The present invention relates to a bearing apparatus for use in a horizontal-shaft pump or the like, and more particularly to a bearing apparatus which is capable of appropriately supplying lubricating oil to a bearing even if a rotational shaft becomes larger in diameter or a rotational speed thereof is higher. Further, the present invention relates to a pump including such a bearing apparatus.
Horizontal-shaft type of rotary machines (e.g., horizontal-shaft pumps), in which a rotational shaft is installed horizontally, have bearing apparatuses disposed in the vicinity of the ends of the rotational shaft in order to rotatably support the rotational shaft. Further, a lubricating oil reservoir that stores lubricating oil for lubricating and cooling the bearing is provided inside or outside the bearing apparatus.
Means for supplying the lubricating oil from the lubricating oil reservoir to the bearing includes a forced oil supply apparatus that uses external power and a self-lubrication device that uses no external power. The forced oil supply apparatus supplies the lubricating oil, by using external power, from the lubricating oil reservoir disposed outside of the bearing apparatus to the bearing disposed in the bearing apparatus. The self-lubrication device scoops up the lubricating oil, by using a rotational force of the rotational shaft, from the lubricating oil reservoir disposed below the rotational shaft in the bearing apparatus to supply the lubricating oil to the bearing.
As shown in
Furthermore, an installation space for the forced oil supply apparatus 26 is required in addition to an installation space for the horizontal-shaft pump and the electric motor for driving this horizontal-shaft pump. As a result, an installation space required by the pump system in its entirety becomes large.
Next, a conventional bearing apparatus which uses a self-lubrication device will be described. Self-lubrication devices using an oil ring and using an oil disk have heretofore been put to use.
However, with the conventional oil-ring-type self-lubrication device, when the peripheral speed of the outer circumferential surface of the rotational shaft 1 (hereinafter simply referred to as peripheral speed) increases due to an increase in the diameter of the rotational shaft 1, an increase in the speed of the rotational shaft 1 or the like, the rotation of the oil rings 20 cannot follow the rotation of the rotational shaft 1. Specifically, the rotational speed of the oil rings 20 greatly decreases compared with the rotational speed of the rotational shaft 1, so that the oil rings 20 cannot appropriately scoop up the lubricating oil. As a result, desired lubricating performance and cooling performance cannot be obtained.
On the other hand, an oil-disk-type self-lubrication device which uses an oil disk fixed to a rotational shaft, has no problem that the oil disk cannot follow the rotation of the rotational shaft, because the oil disk rotates together with the rotational shaft. However, when the rotational shaft rotates at a high speed, centrifugal force which acts on the lubricating oil scooped up by the oil disk, are increased. As a result, the lubricating oil scooped up by the oil disk is scattered only in radial direction of the oil disk, and cannot be supplied to a bearing which is disposed away from the oil disk in axial direction of the rotational shaft. Therefore, when the rotational shaft has an increased diameter or the rotational speed of the rotational shaft increases, it has been difficult to apply the conventional self-lubrication device to a bearing apparatus.
There has heretofore been known an oil-disk-type self-lubrication device which is improved for reliably guiding lubricating oil scooped up by an oil disk. The improved oil-disk-type self-lubrication device is shown in
However, as the diameter of the rotational shaft 1 or the rotational speed thereof increases, centrifugal force which acts on the lubricating oil held by the recess 80 and the protrusion 81 increases, so that the lubricating oil continues to remain in the recess 80, and cannot drop into the oil receiver 8 as shown in
Patent document 1: Japanese laid-open patent publication No. 06-165430
Patent document 2: Japanese laid-open patent publication No. 06-341437
The present invention has been made in view of the various problems described above. It is therefore an object of the present invention to provide a bearing apparatus capable of stably supplying an appropriate amount of lubricating oil to a bearing with a simple arrangement, even if the peripheral speed of the rotational shaft increases. It is also an object of the present invention to provide a pump which includes such a bearing apparatus.
One aspect of the present invention for achieving the above object provides a bearing apparatus including: a bearing unit for receiving a load of a rotational shaft; a lubricating oil reservoir disposed below the bearing unit; and an oil disk fixed to the rotational shaft and rotatable together with the rotational shaft to scoop up lubricating oil stored in the lubricating oil reservoir; wherein the oil disk has a side surface facing the bearing unit, the side surface having a groove formed therein; an outer-circumferential-side end surface of the groove extends parallel to an axial direction of the rotational shaft; the outer-circumferential-side end surface constitutes a guide surface for changing a direction of movement of the lubricating oil in the groove from a radial direction of the oil disk to the axial direction of the rotational shaft; and the outer-circumferential-side end surface is connected to the side surface of the oil disk.
In a preferred aspect of the present invention, the groove includes a plurality of grooves arranged around an axis of the oil disk.
In a preferred aspect of the present invention, the outer-circumferential-side end surface includes a large-diameter portion and a small-diameter portion located at different distances from the center of the oil disk.
In a preferred aspect of the present invention, the outer-circumferential-side end surface has a slope surface which is inclined obliquely with respect to the axial direction of the rotational shaft.
Another aspect of the present invention provides a bearing apparatus including: a bearing unit for receiving a load of a rotational shaft; a lubricating oil reservoir disposed below the bearing unit; and an oil disk fixed to the rotational shaft and rotatable together with the rotational shaft to scoop up lubricating oil stored in the lubricating oil reservoir; wherein the oil disk has a side surface facing the bearing unit, the side surface having a circumferential wall projecting toward the bearing unit and extending around the rotational shaft; an inner circumferential surface of the circumferential wall extends parallel to an axial direction of the rotational shaft; and the inner circumferential surface of the circumferential wall constitutes a guide surface for changing a direction of movement of the lubricating oil on the side surface of the oil disk from a radial direction of the oil disk to the axial direction of the rotational shaft.
In a preferred aspect of the present invention, the inner circumferential surface of the circumferential wall includes a large-diameter portion and a small-diameter portion located at different distances from the center of the oil disk.
In a preferred aspect of the present invention, the inner circumferential surface of the circumferential wall has a slope surface which is inclined obliquely with respect to the axial direction of the rotational shaft.
Another aspect of the present invention provides a bearing apparatus including: a bearing unit for receiving a load of a rotational shaft; a lubricating oil reservoir disposed below the bearing unit; and an oil disk fixed to the rotational shaft and rotatable together with the rotational shaft to scoop up lubricating oil stored in the lubricating oil reservoir; wherein the oil disk has a first side surface facing the bearing unit, a second side surface located opposite to the first side surface, and a plurality of through-holes extending from the first side surface to the second side surface; the through-holes have outer-circumferential-side surfaces extending parallel to an axial direction of the rotational shaft; and the outer-circumferential-side surfaces of the through-holes are connected to the first side surface and the second side surface of the oil disk.
In a preferred aspect of the present invention, the outer-circumferential-side surface includes a large-diameter portion and a small-diameter portion located at different distances from the center of the oil disk.
In a preferred aspect of the present invention, the outer-circumferential-side surface has a slope surface which is inclined obliquely with respect to the axial direction of the rotational shaft.
In a preferred aspect of the present invention, the bearing apparatus further includes: a second bearing unit for receiving the load of the rotational shaft; wherein the second side surface faces the second bearing unit.
Another aspect of the present invention provides a pump including: a rotational shaft; an impeller fixed to the rotational shaft; and the bearing apparatus described above, for rotatably supporting the rotational shaft.
According to the present invention, even when strong centrifugal force acts on the lubricating oil scooped up by the oil disk which rotates at a high peripheral speed, the outer-circumferential-side end surface of the groove formed in the oil disk prevents the lubricating oil from moving radially. As a result, the lubricating oil is prevented from being scattered only in a radial direction of the oil disk. Furtheimore, since the outer-circumferential-side end surface of the groove extends parallel to the axial direction of the rotational shaft, the outer-circumferential-side end surface serves as a guide surface for guiding the lubricating oil moved radially outwardly under the centrifugal force, in a direction parallel to the axial direction of the rotational shaft. Therefore, the oil disk enables the lubricating oil to being scattered in the axial direction of the rotational shaft. As a result, it is possible to stably supply the lubricating oil to the bearing unit which is located away from the oil disk in the axial direction of the rotational shaft. These advantages are also achieved in a case where the oil disk has a circumferential wall thereon or through-holes therein.
In this manner, according to the present invention, even under the high-peripheral-speed conditions in which it has been difficult for the conventional oil ring and oil disk to supply lubricating oil, it is possible to supply lubricating oil stably to the bearing unit in the bearing apparatus with a simple arrangement such as grooves, a circumferential wall, or through-holes. Therefore, since the applicable range of the bearing apparatus is widened without using a forced oil supply apparatus, the installation area for a pump is reduced and the cost of the pump is lowered, so that it is possible to provide a pump which is highly competitive.
Embodiments of the present invention will be described below with reference to the drawings. In the present specification, a polar coordinate system whose origin is located at a central axis of a rotational shaft of a pump, is defined. In this polar coordinate system, a longitudinal direction of the rotational shaft is referred to as an axial direction, a direction perpendicular to the axial direction is referred to as a radial direction, and a direction around the outer circumferential surface of the rotational shaft is referred to as a circumferential direction.
The impeller 2 is disposed in a pump casing 5. The pump casing 5 shown in
The impeller 2 in the illustrated example has a double-suction structure for sucking the liquid from both sides thereof. Liquid inlets of the impeller 2 are equipped with mouth rings 2A, 2B, respectively. These mouth rings 2A, 2B are designed to have different diameters, so that a thrust force due to a differential pressure is applied in one direction along the rotational shaft 1 to allow the rotational shaft 1 to rotate stably. The thrust force is supported by a thrust bearing unit 9A of the bearing apparatus 9. Since the thrust force acts as a load on the thrust bearing unit 9A, it is necessary to supply an appropriate amount of lubricating oil to the thrust bearing unit 9A to cool the thrust bearing unit 9A while lubricating it. Therefore, the bearing apparatus 9, which will be described later, according to the embodiment of the present invention is provided. The thrust bearing unit 9A is lubricated and cooled by lubricating oil stored in a lubricating oil reservoir 10, and the lubricating oil in the lubricating oil reservoir 10 is cooled by a cooling jacket 27 attached to the lubricating oil reservoir 10.
In addition to this thrust bearing unit 9A, two radial bearing units 9B, 9B are disposed in the vicinity of the both ends of the rotational shaft 1. The rotational shaft 1 is supported by the two radial bearing units 9B, 9B and the one thrust bearing unit 9A. In the present embodiment, sleeve-type bearings are used as the radial bearing units 9B, and conventional self-lubrication devices with oil rings 20 are used as the sleeve-type radial bearing units 9B, 9B.
The impellers 2 are disposed in a pump casing 5. When the impellers 2 are rotated as the rotational shaft 1 rotates, a liquid such as water is sucked from a suction port 3, a pressure of the liquid is increased by actions of the impellers 2 and the guide vanes 6, and then the liquid is discharged from an outlet port 4. Since the plurality of impellers 2 are arranged so as to face in the same direction, thrust forces generated by differential pressures between the adjacent impellers 2 are superposed by the number of impellers 2, thereby generating a large thrust force. This thrust force is canceled out by a balancing device 7 provided in the horizontal-shaft multi-stage pump 100. However, during transient operation, a certain amount of thrust force remains. This remaining thrust force is supported by a thrust bearing unit 9A of the bearing apparatus 9. Since the remaining thrust force acts as a load on the thrust bearing unit 9A, it is necessary to supply an appropriate amount of lubricating oil to the thrust bearing unit 9A to cool the thrust bearing unit 9A while lubricating it.
In addition to the thrust bearing unit 9A, two radial bearing units 9B, 9B are disposed in the vicinity of the both ends of the rotational shaft 1. The rotational shaft 1 is supported by the two radial bearing units 9B, 9B and the one thrust bearing unit 9A. In the present embodiment, sleeve-type bearings are used as the radial bearing units 9B, 9B, and conventional self-lubrication devices with oil rings 20 are used as the sleeve-type radial bearing units 9B, 9B. The structure of the bearing apparatuses 9, 9 disposed in the vicinity of the both ends of the rotational shaft 1 is the same as the structure of those in the horizontal-shaft single-stage pump shown in
In either one of the horizontal-shaft pumps 100 shown in
A lubricating oil reservoir 10 is disposed below the thrust bearing unit 9A and the radial bearing unit 9B, and a free surface (lubricating oil surface) of lubricating oil stored in the lubricating oil reservoir 10 is indicated by a dotted line with a symbol 10A. The amount of lubricating oil is controlled such that the free surface 10A in the lubricating oil reservoir 10 is constant. A cooling jacket 27 is provided below the lubricating oil reservoir 10, and the lubricating oil in the lubricating oil reservoir 10 is cooled by a coolant flowing through the cooling jacket 27. Instead of the cooling jacket 27, a finned air cooling structure may be employed. Alternatively, a finned coolant tube may be inserted in the lubricating oil reservoir 10 for directly cooling the lubricating oil.
The bearing apparatus 9 includes an oil disk 12 disposed between the thrust bearing unit 9A and the radial bearing unit 9B and fixed to the rotational shaft 1. Since the oil disk 12 is fixed to the rotational shaft 1, the oil disk 12 rotates at the same rotational speed as the rotational shaft 1 at all times. A lower portion of the oil disk 12 is immersed in the lubricating oil in the lubricating oil reservoir 10. The oil disk 12 is rotated as the rotational shaft 1 rotates, thereby scooping up the lubricating oil stored in the lubricating oil reservoir 10. As shown in
The guide disks 15A, 15B have inner surfaces located closely to the both side surfaces and outer circumferential surface of the oil disk 12, and these inner surfaces of the guide disks 15A, 15B face the both side surfaces and outer circumferential surface of the oil disk 12. An axial gap W1 and a radial gap W2 are formed between the oil disk 12 and the guide casing 15. The axial gap (clearance) W1 is a gap between the side surface of the oil disk 12 and the guide casing 15, and the radial gap (clearance) W2 is a gap between the outer circumferential surface of the oil disk 12 and the guide casing 15.
The gaps W1, W2 are appropriately designed and set on the basis of the viscosity and temperature of the lubricating oil to be used, and pump operating conditions such as the rotational speed of the rotational shaft 1. The lubricating oil scooped up by the oil disk 12 is guided through a lubricating oil passage 17 to the thrust bearing unit 9A.
An inner surface (inner side surface) of the guide casing 15 which faces the side surface of the oil disk 12 is provided with a lubricating oil introducing groove 16. The lubricating oil introducing groove 16 has an upper end portion connected to the lubricating oil passage 17, and is located closely to the side surface of the oil disk 12.
In addition to the gravitational force, surface tension, and frictional forces, centrifugal force generated by the rotation of the oil disk 101 acts on the lubricating oil attached to the surfaces of the oil disk 101. This centrifugal force is proportional to the mass of the lubricating oil and the distance from the center of the oil disk 101 to the lubricating oil, and is also proportional to the square of the angular speed of the oil disk 101.
When the rotational speed of the oil disk 101 is low, the lubricating oil attached to the oil disk 101 does not largely change its position, and is rotated while being held on the oil disk 101. As the rotational speed of the oil disk 101 increases, the centrifugal force acting on the lubricating oil attached to the oil disk 101 becomes greater, so that the lubricating oil is moved outwardly in the radial direction of the oil disk 101. Thus, a relatively large amount of lubricating oil gathers on the outer circumferential edge of the oil disk 101. Therefore, the oil disk 101 which has the radial grooves 14 as shown in
However, as the rotational speed further increases, the centrifugal force becomes dominant over the gravitational force, surface tension, and frictional forces acting on the lubricating oil on the oil disk 101. Therefore, the lubricating oil attached to the surfaces of the oil disk 101 tend to be scattered outwardly in the radial direction of the oil disk 101, irrespective of the surface tension, frictional forces due to viscosity, and the gravitational force. Specifically, when the rotational speed of the oil disk 101 is very high, a sufficient amount of lubricating oil cannot be supplied to the bearing unit 9A, because the lubricating oil cannot be scattered in the axial direction of the rotational shaft 1.
For example, it is assumed that the radius r of the oil disk 101 is 90 mm and the rotational speed of the rotational shaft 1 (i.e., the rotational speed of the oil disk 101 fixed to the rotational shaft 1) is 3600 min−1 as pump operating conditions. In this case, when the pump is in operation, the centrifugal acceleration r ω2 of centrifugal force generated on the oil disk 101 is greater than 1300 times the gravitational acceleration, as indicated by the following equation (1):
Specifically, since centrifugal force with the acceleration greater than 1300 times the gravitational acceleration are generated in the lubricating oil attached to the surfaces of the oil disk 101, this centrifugal force become dominant.
The lubricating oil attached to the surfaces of the oil disk 101 tends to stay on the surfaces of the oil disk 10 by surface tension and frictional forces. However, in the situation where the centrifugal force is dominant as described above, the large centrifugal force that is much greater than the gravitational force, surface tension, and frictional forces causes the lubricating oil on the surfaces of the oil disk 10 to move outwardly in the radial direction of the oil disk 101.
The centrifugal force generated by the rotation of the oil disk 101 acts over the entire circumference of the oil disk 101. Therefore, as shown in
An embodiment of an oil disk 12 capable of solving the above problems is shown in
As shown in
As shown in
The grooves 50 may be replaced with a single groove extending over an entire circumference of the side surface 52 of the oil disk 12. In this case, due to a concern that the lubricating oil may not appropriately be held by the single groove 50, (i.e., a concern about the wetting property of the lubricating oil), the wetting property of the lubricating oil with respect to the groove 50 should preferably be adjusted by suitably selecting a surface roughness of the groove 50 or a material of the oil disk 12.
In the present embodiment, the grooves 50 are formed in one side surface 52 of the oil disk 12. The grooves 50 may be formed in both of the side surface (first side surface) 52 facing the bearing unit 9A and the side surface (second side surface) 52 facing the bearing unit 9B. In this case, the lubricating oil is scooped up by the both side surfaces 52 of the oil disk 12 and supplied to the two bearing units 9A, 9B disposed at both sides of the oil disk 12. Instead of the grooves 50 formed in both side surfaces 52 of the oil disk 12, through-holes, which will be described later, may be forming in the oil disk 12.
When the oil disk 12 having such structures is rotated, the lubricating oil in each groove 50 is forced against the outer-circumferential-side end surface 51 of the groove 50 by action of centrifugal force, as shown in
Further, since the outer-circumferential-side end surface 51 of the groove 50 extends parallel to the axial direction of the rotational shaft 1, the lubricating oil that has been moved outwardly in the radial direction of the oil disk 12 by the centrifugal force changes its direction of movement to an axial direction of the rotational shaft 1 by colliding with the outer-circumferential-side end surface 51 of the groove 50, and then leaves the oil disk 12. As a result, the lubricating oil can be scattered in a direction along which the outer-circumferential-side end surface 51 extends and in a direction in which the groove 50 opens, i.e., in the axial direction of the rotational shaft 1. In this manner, the outer-circumferential-side end surface 51 serves as a guide surface for changing the direction of movement of the lubricating oil in the groove 50 from the radial direction of the oil disk 12 to the axial direction of the rotational shaft 1.
The velocity component of the lubricating oil that is scattered in the axial direction of the rotational shaft 1 is produced by converting of a dynamic pressure in the radial direction which is generated in the lubricating oil by the strong centrifugal force, or a static pressure of the lubricating oil which is increased by the outer-circumferential-side end surface 51, into a dynamic pressure in the axial direction that has been changed from the radial direction by the outer-circumferential-side end surface 51. Therefore, the scattering speed of the lubricating oil on which the strong centrifugal force acts, becomes very high. The direction in which the lubricating oil is scattered is affected by an angle of the outer-circumferential-side end surface 51 of the groove 50 with respect to the axial direction of the rotational shaft 1. In order to supply the lubricating oil most effectively to the bearing unit 9A that is located away from the oil disk 12 in the axial direction of the rotational shaft 1, it is preferred that the outer-circumferential-side end surface 51 extends parallel to the axial direction of the rotational shaft 1 (i.e., perpendicular to the side surface 52 of the oil disk 12). Specifically, it is preferred that the outer-circumferential-side end surface 51 is connected to the side surface 52 of the oil disk 12 at right angle.
With reference to
As shown in
To sum up, even when the strong centrifugal force acts on the lubricating oil attached to the oil disk 12, the outer-circumferential-side end surface 51 prevents the lubricating oil from being scattered outwardly in the radial direction of the oil disk 12. Furthermore, since the outer-circumferential-side end surface 51 of the groove 50 extends parallel to the axial direction of the rotational shaft 1, the lubricating oil that has moved radially on the oil disk 12 by the centrifugal force is forced to change its direction of movement by the outer-circumferential-side end surface 51 and is scattered in the axial direction of the rotational shaft 1.
An amount of lubricating oil held in the groove 50, i.e., an amount of lubricating oil to be scattered from the oil disk 12 in the axial direction of the rotational shaft 1, varies depending on the depth d of the groove 50. Therefore, it is possible to optimize the amount of lubricating oil supplied to the bearing unit 9A by appropriately setting the depth d of the groove 50. As a result, an increase in rolling friction of the bearing due to an excessive supply of lubricating oil to the bearing unit 9A can be prevented. Further, an increase in temperature of the bearing due to increased rolling friction can be prevented.
Experiments were carried out to measure changes in the temperature of the bearing unit 9A when the oil disk 12 according to the above embodiment and the conventional oil disk 101 shown in
As shown in
Further, the flowing manner of the lubricating oil during the operation was observed. As for the conventional oil disk 101, it was observed that the lubricating oil was scattered in the radial direction of the oil disk 101 and was not supplied to the bearing unit 9A. As for the oil disk 12 according to the present embodiment, it was observed that the lubricating oil was scattered in the axial direction of the rotational shaft 1 and was supplied to the bearing unit 9A.
From these experimental results, it can be understood that the conventional oil disk 101 caused inadequate lubrication and resultant heating and inadequate cooling because it failed to appropriately supply the lubricating oil to the bearing unit 9A. In contrast, it can be seen from the experimental results that the oil disk 12 according to the present embodiment assisted appropriate lubrication, heating suppression, and cooling because it was able to appropriately supply the lubricating oil to the bearing unit 9A.
A modified example of the oil disk 12 will be described below with reference to
As shown in
Since the oil disk 12 rotates at a high speed, the amount of lubricating oil held by the outer-circumferential-side end surface 51 of the groove 50 is not uniform along the circumferential direction of the oil disk 12. In the embodiment shown in
As shown in
The outer-circumferential-side surface 71 of the through-hole 70 produces the same advantageous effects as the outer-circumferential-side end surfaces 51 of the grooves 50. Specifically, the outer-circumferential-side surface 71 of the through-hole 70 prevents the lubricating oil, scooped up by the oil disk 12 that rotates at a high speed, from being scattered in the radial direction of the oil disk 12. Further, the lubricating oil is caused by the outer-circumferential-side surface 71 of the through-hole 70 to change its direction of movement to the axial direction of the rotational shaft 1, and thus is scattered from the oil disk 12 in the axial direction of the rotational shaft 1. In this manner, the outer-circumferential-side surface 71 constitutes a guide surface for changing the direction of movement of the lubricating oil from the radial direction of the oil disk 12 to the axial direction of the rotational shaft 1.
As shown in
The outer-circumferential-side end surface 51 of the groove 50 shown in
The outer-circumferential-side end surface 51 of the groove 50 shown in
The cross-sectional shape shown in
The cross-sectional shapes shown in
According to the embodiments described thus far, even under the high-peripheral-speed conditions in which it has been difficult for the conventional oil ring and oil disk to supply the lubricating oil, it is possible to supply the lubricating oil stably to the bearing unit 9A in the bearing apparatus with a simple arrangement wherein the groove 50, the circumferential wall 60, or the through-hole 70 is provided in or on the oil disk 12. Therefore, since the applicable range of the bearing apparatus is widened without using a forced oil supply apparatus, the installation area for pump is reduced and the cost of the pump is lowered, so that it is possible to provide a pump which is highly competitive.
Although the embodiments according to the present invention have been described above, it should be understood that the present invention is not limited to the above embodiments, and various changes and modifications may be made within the technical concept of the appended claims. Needless to say, the present invention is applicable to various types of rotary machines by appropriately designing the shapes and sizes of the outer-circumferential-side end surface 51 of the groove 50, the inner circumferential surface 61 of the circumferential wall 60, or the outer-circumferential-side surface 71 of the through-hole 70 which is provided in or on the oil disk 12, depending on operating conditions, such as the rotational speed of the rotational shaft 1, of the rotary machines, and property values such as the viscosity of the lubricating oil.
The present invention is applicable to a bearing apparatus which is capable of appropriately supplying lubricating oil to a bearing even if a rotational shaft becomes larger in diameter or a rotational speed thereof is higher. The present invention is also applicable to a pump including such a bearing apparatus.
Number | Date | Country | Kind |
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2014-210089 | Oct 2014 | JP | national |
Filing Document | Filing Date | Country | Kind |
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PCT/JP2015/072145 | 8/4/2015 | WO | 00 |