig. 12). 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. The above mentioned problems with the prior art are solved to some extent by the contra-rotating bearing device disclosed in Japanese Examined Patent Publication No. 5-45479 entitled "STERN TUBE BEARING SYSTEM OF CONTRA-ROTATING PROPELLER". Figure 13 shows a sectional view of a hydrostatic bearing disclosed in that Patent Publication. Figure 13 shows a contra-rotating bearing device for a contra-rotating propeller comprising an inner shaft for driving a rear propeller and an outer shaft for driving a front propeller, both shafts rotating in mutually opposite directions, wherein a hollow portion is provided on the core of the inner shaft to form an oil feed port, a plurality of oil feed holes which are connected with both of the outer peripheral face of the inner shaft within the range of the bearing surface of the inner shaft and the oil feed port are radially provided. 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. 14 (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 improved bearing function can be displayed. The present invention provides a contra-rotating bearing device for a contra-rotating propeller comprising an inner shaft for driving a rear propeller and an outer shaft for driving a front propeller, both shafts rotating in mutually opposite directions, wherein a hollow portion is provided on the core of the inner shaft to form an oil feed port, a plurality of oil feed holes which are connected with both of the outer peripheral face of the inner shaft within the range of the bearing surface of the inner shaft and the oil feed port are radially provided, characterised in that oil grooves, each of which includes an inner shaft surface side opening portion of the oil feed hole, are provided on the outer peripheral face of the inner shaft. A plurality of said oil feed holes may be radially provided in a line. Optionally, a plurality of said oil feed holes are radially provided, the oil feed holes being axially provided in a plurality of lines, and said oil grooves are circumferential or axial. Such oil feed holes may be offset circumferentially. Preferably, the cross sectional area of a said oil groove is formed so as to be decreased from the inner shaft surface side opening portion of the oil feed hole to ends thereof. The embodiments hereinafter describe: a contra-rotating bearing device for a contra-rotating propeller which can lubricate the contra-rotating bearing by using a small number of oil feed holes without reducing the strength of the inner shaft; a contra-rotating bearing device for a contra-rotating propeller which can supply lubrication oil having a pressure which is necessary within the range of the bearing surface of the inner shaft by simple working; a contra-rotating bearing device for a contra-rotating propeller which can particularly give a load carrying capacity to the contra-rotating bearing during uniform contra-rotation in which an inner shaft and an outer shaft rotate in mutually opposite directions at almost equal speeds, or in the state close thereto; a contra-rotating bearing device for a contra-rotating propeller to surely keep a load carrying capacity by supporting the inner shaft with only the load carrying capacity generated by the dynamic pressure of the lubrication oil in the high rotation area of an engine and by increasing an oil feeding pressure to add a static pressure in a low rotation area in which it is hard to generate the sufficient load carrying capacity by only the dynamic pressure; and a contra-rotating bearing device for a contra-rotating propeller which can generate the sufficient load carrying capacity with a low oil feeding pressure by using the non-circular shape of the contra-rotating bearing. In the embodiment, lubrication oil fed through the oil feed port of the inner shaft is supplied to the bearing surface through a plurality of the oil feed holes which are provided radially within the range of the bearing surface of the inner shaft and connected with the outer peripheral face of the inner shaft. Therefore, the lubrication oil having a pressure which is necessary for almost the whole range of the bearing surface is supplied by the oil grooves provided on the outer peripheral face of the inner shaft including the inner shaft surface side opening portions of the oil feed holes so that an oil film is formed to support the inner shaft. Thus, the function of the contra-rotating bearing for a contra-rotating propeller for causing both shafts to rotate in mutually opposite directions can be obtained. Accordingly, the contra-rotating bearing which can display the bearing function can be formed with a small number of oil feed holes. Consequently, a reduction in strength of the shaft can be prevented and processing can be performed easily to decrease working manhour. Thus, the manufacturing time and the manufacturing costs for the contra-rotating bearing can be reduced greatly. As will be appreciated from Figures 1 to 8 hereinafter the plurality of oil feed holes are radially provided in a line, and axial oil grooves each of which includes an inner shaft surface side opening portion of the oil feed hole are provided on the outer peripheral face of the inner shaft. Consequently, the lubrication oil fed through the oil feed port is supplied to the bearing surface through the oil feed holes which are radially provided in a line within the range of the bearing surface of the inner shaft and connected with the outer peripheral face of the inner shaft. Therefore, the lubrication oil having a pressure which is necessary for almost the whole range of the bearing surface is supplied by the axial oil grooves provided on the outer peripheral face of the inner shaft including the inner shaft surface side opening portions of the oil feed holes so that the inner shaft can be supported. In Figures 1 to 8, the plurality of oil feed holes are radially provided, the oil feed hole being axially provided in a plurality of lines, and circumferential oil grooves or axial oil grooves each of which includes an inner shaft surface side opening portion of the oil feed hole are provided on the outer peripheral face of the inner shaft. Consequently, the lubrication oil fed through the oil feed port is supplied to the bearing surface through the oil feed holes which are radially provided within the range of the bearing surface of the inner shaft and axially provided in a plurality of lines, and connected with the outer peripheral face of the inner shaft. Therefore, the lubrication oil having a pressure which is necessary for almost the whole range of the bearing surface is supplied by the circumferential or axial oil grooves which are provided on the outer peripheral face of the inner shaft including the inner shaft surface side opening portions of the oil feed holes so that the inner shaft can be supported. When the oil feed holes are axially provided in a plurality of lines and offset circumferentially, the lubrication oil having a necessary pressure is easily supplied efficiently to almost the whole range of the bearing surface through the oil feed holes. Thus, the inner shaft can be supported. When the cross-sectional area of the oil groove is formed so as to be decreased from the inner shaft surface side opening portion of the oil feed hole to ends thereof, the cross-sectional area of the oil groove can be formed so as to be decreased from the inner shaft surface side opening portion of the oil feed hole to ends thereof. Accordingly, the pressure of the lubrication oil can be optimized within the range of the bearing surface by changing the cross-sectional area of the oil groove. Thus, a contra-rotating bearing device which generates an oil pressure according to a load within the range of the bearing surface can be formed. In order that the present invention may be well understood, some embodiments thereof which are given by way of example only, will now be described with reference to the accompanying drawings, in which : Figure 1 is a view showing a contra-rotating bearing device for a contra-rotating propeller according to the first embodiment of the present invention, wherein (a) is a side sectional view and (b) is a sectional view taken along the line A - A of (a); Figures 2 (a) and (b) are sectional views showing an oil groove in the circumferential direction shown in Figure 1; Figure 3 is a view showing an example of dimensions according to the first embodiment in Figure 1, wherein (a) is a side sectional view and (b) is an enlarged view showing the oil groove; Figure 4 is a side sectional view showing another example of the axial section of the oil groove in Figure 1; Figure 5 is a side sectional view showing the second embodiment of the present invention; Figure 6 is a view showing the third embodiment of the present invention, wherein (a) is a sectional view and (b) is a sectional view taken along the line B - B of (a); Figure 7 is a side sectional view showing the fourth embodiment of the present invention; Figure 8 is a side sectional view showing the fifth embodiment of the present invention; Figure 9 is a partial broken side view showing a contra-rotating propeller according to the prior art; Figure 10 is a sectional view taken along the line E - E in Figure 9; Figure 11 is a sectional view showing a contra-rotating bearing device for a contra-rotating propeller according to the prior art; Figure 12 is a sectional view showing another contra-rotating bearing device for a contra-rotating propeller according to the prior art; Figure 13 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; and Figure 14 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). In the drawings for the following description, a radial clearance Cr and the like are exaggerated. In Fig. 1(a), the right side is the fore direction, and the left side is the after direction. As shown, an outer shaft 1 for driving a front propeller of the contra-rotating propeller and an inner shaft 2 for driving a rear propeller are provided almost concentrically so as to rotate in mutually opposite directions. The outer shaft 1 is supported by a journal bearing provided on a hull, which is not shown. The inner shaft 2 is supported by the contra-rotating bearing device T1 formed in the outer shaft 1. In the contra-rotating bearing device T1 according to the first embodiment, a hollow portion is provided on the core of the inner shaft 2 to form an oil feed port 3, and a plurality of oil feed holes 4 which are connected with both of the outer peripheral face of the inner shaft and the oil feed port 3 are provided within a range L of a bearing surface. In the embodiment, the oil feed holes 4 are provided in a line on the rear end side within the range L of the bearing surface, that is, the after side having a greater load on the propeller side. In the first embodiment, eight oil feed holes 4 are radially provided. Axial oil grooves 5 are provided within the range L of the bearing surface on the outer peripheral face of the inner shaft including an inner shaft surface side opening portions 4a of the oil feed holes 4. According to the present embodiment, it is preferable that the number of the oil feed holes 4 should be three or more. The oil grooves 5 are formed from a plurality of oil feed holes 4 toward the fore side in the axial direction, and has a structure in which lubrication oil fed from the oil feed holes 4 generates a predetermined oil pressure that is necessary for the range L of the bearing surface along the oil groove 5. The oil groove 5 can be easily processed because it is formed on the surface of the inner shaft 2. As shown by the sectional views of Figs. 2 (a) and (b), furthermore, the oil groove 5 may be a deep groove in (a) or a groove having a shallow oil reservoir in (b). In other words, it is sufficient that the oil groove 5 can generate a predetermined oil pressure within the range L of the bearing surface. As will be seen from Figures 2(a) and 2(b), the cross-sectional area of an oil groove is formed so as to be decreased from the inner shaft surface side opening portion the oil feed hole to ends thereof. An example of dimensions obtained by an experiment in the contra-rotating bearing device T1 according to the first embodiment will be described below with reference to the side sectional view of Fig. 3 (a) and the enlarged view showing the oil groove of Fig. 3 (b). The following dimensions are variable depending on the loading conditions of the bearing, whose example will be described. As shown, the range of the bearing surface (bearing length) is expressed by L, the outer diameter of the inner shaft is expressed by D, a radius clearance is expressed by Cr, the axial length of the oil groove is expressed by v, a width is expressed by w, and oil is fed in eight directions on a section with L/D = in this example. Eight oil feed holes 4 are provided in a line in positions apart from the center of the range L of the bearing surface backward by a predetermined distance of L1. An oil groove 5 having an axial length v and a width w is provided around an inner shaft surface side opening portion 4a of the oil feed hole 4. It is preferable that the predetermined distance L1 should be L/6 to L/4, the width w of the oil groove 5 should be πD/32 and the axial length v should be 1w to 2w. It is preferable that the depth of the oil groove 5 should be three to five times as much as the radius clearance Cr. According to general documents, a pressure drop can be ignored when the depth of the oil groove 5 is ten times as much as the radius clearance Cr or more. Consequently, it is supposed that a great change in the pressure is not caused in the oil groove 5 even through the depth of the oil groove 5 is three to five times as much as the radius clearance Cr or more. Therefore, if the position of the oil groove 5 is set, the pressure of the oil groove 5 is not changed greatly even though the position of the opening portion 4a of the oil feed hole 4 is changed axially. Thus, bearing performance is not affected greatly. As shown by a sectional view of Fig. 4, the oil groove 5 according to the first embodiment may be tapered in such a manner that it gradually becomes shallower from the position where the oil feed hole 4 is provided toward an end 5a, that is, an axial sectional area is decreased from the inner shaft surface side opening portion of the oil feed hole 4 to the end thereof. By such formation, a difference between an oil pressure in the position of the oil feed hole 4 and an oil pressure in the position of the end of the oil groove 5 can be made. Consequently, the oil feed hole 4 is provided in a position where a high oil pressure is necessary within the range L of the bearing surface to reduce the oil pressure in a position apart from the oil feed hole 4 so that the optimum pressure of the lubrication oil can be obtained over the range L of the bearing surface. In order to decrease the cross sectional area of the oil groove 5, a groove width, a groove depth or both of them can be decreased. The contra-rotating bearing device T1 for a contra-rotating propeller having the above-mentioned structure according to the first embodiment functions as a contra-rotating bearing which supports the inner shaft 2 in the following manner. More specifically, the oil fed from the oil feed port 3 of the inner shaft 2 is supplied to the inner shaft surface through the oil feed hole 4 and flows into the range L of the bearing surface along the oil groove 5. The contra-rotating bearing device T1 functions to generate a predetermined oil pressure within the range L of the bearing surface so that an oil film is formed and the inner shaft 2 is supported. Thus, the contra-rotating bearing device T1 can be formed by the oil feed holes 4 provided on the inner shaft 2 in a line. Consequently, a small number of oil feed holes 4 are provided on the inner shaft 2 so that the contra-rotating bearing device T1 can be formed without reducing an axial strength. A contra-rotating bearing device T2 according to the second embodiment will be described below with reference to a side sectional view of Fig. 5. In the second embodiment, the oil feed hole 4 according to the first embodiment is provided in almost the central portion within a range L of a bearing surface. Therefore, the same structures have the same reference numerals as in the first embodiment and their description will be omitted. As shown, the oil feed hole 4 according to the second embodiment is provided in almost the central portion within the range L of the bearing surface, and an oil groove 5 is provided from the oil feed hole 4 toward the fore and after sides within the range L of the bearing surface. In case of the second embodiment, the width or depth of the oil groove 5 provided from an opening portion 4a of the oil feed hole 4 toward the fore side and the width or depth of the oil groove 5 provided from the opening portion 4a toward the after side are set to optimum values so that an oil pressure within the range L of the bearing surface can be controlled to obtain an optimum function as the contra-rotating bearing device T2. Also in the second embodiment, the same functions and effects as in the first embodiment can be obtained. A contra-rotating bearing device T3 according to the third embodiment will be described below with reference to a side sectional view in figs. 6 (a) and (b) and a sectional view taken along the line B - B in Figs. 6 (a) and (b). The same structures have the same reference numerals as in the first embodiment and their description will be omitted. In the third embodiment, oil feed holes 4 are axially provided in a plurality of lines, that is, three lines within a range L of a bearing surface, each line having two oil feed holes 4 as shown. The oil feed holes 4 are provided in positions where the phases of the first and the second lines are shifted (hereinafter referred to as "offset") by 90 degrees in the circumferential direction. The oil feed holes 4 are provided in positions where the second and third lines are offset by 90 degrees. Oil grooves 6 are provided in the circumferential direction within the range L of the bearing surface including inner shaft surface side opening portions 4a of the oil feed holes 4. Also in the third embodiment, the surface of an inner shaft 2 is processed. Consequently, processing can be easily performed in the same manner as in the first embodiment. The contra-rotating bearing device T3 for a contra-rotating propeller having the above-mentioned structure according to the third embodiment functions to support the inner shaft 2 in the following manner. More specifically, oil fed from an oil feed port 3 of the inner shaft 2 is supplied from the oil feed holes 4 which are axially provided in a plurality of lines into the range L of the bearing surface, and a predetermined oil pressure is generated on the surface of the inner shaft 2 to form an oil film. Thus, the contra-rotating bearing function can be displayed. Since the propeller is provided on the after side, a load is usually great on the after side. Therefore, it is sufficient that the oil pressure is generated within the range L of the bearing surface corresponding to the load therein by setting the diameters of the oil feed holes 4, the width of the oil groove 6, the depth of the oil groove 6 and the like on the after and fore sides to optimum values. Other functions and effects are the same as in the first embodiment. A contra-rotating bearing device T4 according to the fourth embodiment will be described below with reference to a side sectional view of Fig. 7. In the fourth embodiment, the number of oil feed holes 4 which are axially provided in the third embodiment is increased and the oil feed holes 4 are offset by a predetermined amount. The same structures have the same reference numerals as in the third embodiment and their description will be omitted. In the fourth embodiment, the oil feed holes 4 are axially provided in a plurality of lines, that is, five lines within a range L of a bearing surface, each line having two oil feed holes 4 as shown. The oil feed holes 4 are provided in such a manner that the first and the second lines are shifted in the circumferential direction, that is offset, by 45 degrees. The second and the third lines are also offset by 45 degrees, and the following lines are sequentially offset by 45 degrees. Oil grooves 6 are provided in the circumferential direction within the range L of the bearing surface including an inner shaft surface side opening portions 4a of the oil feed holes 4. Also in the fourth embodiment, the surface of an inner shaft 2 is processed. Consequently, processing can be easily performed. The contra-rotating bearing device T4 for a contra-rotating propeller having the above-mentioned structure according to the fourth embodiment functions in the same manner as the contra-rotating bearing device T3 for a contra-rotating propeller in the third embodiment described above. More specifically, oil fed from an oil feed port 3 of the inner shaft 2 is supplied into the range L of the bearing surface through the oil feed holes 4 which are axially provided in a plurality of lines, and a predetermined oil pressure is operated on the surface of the inner shaft 2 to form an oil film. Thus, the contra-rotating bearing function can be displayed. According to the fourth embodiment, the oil feed holes 4 are axially provided in more lines than in the third embodiment. Consequently, the oil pressure can be controlled corresponding to a load within the range L of the bearing surface. Other functions and effects are the same as in the third embodiment described above. A contra-rotating bearing device T5 according to the fifth embodiment will be described below with reference to a side sectional view of Fig. 8. In the fifth embodiment, a circumferential oil groove in the third embodiment is changed into an axial oil groove. As shown, oil feed holes 4 are axially provided in a plurality of lines, that is, three lines within a range L of a bearing surface, each line having two oil feed holes 4 in the same manner as in the third embodiment. The oil feed holes 4 are provided in positions where the first and the second lines are circumferentially offset by 90 degrees. The second and the third lines are also offset by 90 degrees. Oil grooves 5 are axially provided within the range L of the bearing surface including inner shaft surface side opening portions 4a of the oil feed holes 4. The contra-rotating bearing device T5 for a contra-rotating propeller having the above-mentioned structure according to the fifth embodiment functions in the same manner as the contra-rotating bearing device T3 in the third embodiment described above. More specifically, oil fed from the oil feed port 3 of the inner shaft 2 is supplied into the range L of the bearing surface through the oil feed holes 4 which are axially provided in a plurality of lines, and a predetermined oil pressure is generated on the surface of the inner shaft 2 to form an oil film. Thus, the contra-rotating bearing function can be obtained. Also in the fifth embodiment, the oil pressure corresponding to a load within the range L of the bearing surface can be generated by setting the diameters of the oil feed holes 4, the width of the oil groove 5, the depth of the oil groove 5 and the like on the after and fore sides to optimum values in the same manner as in the third embodiment, or by making the tapered shape as shown in Fig. 4. With the embodiments hereinbefore described a sufficient oil film is formed on the bearing surface which supports the inner shaft of the contra-rotating propeller so that an excellent bearing function can be obtained. The embodiments display the bearing function of a contra-rotating bearing when an inner shaft and an outer shaft rotate in mutually opposite directions at almost equal speeds, and are particularly suitable for a large-sized contra-rotating propeller of a ship or the like. An excellent bearing function can be obtained as a contra-rotating bearing which supports an inner shaft of a contra-rotating propeller in which the inner shaft and an outer shaft rotate in mutually opposite directions, which is useful for the general contra-rotating bearing device for supporting the inner shaft of the contra-rotating propeller, and more particularly suitable for a contra-rotating bearing device for a contra-rotating propeller of a ship which is provided with a large-sized contra-rotating propeller requiring a great load carrying capacity.

Claims: A contra-rotating bearing device for a contra-rotating propeller comprising an inner shaft for driving a rear propeller and an outer shaft for driving a front propeller, both shafts rotating in mutually opposite directions, wherein a hollow portion is provided on the core of the inner shaft to form an oil feed port, a plurality of oil feed holes which are connected with both of the outer peripheral face of the inner shaft within the range of the bearing surface of the inner shaft and the oil feed port are radially provided, characterised in that oil grooves, each of which includes an inner shaft surface side opening portion of the oil feed hole, are provided on the outer peripheral face of the inner shaft. A contra-rotating bearing device for a contra-rotating propeller as defined in Claim 1, wherein a plurality of said oil feed holes are radially provided in a line and said oil grooves are axially provided. A contra-rotating bearing device for a contra-rotating propeller as defined in Claim 1, wherein a plurality of said oil feed holes are radially provided, the oil feed holes being axially provided in a plurality of lines, and said oil grooves are circumferential or axial. A contra-rotating bearing device for a contra-rotating propeller as defined in Claim 3, wherein the oil feed holes which are axially provided in a plurality of lines are offset circumferentially. A contra-rotating bearing device for a contra-rotating propeller as defined in any of Claims 1 to 4, wherein the cross sectional area of a said oil groove is formed so as to be decreased from the inner shaft surface side opening portion of the oil feed hole to ends thereof.

Inventors: ASHIDA SATOSHI, KEIRIMBO SATOSHI, MATSUDA MASAYASU, NAKAYAMA MIKIHIKO, NITTA KEIICHI, OHTA KAZUHIDE, OHTANI SHINICHI, SHIBUYA HIDEKI, ASHIDA, SATOSHI, KEIRIMBO, SATOSHI, MATSUDA, MASAYASU, NAKAYAMA, MIKIHIKO, 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: F16C17, F16C32, B63H23, B63H5, F16C33