KR102222669B1 - Lubricant spill suppression device, lubricant spill suppression method and rotary machine - Google Patents

Abstract

An object of the present invention is to suppress outflow of lubricating oil from an oil lubricating bearing.
Lubricant leakage suppression used in rotating machines with a main shaft extending in the axial direction and bearings that rotatably support the main shaft, bearings using lubricating oil, and bearing casings in which an oil reservoir for storing lubricating oil is formed. The device is a bearing cover for covering one side of the bearing, and a bearing cover having a through hole for penetrating the main shaft in the axial direction, and between the bearing and the bearing cover, the device is spaced apart from the main shaft and disposed so as to surround the circumference of the main shaft. Equipped with an oil cover. The oil cover has an intersecting surface crossing the axial direction. The crossing surface is disposed adjacent to the bearing so as to isolate the bearing from the lubricating oil stored in the area on the bearing cover side rather than the crossing surface as a part of the oil reservoir, and a part of the lubricating oil is suppressed from being scratched by rotation of the bearing.

Description

Lubricant oil spill control device, lubricant oil spill control method and rotating machine {LUBRICANT SPILL SUPPRESSION DEVICE, LUBRICANT SPILL SUPPRESSION METHOD AND ROTARY MACHINE}

The present invention relates to a technology for suppressing outflow of lubricating oil used for bearings to the outside.

In oil lubricated bearings used in rotating machines, for example, pumps, lubricating oil is scattered by ball bearings, and lubricating oil is adhered to the outer circumference of the main shaft or the inner surface of the bearing cover. When the bearing cover is provided with a through portion through which the main shaft passes, the attached lubricating oil flows out from the gap between the through portion of the bearing cover and the main shaft.

In order to suppress the outflow of such lubricating oil, conventionally, a lip seal has been provided between the main shaft and the penetrating portion of the bearing cover. In the method of using a lip seal, since the main shaft slides while the lip seal and the main shaft are in contact with each other during rotation of the main shaft, fine foreign matter between the lip seal and the main shaft (for example, iron powder caused by rust or abrasion). When this enters, the sliding part of the main shaft is worn. When the degree of wear increases, the sealing performance decreases, and the lubricating oil leaks to the outside, and as a result, replacement of the main shaft is required.

Japanese Patent Application Publication No. Hei 9-196186

Instead of such a lip seal, it is also possible to suppress the outflow of lubricating oil by using a labyrinth seal (for example, Patent Document 1 described above). For example, a groove called labyrinth is formed in the through portion of the bearing cover, that is, on the surface of the bearing cover facing the outer surface of the main shaft. According to this groove structure, the lubricating oil that has entered the gap between the main shaft and the bearing cover remains in the groove by the surface tension of the lubricating oil, and is guided downward along the groove. This groove is formed over approximately the entire circumference of the penetrating portion, and only the predetermined width of the lowermost portion is a notch in which the bearing surface of the bearing cover is cut to a depth equal to or deeper than the groove, instead of the groove. By providing the lubricating oil guided downward along the groove, it is possible to guide the lubricating oil from the notch to the oil reservoir. According to such a labyrinth seal, since oil sealing is performed in a state in which the bearing cover and the main shaft are not in contact, the same problem as the above-described lip seal does not occur.

However, in the labyrinth seal described above, since the groove is not formed in the notch at the lowermost part, the lubricating oil scattered on the notch is likely to flow out to the atmosphere. Further, the depth of the grooves, the number of grooves, etc. are finite due to space constraints and the like, and when the amount of lubricating oil scatters is large, there is a fear that only the grooves cannot sufficiently suppress the outflow of the lubricant to the outside. This problem is not limited to pumps, but is common to various rotating machines employing oil lubricated bearings. From this, there is a need for a technique capable of appropriately suppressing the outflow of lubricating oil from the oil lubricating bearing to the outside.

The present invention has been made in order to solve at least a part of the problems described above, and can be realized, for example, in the following form.

A first aspect of the present invention is provided as a lubricating oil leakage suppression device for a rotating machine including a main shaft extending in the axial direction and a bearing rotatably supporting the main shaft, and a bearing using lubricating oil. This lubricating oil leakage suppression device is a bearing cover for covering one side of the bearing, and a bearing cover having a through hole for penetrating the main shaft in the axial direction, and between the bearing and the bearing cover, spaced apart from the main shaft, and the periphery of the main shaft. It is provided with an oil cover disposed so as to surround the.

According to such a lubricating oil outflow suppression device, when lubricating oil scatters from the bearing toward the bearing cover side, the scattering of the lubricating oil can be blocked by the oil cover. Accordingly, it is possible to suppress the lubricating oil from entering the through hole of the bearing cover and flowing out to the outside.

As a second aspect of the present invention, in the first aspect, the oil cover is a bottom surface orthogonal to the axis line, a bottom surface in which a first through hole through which the main axis passes is formed, and a bearing It may be provided with an outer side surface formed over the entire circumferential direction to the vicinity of the bearing toward the side. According to this aspect, most of the lubricating oil scattered toward the outer side in the radial direction of the oil cover is trapped by the outer side surface and is stored inside the oil cover. Accordingly, it is possible to suppress the lubricating oil from scattering outward in the radial direction of the oil cover and entering the bearing cover side from the outer side in the radial direction of the oil cover. As a result, penetration of the lubricating oil into the through hole of the bearing cover can be further suppressed.

As a third aspect of the present invention, in the second aspect, the oil cover may have an inner side surface formed by extending from the radially inner end of the bottom surface toward the bearing side over the entire circumferential direction. According to this form, since the lubricating oil scattered on the inside of the oil cover is guided downward along the inner surface of the inner side, the lubricating oil enters the gap between the main shaft and the oil cover, or the gap between the oil break ring and the oil cover. You can restrain yourself from doing it. Therefore, it is possible to suppress the lubricating oil from moving to the bearing cover side of the oil cover. As a result, penetration of the lubricating oil into the through hole of the bearing cover can be further suppressed.

As a fourth aspect of the present invention, in any one of the first to third aspects, the oil cover may be fitted in a step portion formed inside the bearing cover. According to this aspect, it is possible to easily mount the oil cover.

As a fifth aspect of the present invention, in any one of the first to fourth aspects, the lubricating oil leakage suppression device is an oil disconnection ring installed along the circumferential direction on the outer circumference of the main shaft, and is installed between the bearing and the bearing cover. An oil break ring may be provided. The oil cover may be disposed at a position spaced apart from the oil cut-off ring and surrounds the oil cut-off ring. In this form, when lubricating oil enters the bearing cover side from the gap between the oil cover and the oil disconnection ring, the lubricating oil is released from the main shaft by the centrifugal force accompanying the rotation of the main shaft and the oil disconnection ring. It is blown in a direction that is spaced apart. According to this form, a configuration that does not have an oil break ring, that is, from the gap between the oil cover and the main shaft, the lubricant oil enters the bearing cover side, and the lubricant is blown away from the main shaft by centrifugal force. Compared to the configuration, the lubricating oil is blown from a position more spaced apart from the main shaft in a direction spaced apart from the main shaft. Therefore, it is possible to further suppress the intrusion of lubricating oil into the through hole of the bearing cover.

As a sixth aspect of the present invention, in the fifth aspect, the oil cut-off ring has a first portion and a second portion that is formed larger in diameter than the first portion and is located on the bearing cover side than the first portion. You can do it. The end of the oil cover on the axial side may be disposed on the bearing cover side rather than the end on the bearing side of the second portion. According to this aspect, the lubricating oil scattered on the first portion is more difficult to penetrate into the bearing cover side than in the oil cover. Therefore, it is possible to further suppress the intrusion of lubricating oil into the through hole of the bearing cover.

As a seventh aspect of the present invention, in the fifth or sixth aspect, in a portion on the inner surface of the bearing cover facing the bearing, oil surrounding the outer side of the through hole at least at a position above the center of the through hole. A relief groove may be formed. According to this aspect, even when the lubricant enters the bearing cover side rather than the oil cover, the lubricant that scatters from the oil break ring to an area outside the oil relief groove of the inner surface of the bearing cover is guided to the oil relief groove through the inner surface. do. Since the lubricating oil guided to the oil relief groove moves downward than the through hole along the oil relief groove by gravity, it is possible to suppress the lubricating oil from entering the through hole of the bearing cover.

As an eighth aspect of the present invention, in the seventh aspect, the end surface outside the circumferential direction in a direction orthogonal to the axis of the oil break ring and the top portion on the inner peripheral side of the oil relief groove are the same in the radial direction. You may be in a position. According to this aspect, even if the lubricating oil penetrates the bearing cover side from the gap between the oil cover and the oil bleeding ring, almost all of the lubricating oil is scattered in a region outside the oil relief groove. Therefore, the effect of the fifth aspect can be maximized.

As a ninth aspect of the present invention, in any of the fifth to eighth aspects including at least the fourth aspect, or the fourth aspect, the outer side is penetrated in the thickness direction of the side surface to the lower end of the bearing-side end portion. The cutout to be formed may be formed. According to this aspect, since the lubricating oil scattered on the bearing side of the bottom surface of the oil cover can be guided below the oil cover through the cutout portion, the lubricating oil does not stay on the bearing side of the oil cover.

As a tenth aspect of the present invention, in the ninth aspect, the outer side surface may include a bent portion formed to extend from the base end portion of the cutout portion to a side spaced apart from the axis line. According to this aspect, by inserting a bent portion into a groove formed in the bearing cover for guiding the lubricating oil downward, the oil cover can be mounted on the bearing cover. That is, it is possible to easily position the oil cover.

As an eleventh aspect of the present invention, in the ninth or tenth aspect, a second through hole may be formed in the lower end portion of the bottom surface in the thickness direction of the bottom surface. The lowermost end of the second through hole may be disposed so as to be located below the liquid level of the lubricating oil. According to this aspect, the lubricating oil that enters the bearing cover side more than the oil cover and remains below the oil cover is more likely to move to the bearing side than the oil cover, and the liquid level of the lubricating oil on the bearing cover side than the oil cover is higher than the oil cover. It is possible to prevent it from becoming higher than the liquid level of the lubricating oil. As a result, it is possible to prevent the lubricating oil from contacting the outer circumference of the oil break ring and the lubricating oil due to the bending of the lubricating oil liquid surface due to the rotation of the bearing, and the scattering of the oil is promoted. Accordingly, it is possible to suppress the oil that has penetrated into the bearing cover side rather than the oil cover from staying on the side and the lubricating oil from entering the through hole of the bearing cover.

As a twelfth aspect of the present invention, in any one of the ninth to eleventh aspects, the oil cover may have a vertically symmetrical shape. According to this aspect, the oil cover is not mounted in a state in which the upper and lower positions are wrong. In other words, the operator does not need to distinguish and recognize the upper and lower positions of the oil cover, thereby facilitating the installation of the oil cover.

As a thirteenth aspect of the present invention, in any one of the ninth to twelfth aspects, on the bearing side surface of the oil cover, the outer side of the first through hole is at least at a position above the center of the first through hole. An enclosing oil relief groove may be formed. According to this aspect, the lubricating oil scattered on the oil cover can be guided to the oil relief groove, and can be moved by gravity below the through hole of the bearing cover along the oil relief groove. Therefore, it is possible to suppress the lubricating oil from entering the through hole of the bearing cover.

A fourteenth aspect of the present invention is provided as a rotary machine including a main shaft, a bearing, and a lubricant oil outflow suppression device of any one of the first to thirteenth aspects. According to such a rotating machine, the same effects as those of the first to thirteenth aspects are exhibited.

A fifteenth aspect of the present invention is a main shaft extending in the axial direction and a bearing rotatably supporting the main shaft, and is provided as a method of suppressing outflow of lubricating oil in a rotating machine including a bearing using lubricating oil. In this method, a bearing cover for covering one side of the bearing and the bearing, and a bearing cover having a through hole for penetrating the main shaft in the axial direction, is spaced apart from the main shaft, and is disposed so as to surround the circumference of the main shaft. The oil cover is provided and at least a part of the scattering of the lubricating oil from the bearing toward the bearing cover is blocked by the oil cover, so that the lubricating oil is prevented from flowing out from the through hole. According to this method, the same effect as that of the first aspect is exhibited.

A sixteenth aspect of the present invention includes a main shaft extending in the axial direction, a bearing rotatably supporting the main shaft, a bearing using lubricating oil, and a bearing casing in which an oil reservoir for storing lubricating oil is formed. It is provided as a lubricant oil spill suppression device used in rotating machinery. This lubricating oil leakage suppression device is a bearing cover for covering one side of the bearing, a bearing cover having a through hole for penetrating the main shaft in the axial direction, and an oil cover disposed to be spaced apart from the main shaft between the bearing and the bearing cover. It is equipped with. The oil cover has an intersecting surface crossing the axial direction. The crossing surface is disposed adjacent to the bearing so as to isolate the bearing from the lubricating oil stored in the area on the bearing cover side rather than the crossing surface as a part of the oil reservoir, and a part of the lubricating oil is suppressed from being scratched by rotation of the bearing.

According to such a lubricating oil outflow suppression device, since the cross surface of the oil cover is disposed adjacent to the bearing, almost no oil reservoir is formed between the cross surface and the bearing. For this reason, it is suppressed that the lubricating oil is scraped up by the rotation of the bearing. That is, since the scattering of lubricating oil can be suppressed as a scattering source, it is possible to extremely effectively suppress the lubricating oil from scattering on the bearing cover side, and the lubricating oil from flowing out from the gap between the through hole of the bearing cover and the main shaft.

According to the seventeenth aspect of the present invention, in the sixteenth aspect, the crossing surface of the oil cover is disposed so as to surround the periphery of the main shaft. The oil cover has a substantially cylindrical shape extending in the axial direction. According to this aspect, since the cross surface of the oil cover is arranged so as to surround the circumference of the main shaft, it is possible to effectively block the lubricating oil scattering from the bearing to the bearing cover side at all positions in the circumferential direction by the cross surface. Therefore, it is possible to increase the effect of suppressing the outflow of lubricating oil. In addition, since the oil cover has a substantially cylindrical shape, it is easy to fit into the bearing cover and install it. In addition, since the inner surface of the cylindrical shape extends in the axial direction, a small gap between the main shaft and the oil cover (in the case where an oil break ring to be described later is installed, between the oil break ring and the oil cover) is formed across the entire circumferential direction. It is possible to configure the lubricant leakage suppression device so as to extend in the direction. As a result, even if oil enters the gap, it becomes more difficult to move to the bearing cover side, so that the effect of suppressing the outflow of lubricating oil can be further enhanced.

According to the eighteenth aspect of the present invention, in the sixteenth aspect, the crossing surface of the oil cover is disposed so as to surround the circumference of the main shaft. The oil cover has an inner wall extending from the radially inner end of the crossing surface toward the bearing cover side over the entire circumferential direction, and from the radially outer end of the crossing surface toward the bearing cover side over the entire circumferential direction. It has an extending outer wall. According to this aspect, the same effect as that of the seventeenth aspect is exhibited.

According to a nineteenth aspect of the present invention, in any one of the sixteenth to eighteenth aspects, the oil cover is fitted into a step portion formed inside the bearing cover. According to this aspect, it is possible to easily mount the oil cover.

According to a twentieth aspect of the present invention, in any one of the sixteenth to nineteenth aspects, the lubricating oil outflow suppression device includes an oil disconnection ring installed along the circumferential direction on the outer periphery of the main shaft between the bearing and the bearing cover Equipped. The oil cover is spaced apart from the oil break ring and is disposed in a position surrounding the oil break ring. The oil break ring is disposed so as to protrude from the oil cover toward the bearing cover side. In this form, when lubricant enters the bearing cover side on the oil break ring from the gap between the oil cover and the oil break ring, the lubricant is a portion of the oil break ring that protrudes from the oil cover toward the bearing cover side. In this case, it is blown in a direction away from the main shaft by the centrifugal force accompanying the rotation of the main shaft and the oil break ring. According to this form, a configuration that does not have an oil break ring, that is, from the gap between the oil cover and the main shaft, the lubricant oil enters the bearing cover side, and the lubricant is blown away from the main shaft by centrifugal force. Compared to the configuration, the lubricating oil is blown from a position more spaced apart from the main shaft in a direction spaced apart from the main shaft. Therefore, it is possible to further suppress the intrusion of lubricating oil into the through hole of the bearing cover.

According to a twenty-first aspect of the present invention, in a twenty-first aspect, a plurality of radially extending grooves are radially formed on the end surface of the oil cut-off ring on the bearing cover side. According to this aspect, the plurality of grooves function similarly to the impeller of the pump, and an airflow directed outward in the radial direction is created in the space between the bearing cover and the oil cut-off ring. Therefore, even when the lubricating oil moves on the oil break ring toward the bearing cover side through the gap between the oil cover and the oil break ring, the lubricating oil at the end of the oil break ring on the bearing cover side is radially outward due to airflow. It becomes easy to be blown by. That is, the movement of the lubricating oil toward the main shaft from the gap between the bearing cover and the oil break ring is suppressed. As a result, penetration of the lubricating oil into the through hole of the bearing cover can be further suppressed.

According to a 22nd aspect of the present invention, in the 20th aspect, a plurality of grooves are formed in a blade shape on the end surface of the oil cut-off ring on the bearing cover side. According to this aspect, the same effect as that of the 21st aspect is exhibited.

According to a twenty-third aspect of the present invention, in any one of the sixteenth to twenty-second aspects, at a position on the inner surface of the bearing cover facing the bearing, at a position above the center of the through hole of the bearing cover. An oil relief groove is formed surrounding the outside of the through hole. According to this aspect, even when the lubricating oil penetrates the bearing cover side rather than the oil cover, the lubricating oil scattered from the oil break ring to an area outside the oil relief groove among the inner surfaces of the bearing cover travels through the outer area to the oil relief groove. Is guided by. The lubricating oil guided to the oil relief groove is moved by gravity along the oil relief groove, i.e., avoiding the through hole, and moves downward than the through hole, so that the lubricating oil can be suppressed from entering the through hole of the bearing cover.

According to a twenty-fourth aspect of the present invention, there is provided a rotary machine including the lubricant oil leakage suppression device of any one of the sixteenth to twenty-third, a main shaft, a bearing, and a bearing casing. According to such a rotating machine, the same effects as those of the 16th to 23rd aspects are exhibited.

According to a twenty-fifth aspect of the present invention, a main shaft extending in the axial direction, a bearing rotatably supporting the main shaft, a bearing using lubricating oil, and a bearing casing having an oil reservoir for storing lubricating oil are formed therein. In one rotating machine, a method of suppressing the outflow of lubricating oil is provided. In this method, an oil cover having an intersecting surface crossing the axial direction is provided between the bearing and the bearing cover, which is a bearing cover for covering one side of the bearing, and has a through hole for penetrating the main shaft in the axial direction. Arranged adjacent to the bearing to isolate the bearing from the lubricant that is stored in the area on the bearing cover side than the crossing surface as a part of the oil reservoir and the crossing surface is separated from the crossing surface, and a part of the lubricant is prevented from being scratched by rotation of the bearing. Thereby, it is suppressed that the lubricating oil flows out from the through hole to the outside. According to this method, the same effect as in the sixteenth aspect is achieved.

The present invention is not limited to the above-described form, but can also be realized as a bearing cover, an oil break ring, or the like.

1 is a cross-sectional view showing a schematic configuration of a pump as a first embodiment of the present invention.
2 is a cross-sectional view showing a schematic configuration of a lubricating oil outflow suppression device.
3 is an explanatory diagram showing a schematic configuration of a bearing cover.
4 is an explanatory diagram showing a schematic configuration of an oil cut-off ring.
5 is an explanatory diagram showing a schematic configuration of an oil cover.
6 is a cross-sectional view showing a schematic configuration of a device for suppressing lubricating oil leakage as a second embodiment.
7 is an explanatory diagram showing a configuration of an oil cover as a modified example.
8 is a cross-sectional view showing a schematic configuration of a device for suppressing lubricating oil leakage as a third embodiment.
Fig. 9 is a view of the oil cover as seen from the bearing cover side.
Fig. 10 is a view of the oil break ring as seen from the bearing cover side.
11 is a cross-sectional view showing a schematic configuration of a device for suppressing lubricating oil leakage as a fourth embodiment.
12 is an explanatory diagram showing a schematic configuration of an oil cover as a fourth embodiment.

A. First embodiment:

1 is a cross-sectional view showing a schematic configuration of a pump 20 as an embodiment of the present invention. As shown, the pump 20 as an example of a rotating machine includes a main shaft 30, a bearing casing 40, bearings 51 and 52, and a lubricant oil leakage suppression device 90. In the inside of the bearing casing 40, the main shaft 30 is formed to extend along the axis line AL direction orthogonal to the vertical (gravity) direction, and at one end side thereof, the impeller around the main shaft 30 (35) is fixed. On the other end side of the main shaft 30, the main shaft 30 is supported by the bearings 51 and 52 cantilevered. An electric motor (not shown) is connected in front of the bearing 52 on the other end side of the main shaft 30. With this configuration, the main shaft 30 and the impeller 35 rotate with the axis AL as a rotational center axis.

The bearings 51 and 52 are ball bearings using lubricating oil. An oil reservoir 41 is formed between the bearing 51 and the bearing 52 by a bearing casing 40. In this embodiment, the oil level OL in the oil reservoir 41 is maintained near the center of the ball when the ball constituting the bearings 51 and 52 is positioned at the lowest position.

The bearing casing 40 is terminated at the position of the bearing 52 on the other end side of the main shaft 30, whereby the outer side of the bearing 52 (the side opposite to the bearing 51), It is exposed from the bearing casing 40. One side of the bearing 52, that is, an exposed portion, is covered by the bearing cover 60. In this embodiment, the bearing cover 60 has a cylindrical cup shape with a bottom. The end of the bearing cover 60 on the opposite side to the bottom portion is formed in a flange shape, whereby the bearing cover 60 is attached to the bearing casing 40. A through hole 61 penetrating in the direction of the axis AL is formed in the bottom of the bearing cover 60. The main shaft 30 penetrates through the through hole 61 and extends to the outside of the bearing cover 60.

Between the bearing 52 and the bearing cover 60, an oil cover 80 and an oil break ring 70 are disposed. The bearing cover 60, the oil cover 80, and the oil break ring 70 are lubricating oil that prevents the lubricating oil scattering from the bearing 52 from spilling out to the outside (the side of the motor) when the main shaft 30 rotates. It functions as an outflow suppression device 90.

FIG. 2 is a partially enlarged view of FIG. 1 showing a schematic configuration of the periphery of the bearing 52 and the lubricating oil leakage suppression device 90. 3 shows a schematic configuration of the bearing cover 60. Fig. 3(a) is a cross-sectional view of the bearing cover 60 in the same cross-section as in Fig. 2, and Fig. 3(b) is an arrow diagram of the inner surface of the bearing cover 60 (surface on the bearing 52 side). . 4 shows a schematic configuration of the oil break ring 70. 4(a) is a cross-sectional view of the oil break ring 70 in the same cross-section as in FIG. 2, and FIG. 4(b) is an arrow as seen from the side on which the oil break ring 70 is mounted. It is a degree. 5 shows a schematic configuration of the oil cover 80.

As shown in Figs. 2 and 3, an oil relief groove 62 is formed in a portion on the inner surface of the bearing cover 60 that faces the bearing 52. As shown in FIG. The said site|part is formed as a surface orthogonal to the axis line AL in this embodiment. The oil relief groove 62 surrounds the outside of the through hole 61 and is formed in an annular shape. The oil relief groove 62 includes a top portion 62a that is an end point on the outer circumference side of the groove, a top portion 62b that is an end point on the inner circumference side of the groove, and a bottom portion 62c that is the deepest portion of the groove. I have.

The end of the outer circumferential side of the surface of the oil relief groove 62 (the surface forming the groove), that is, the periphery of the top part 62a, is the side of the bearing 52 which crosses at an angle θ with respect to the axis AL. It has a slope facing toward. In this embodiment, the surface between the top portion 62a and the bottom portion 62c of the oil relief groove 62 is not limited to the end portion on the outer circumference side, and extends from the top portion 62a to the bottom portion 62c. It is formed so as to intersect the axis AL at an angle θ with respect to AL), in other words, as it goes from the top 62a to the bottom 62c, so as to be close to the axis AL (away from the bearing 52). have. In this embodiment, the angle θ from the top portion 62a to the bottom portion 62c is a constant value. According to the shape of the oil relief groove 62, in a position above the center of the through hole 61 (the position where the axis AL passes) (above the vertical direction), on the inner surface of the bearing cover 60 It is easier to guide the lubricating oil scattered on the outer surface 63 outside the groove 62 to the oil relief groove 62, more specifically, to the bottom portion 62c. Further, at a position below the center of the through hole 61, it is easy to guide the lubricating oil in the oil relief groove 62 to the outside of the oil relief groove 62, that is, downward than the through hole 61.

In order to guide the lubricating oil over a wide range while securing the inclination angle of the surface of the oil relief groove 62 that can appropriately guide the lubricating oil, the angle θ is preferably 30° or more and 75° or less. In this embodiment, the angle θ is 45°. In addition, the angle θ may change depending on the position.

The end portion on the inner circumferential side of the surface of the oil relief groove 62, that is, the periphery of the top portion 62b is formed parallel to the axis AL. In this embodiment, the surface between the top portion 62b and the bottom portion 62c of the oil relief groove 62 is not limited to the end portion on the inner circumferential side, and the axis line AL from the top portion 62b to the bottom portion 62c is It is formed parallel to ). According to the shape of the oil relief groove 62, it is difficult for the lubricating oil guided to the oil relief groove 62 to penetrate into the inner surface 64 inside the oil relief groove 62. However, the end portion on the inner circumferential side of the surface of the oil relief groove 62 may be formed as an inclined surface facing the side opposite to the bearing 52, which crosses obliquely with respect to the axis AL. That is, the end portion on the inner circumferential side of the surface of the oil relief groove 62 may be formed so as to be close to the axis AL as it goes from the top portion 62b to the bottom portion 62c. In addition, the surface between the top portion 62b and the bottom portion 62c is an inclined surface facing the side opposite to the bearing 52, which crosses obliquely with respect to the axis AL from the top portion 62b to the bottom portion 62c. It may be formed. Even with these configurations, the same effect as the configuration parallel to the axis line AL described above is exhibited.

According to the above-described oil relief groove 62, when the lubricating oil scattered on the outer surface 63 outside the oil relief groove 62 moves downward by gravity on the outer surface 63, the lubricating oil is I can capture it. The lubricating oil trapped in the oil relief groove 62 moves below the through hole 61 along the annular oil relief groove 62 by gravity, and returns to the oil reservoir 41. Therefore, the lubricating oil scattered on the outer surface 63 penetrates the through hole 61 of the bearing cover 60, and the gap between the main shaft 30 and the surface forming the through hole 61 of the bearing cover 60 It can be prevented from leaking to the outside through.

2 and 3, at least one (here two) grooves 65 are formed along the circumferential direction on the surface of the bearing cover 60 on which the through hole 61 is formed. have. This groove 65 constitutes a labyrinth seal. Further, below the surface of the bearing cover 60 on which the through hole 61 is formed, a notch 66 in which the bearing 52 side is cut is formed. The groove 65 is formed in an annular shape except for the region in which the cutout 66 is formed, and communicates with the cutout 66 at its lower end. According to this configuration, even if a small amount of lubricating oil has penetrated into the through hole 61 even by the lubricating oil outflow suppression device 90, the lubricating oil is captured by the cutout 66 and through the cutout 66 It returns to the oil reservoir 41.

As shown in FIG. 2, the oil cut-off ring 70 is provided between the bearing 52 and the bearing cover 60 on the outer periphery of the main shaft 30 along the circumferential direction. A through hole 74 having a diameter approximately equal to the diameter of the main shaft 30 is formed in the central portion of the oil break ring 70 (see Fig. 4). The oil cut-off ring 70 is fixed to the main shaft 30 by screwing after passing the main shaft 30 through the through hole 74 in the present embodiment. For this reason, when the main shaft 30 rotates, the oil cut-off ring 70 rotates together with the main shaft 30.

As shown in Figs. 2 and 4, the oil break ring 70 is located on the bearing cover 60 side rather than the first part 71 extending along the axis AL direction, and the first part 71. It has a second part 72 located. The second portion 72 has a larger diameter than the first portion 71. As shown in Fig. 2, the oil cut-off ring 70 leaves a slight gap between the inner surface 64 of the bearing cover 60, and approximately the entire area between the bearing cover 60 and the bearing 52. It is formed by extending. The end of the first portion 71 on the bearing 52 side in the axial line AL direction is in contact with the outer ring of the bearing 52. According to this configuration, the lubricating oil scattered from the bearing 52 toward the main shaft 30 is blocked by the first part 71 and blown outward in the radial direction by the centrifugal force of the rotating first part 71. Lose. For this reason, the lubricating oil adheres to the main shaft 30, and the lubricating oil moves along the main shaft 30 in a direction toward the bearing cover 60, and does not leak out.

The height of the oil break ring 70 in the radial direction is in a range in which the end surface 72a outside the circumferential direction of the second portion 72 does not contact the oil level OL, as shown in FIG. 2. . In this way, when the oil cut-off ring 70 rotates together with the main shaft 30, the second portion 72 contacts the oil level OL, and the lubricant does not scatter.

According to the above-described oil cut-off ring 70, the lubricating oil scattered toward the inner surface 64 in a range corresponding to the outer diameter of the oil cut-off ring 70 (the second part 72) is the oil cut-off ring. Since it is blocked by 70, it is possible to prevent the scattered lubricating oil from landing on the inner side 64. Therefore, the lubricating oil hits the inner surface 64, the lubricating oil penetrates the through hole 61 of the bearing cover 60, and forms the main shaft 30 and the through hole 61 of the bearing cover 60. It is possible to suppress leakage to the outside through the gap of the surface.

In addition, in this embodiment, as shown in FIG. 2, the end surface 72a on the outer circumferential direction of the oil cut-off ring 70, and the top part 62b on the inner circumferential side of the oil relief groove 62 have a radius They are in the same position in the direction. That is, in the surface direction orthogonal to the axis AL, the entire area of the inner surface 64 inside the groove 62 is prevented from scattering of the lubricating oil by the oil cut-off ring 70. This prevents the lubricating oil scattered on the outer surface 63 outside the oil relief groove 62 from entering the through hole 61 by the groove 62, and suppresses the outflow of the lubricating oil to the outside. Make it remarkably large. In addition, compared to the case where the top part 62b is on the axis AL side than the end surface 72a, the through hole 61 is difficult to enter the lubricating oil into the gap between the bearing cover 60 and the oil break ring 70. The intrusion of the lubricant oil into it is suppressed. However, the configuration in which the top portion 62b is located on the axis line AL side than the end surface 72a is not excluded. Similarly, the configuration in which the end surface 72a is on the axis line AL side than the top portion 62b is not excluded.

As shown in Figs. 2 and 4, on the surface of the second part 72 of the oil break ring 70 on the side of the bearing cover 60 (the surface facing the inner surface 64), the axis AL A groove 73 extending toward the outer diameter side of the oil break ring 70 is formed from the side of. In this embodiment, the groove 73 extends in the radial direction. A plurality of grooves 73 are formed along the circumferential direction. 4B shows an example in which six grooves 73 are formed at equiangular intervals in the circumferential direction. Since the groove 73 is formed, when the oil cut-off ring 70 rotates together with the main shaft 30, the shape of the groove 73 functions as the impeller of the pump, so the inner surface 64 Even if the lubricating oil enters between the oil breaker ring 70 and the lubricating oil, the lubricating oil is easily discharged in a direction away from the main shaft 30 (through hole 61) by centrifugal force. As a result, it is possible to further suppress the lubricating oil from flowing out from the through hole 61 to the outside.

In addition, as shown in FIG. 4, the groove 73 formed in the oil cut-off ring 70 is open on the outer circumferential side and closed on the inner circumferential side. That is, the groove end 73a, which is the end of the outer circumferential side of the groove 73, is formed to extend to the outer periphery of the surface of the bearing cover 60 side of the oil break ring 70, and is formed on the inner circumferential side of the groove 73. The groove end portion 73b, which is an end portion of, is terminated before reaching the through hole 74. According to this configuration, it is possible to further suppress the intrusion of the lubricating oil into the through hole 74 side, that is, the main shaft 30 side. In this embodiment, the groove end portion 73b has a semicircular shape.

As shown in FIG. 2, the oil cover 80 is disposed between the bearing 52 and the bearing cover 60 so as to surround the main shaft 30 by being spaced apart from the main shaft 30. In this embodiment, since the oil cut-off ring 70 is mounted around the main shaft 30, the oil cover 80 is spaced apart from the oil cut-off ring 70, so that the circumference of the oil cut-off ring 70 is It is arranged so as to surround it. The gap D1 between the oil cover 80 and the oil break ring 70 is preferably made as small as possible within a range in which both are not in contact. The oil cover 80 is fitted in a step 67 formed inside the bearing cover 60 in this embodiment. The stepped portion 67 is formed outside the outer surface 63 in the radial direction. With this configuration, it is easy to mount the oil cover 80. However, as a mounting method of the oil cover 80, an arbitrary method can be adopted. For example, the oil cover 80 may be fitted in the outer edge portion of the bearing 52 and may be attached. According to the oil cover 80, it is possible to block the lubricating oil that scatters radially outward from the oil cover 80 toward the bearing cover 60 than the oil break ring 70.

2 and 5, the oil cover 80 is provided with a bottom surface 81 and an outer side surface 82. The bottom surface 81 is a surface orthogonal to the axis line AL, and has a substantially circular shape. In the interior of the bottom surface 81, a first through hole 89 through which the main shaft 30 and the oil cut-off ring 70 pass is formed. The outer side surface 82 is formed extending from the radially outer end of the bottom surface 81 to the vicinity of the bearing 52. This outer side surface 82 is formed over the entire circumferential direction. Most of the lubricating oil scattered toward the outer side in the radial direction of the oil cover 80 is trapped by the outer side surface 82 and is stored inside the oil cover 80. For this reason, the risk that the lubricating oil scatters outward in the radial direction of the oil cover 80 and penetrates into the bearing cover 60 side from the outer side in the radial direction of the oil cover 80 can be reduced.

As shown in FIG. 5, in the lower end of the end of the outer side surface 82 on the bearing 52 side, cutouts 87 are formed respectively penetrating in the thickness direction of the outer side surface 82. As shown in FIG. Lubricating oil on the bearing 52 side rather than the oil cover 80, for example, the lubricating oil scattered from the bearing 52 toward the oil cover 80, and guided downward through the oil cover 80, is 87). Accordingly, it is possible to suppress the lubricating oil from staying inside the oil cover 80 and a local increase in the oil level inside the oil cover 80. As a result, the risk of lubricating oil entering the bearing cover 60 side rather than the oil cover 80 can be reduced.

At the base end of the cutout 87 of the outer side 82, a bent portion 85 is formed extending toward a side spaced apart from the axis AL. By inserting the bent portion 85 into the groove 68 (see FIG. 3) of the bearing cover 60, the oil cover 80 can be mounted on the bearing cover 60. The groove 68 is formed in order to further guide the lubricating oil guided downward by the oil relief groove 62 downward. According to the bent portion 85, the position of the oil cover 80 can be easily performed.

In the lower end of the bottom surface 81, a second through hole 83 penetrating in the thickness direction of the bottom surface 81 is formed. The lowermost end portion 83a of the second through hole 83 is provided at a position below the oil level OL in the oil storage portion 41. Such a second through hole 83 can suppress the lubricating oil that has penetrated into the bearing cover 60 side than the oil cover 80 from staying below. Specifically, the lubricating oil remaining below the space between the oil cover 80 and the bearing cover 60 is connected to the bearing 52 side of the oil cover 80 through the second through hole 83. Therefore, the liquid level of the retained lubricating oil can be reduced compared to the case where the second through hole 83 is not present. Therefore, the risk of invading the lubricating oil into the through hole 61 can be reduced. It is preferable that the uppermost end portion 83b of the second through hole 83 is disposed at a position equal to or lower than the oil level OL of the lubricating oil.

Such an oil cover 80 is formed in a vertically symmetrical shape. That is, in the oil cover 80, the notch 87, the bent part 85, and the second through hole 83 are vertically symmetrical, respectively, the notched part 88, the bent part 86, and A second through hole 84 is formed. According to this configuration, when the oil cover 80 is mounted, the worker does not need to recognize and recognize the upper and lower positions of the oil cover 80, so that the installation work of the oil cover 80 is facilitated.

The second through hole 84 exerts a further effect. That is, since the opening area of the oil cover 80 (bottom 81) is increased by the second through hole 84, the heat in the inner space of the oil cover 80 is suitably radiated, and the bearing 52 It is possible to suppress the lubricating oil inside from becoming excessively high temperature. In the case where the surface of the bearing 52 on the bearing 51 side is covered to prevent the lubricating oil from scattering on the bearing 52 side, since heat is easily accumulated inside the bearing 52, such a configuration is particularly effective. . An arbitrary number of through holes in the bottom surface 81 may be formed at an arbitrary location in accordance with a desired heat dissipation characteristic.

In this embodiment, as shown in FIG. 2, the oil cover 80 has an end portion of the oil cover 80 on the axis AL side of the second portion 72 of the oil break ring 70. It is arranged so as to be positioned on the bearing cover 60 side rather than the end portion on the bearing 52 side. In other words, the bottom surface 81 is located on the bearing cover 60 side rather than the end of the second portion 72 of the oil break ring 70 on the bearing 52 side in the direction of the axis line AL. According to this configuration, the lubricating oil scattered on the first portion 71 is more difficult to penetrate into the bearing cover 60 side than the oil cover 80. Specifically, the position of the gap between the bottom surface 81 and the oil break ring 70 (the second part 72) is from the end of the second part 72 on the bearing 52 side to the bearing cover 60 side. Since it is offset by the distance D2, the lubricating oil adhering to the first part 71 or the lubricating oil adhering to the end surface of the bearing 52 side of the second part 72 is away from the axis AL by centrifugal force. Even if it is blown away, this lubricating oil is more difficult to penetrate into the bearing cover 60 side than the oil cover 80.

According to the above-described lubricating oil outflow suppression device 90, the lubricating oil scattering from the bearing 52 toward the bearing cover 60 side is blocked by the oil cover 80 and the oil break ring 70. For this reason, most of the scattered lubricating oil returns to the oil reservoir 41 without entering the bearing cover 60 side rather than the outer surface 63. Some of the scattered lubricating oil may pass through the gap between the oil cover 80 and the oil break ring 70 and invade the bearing cover 60 side rather than the oil cover 80. However, in this case, the lubricating oil riding on the second part 72 and entering the bearing cover 60 side from the gap is separated from the axis AL by the centrifugal force, that is, the oil relief groove 62 ) Is blown outward. As a result, the lubricating oil is trapped in the oil relief groove 62 and returns to the oil reservoir 41. In addition, even if a very small amount of lubricating oil penetrates the through hole 61 without being trapped in the oil relief groove 62, the lubricating oil is trapped in the groove 65 as a labyrinth seal, and the oil reservoir 41 ). Therefore, it is possible to suppress the outflow of the lubricating oil to the outside with high reliability.

B. Second embodiment:

Fig. 6 shows a schematic configuration around the lubricating oil outflow suppression device 190 as the second embodiment. In FIG. 6, among the constituent elements of the lubricating oil outflow suppression device 190, the same reference numerals as in FIG. The lubricating oil leakage suppressing device 190 differs from the lubricating oil leakage suppressing device 90 only in the shape of the oil cut-off ring 170 and the oil cover 180. The oil cover 180 is provided with an inner side surface 101 in addition to each component of the oil cover 80. The inner side surface 101 is formed extending toward the bearing 52 side from the radially inner end of the bottom surface 81. This inner side surface 101 is formed over the entire circumferential direction.

The second portion 172 of the oil cut-off ring 170 is formed to extend longer toward the bearing 52 than the second portion 72 of the first embodiment. That is, the first portion 171 is formed shorter than the first portion 71 of the first embodiment. Thereby, the inner side surface 101, i.e., the end of the oil cover 180 on the axis AL side, is the entire bearing cover 60 than the end of the second portion 172 on the bearing 52 side. It is located on the side.

According to this lubricating oil leakage suppression device 190, the position of the gap between the inner side surface 101 and the oil cut-off ring 170 (the second part 172) is on the side of the bearing 52 of the second part 172. Since it is offset by a distance D3 from the end to the bearing cover 60 side, the lubricating oil attached to the first part 171 or the lubricating oil attached to the end surface of the bearing 52 side of the second part 172 is As a result, even if it is blown away from the axis AL, these lubricants are less likely to penetrate the bearing cover 60 side than the oil cover 180.

In addition, according to the lubricating oil leakage suppression device 190, the lubricating oil scattered on the inside of the oil cover 180 is guided downwards along the inner surface of the inner side surface 101, so that the lubricating oil, the second part 172 and the oil Intrusion into the gap between the covers 180 can be suppressed. Accordingly, it is possible to suppress the lubricating oil from moving toward the bearing cover 60 of the oil cover 180. As a result, penetration of the lubricating oil into the through hole 61 of the bearing cover 60 can be further suppressed.

C. Variation:

C-1. Modification Example 1:

7 shows the configuration of the oil cover 280 as a modified example of the oil cover 80 described above. In FIG. 7, among the components of the oil cover 280, components identical to those of the oil cover 80 are denoted by the same reference numerals as in FIG. 5. The oil cover 280 differs from the oil cover 80 only in that oil relief grooves 287 and 288 are formed in the bottom surface 281. The oil relief grooves 287 and 288 are formed so as to surround the outside of the first through hole 89, respectively, at a position where the second through holes 83 and 84 are avoided. According to this configuration, the lubricating oil scattered on the oil cover 80 is guided to the oil relief grooves 287 and 288, and is moved downward than the through hole 61 along the oil relief grooves 287 and 288 by gravity. I can. Therefore, it is possible to further suppress the intrusion of the lubricating oil into the through hole 61. These oil relief grooves may be annular or may be one groove communicated from above. In addition, it is sufficient that such an oil relief groove is formed at least at a position above the center of the first through hole 89 of the oil cover 280.

C-2. Variation 2:

Some of the various configurations described above can be appropriately omitted. For example, the bent portions 85 and 86 of the oil covers 80 and 180 may be omitted. Alternatively, the second portion 72 of the oil cut-off ring 70 may be omitted. In this case, the first portion 71 may also be formed at the position of the second portion 72 in the above-described embodiment. Of course, the oil break ring 70 itself may be omitted. In this case, the outer side surface 82 of the oil cover 80 is preferably formed to extend to the vicinity of the main shaft 30. Even with these configurations, the effect of preventing leakage of the lubricating oil by the oil cover 80 is exhibited. However, from the viewpoint that the lubricant can be blown away from the main shaft 30 from a position more spaced apart from the main shaft 30, that is, in a direction spaced apart from the through hole 61, by means of a centrifugal force, the oil cover ( It is more preferable that 80 is provided with the oil cut-off ring 70, and it is more preferable that the oil cut-off ring 70 is provided with the 2nd part 72.

C-3. Variation 3:

The oil relief groove 62 does not necessarily have to be formed in an annular shape. The oil relief groove 62 should just surround the outside of the through hole 61 at a position above the center of the through hole 61 in order to suppress the penetration of lubricating oil into the through hole 61. For example, the oil relief groove 62 may have an inverted U-shape or an arc shape that terminates below the center of the through hole 61. Even with such a shape, since it is difficult for the lubricating oil to move in the direction opposite to the direction of gravity, that is, upward, it is possible to suitably suppress the intrusion of the lubricating oil into the through hole 61.

In addition, the cross-sectional shape of the oil relief groove 62 is not limited to the above-described example, and can be made into various shapes. For example, the outer circumferential end and the inner circumferential end of the oil relief groove 62 may be cut in parallel to the axis AL to the bottom surface formed as a surface orthogonal to the axis AL. Alternatively, a surface parallel to the axis AL or a surface orthogonal to the axis AL may be partially formed in the middle between the top portion 62a and the bottom portion 62c. Alternatively, there may be an uneven shape in the middle between the top portion 62b and the bottom portion 62c.

C-4. Modification Example 4:

The oil relief groove 62 and the oil break ring 70 described above exhibit a remarkable effect of suppressing the outflow of lubricating oil by combining both of them, but it is also possible to use only one of them alone. For example, you may combine the oil relief groove 62 and labyrinth seal mentioned above. Even in this way, compared with the case where the outflow of lubricating oil is suppressed only by the labyrinth seal, the effect of suppressing the outflow of lubricating oil can be enhanced. In this case, the oil relief groove 62 is preferably formed in the vicinity of the through hole 61.

C-5. Modification 5:

The shape of the groove 73 of the oil break ring 70 can be any shape. For example, the groove end portion 73b may be terminated in a rectangular shape. Alternatively, the groove end portion 73b may be opened similarly to the groove end portion 73a. Of course, the groove 73 need not be formed.

C-6. Variation 6:

The above-described configuration for suppressing the outflow of lubricating oil is not limited to the pump 20, and can be applied to various rotary machines including bearings using lubricating oil, for example, a compressor, a blower, and the like.

D. Third embodiment:

Fig. 8 is a cross-sectional view showing a schematic configuration of a lubricating oil outflow suppression device 390 as a third embodiment. In Fig. 8, the same reference numerals as in Fig. 2 are assigned to the same components as those of the lubricant oil leakage suppression device 90 according to the first embodiment. The lubricating oil leakage suppression device 390 includes a bearing cover 60, an oil cut-off ring 370, and an oil cover 380. The shape of the oil cut-off ring 370 and the oil cover 380 is different from that of the first embodiment, and other points are the same as those of the first embodiment. In the following, only differences from the first embodiment will be described. 9 is a view of the oil cover 380 viewed from the bearing cover 60 side. 10A is a view of the oil disconnection ring 370 viewed from the bearing cover 60 side.

The oil cover 380 is arranged spaced apart from the main shaft 30 between the bearing 52 and the bearing cover 60 as shown in FIG. 8. In this embodiment, the oil cover 380 has a substantially cylindrical shape extending in the direction of the axis line AL. The oil cover 380 is fitted in the stepped portion 67 formed inside the bearing cover 60 in this embodiment. Since the oil cover 380 has a cylindrical shape, the fitting operation can be easily performed by fitting the outer peripheral surface of the oil cover 380 into the inner surface of the stepped portion 67. This oil cover 380 has an intersection surface 381 which intersects (here orthogonal to) the axis line AL, and the intersection surface 381 is arranged so as to surround the circumference of the main shaft 30. It is preferable that the oil cover 380 is substantially orthogonal to the axis line AL. The term “roughly orthogonal” includes a state in which several degrees are inclined with respect to a strictly orthogonal state, and includes an inclination based on a tolerance or mounting accuracy. Further, the crossing surface 381 is disposed adjacent to the bearing 52 on the bearing cover 60 side of the bearing 52. Here, "adjacent" refers to a position that is in contact with the outer ring 52a of the bearing 52 or offset toward the bearing cover 60 by a distance of 1 mm or less from the outer ring 52a in the axis AL direction. Say. In the example shown in FIG. 8, the crossing surface 381 is offset from the outer ring 52a by about 0.5 mm, and a gap 393 is formed between the crossing surface 381 and the outer ring 52a.

The crossing surface 381 is a part of the oil storage part 41 in order to isolate the bearing 52 from the lubricating oil stored in the oil storage area 41a on the side of the bearing cover 60 rather than the crossing surface 381. , Is placed in the above-described position. For example, if the oil cover 380 is not disposed, the lubricating oil in the oil reservoir region 41a is scratched when the ball 52c of the bearing 52 and the inner ring 52b rotate with the rotation of the main shaft 30. It is raised and scattered in a large amount on the bearing cover 60 side. On the other hand, when the crossing surface 381 is in the above-described position, since the crossing surface 381 blocks almost all of the oil reservoir region 41a from the bearing 52, the lubricant that is scraped up by the bearing 52 The amount of is significantly reduced. In other words, the scattering of the lubricating oil to the bearing cover 60 side is remarkably suppressed in the scattering source by the crossing surface 381.

As apparent from the above description, the crossing surface 381 may be disposed only in a region in the circumferential direction in which the oil reservoir region 41a is formed. However, it is preferable that the intersecting surface 381 is disposed so as to surround the main shaft 30 as in the present embodiment. According to this configuration, the lubricating oil scattering from the bearing 52 to the bearing cover 60 side at all positions in the circumferential direction around the main shaft 30 can be effectively blocked by the crossing surface 381. That is, the crossing surface 381 can block most of the lubricating oil scattering on the bearing cover 60 side.

As described above, slightly offsetting the intersection surface 381 is a design in consideration of tolerance. Specifically, when the oil cover 380 is fitted into the bearing cover 60 due to a manufacturing error, when the crossing surface 381 protrudes toward the bearing 52 rather than a predetermined position, the bearing cover 60 and the bearing casing ( 40) In a state where a gap is generated, the crossing surface 381 contacts the outer ring 52a of the bearing 52, and mounting of the bearing cover 60 to the bearing casing 40 is inhibited. The offset of the intersection surface 381 is done to avoid this situation. As also apparent from the effect of the above-described crossing surface 381, ideally, the crossing surface 381 is installed at a position in contact with the outer ring 52a of the bearing 52, in this case, the crossing surface 381 ) Blocks all of the oil reservoir region 41a from the bearing 52.

As shown in Figs. 8 and 9, in the vertical lower portion of the oil cover 380 (lower end in this embodiment), the end of the oil cover 380 on the bearing 52 side is on the bearing cover 60 side. The groove 383 is formed along the axis line AL direction in a range not penetrating the crossing surface 381 located at. Likewise, a groove 384 is formed symmetrically with respect to the axis AL in the upper part in the vertical direction (the upper end in this embodiment) of the oil cover 380. The groove 383 functions as an oil return groove, and the groove 384 functions as an air discharge groove (detailed later).

As shown in FIG. 8, the oil cut-off ring 370 is provided between the bearing 52 and the bearing cover 60 on the outer periphery of the main shaft 30 along the circumferential direction. In this embodiment, the oil cut-off ring 370 has a substantially cylindrical shape extending in the direction of the axis line AL, and at the central portion of the oil cut-off ring 370, the oil cut-off ring 370 has a diameter approximately equal to the diameter of the main shaft 30. A through hole 374 is formed (see Fig. 10A). The oil cut-off ring 370 is fixed to the main shaft 30 by screwing after passing the main shaft 30 through the through hole 374 in the present embodiment. For this reason, when the main shaft 30 rotates, the oil cut-off ring 370 rotates together with the main shaft 30. The diameter of the oil cut-off ring 370 is in a range in which the oil cut-off ring 370 does not contact the oil level OL, as shown in FIG. 8. In this way, when the oil cut-off ring 370 rotates together with the main shaft 30, the oil cut-off ring 370 contacts the oil level OL, and the lubricating oil does not scatter.

The oil break ring 370 is, as shown in FIG. 8, between the end surface 376 of the oil break ring 370 on the bearing cover 60 side and the inner surface 64 of the bearing cover 60. In the state where the small gap 392 is formed, it is formed to extend substantially all over the bearing cover 60 and the bearing 52. The end of the oil break ring 370 on the bearing 52 side in the axial line AL direction is in contact with the inner ring 52b of the bearing 52. The oil cover 380 described above is spaced apart from the oil break ring 370 in a state in which a small gap 391 is formed between the outer surface 375 of the oil break ring 370 and the oil break ring 370 It is placed in a position surrounding the circumference of.

8 and 10(a), in the end surface 376 (refer to FIG. 8) on the bearing cover 60 side of the oil break ring 370, a groove 371 extending in the radial direction It is formed in plural in this radial shape. The groove 371 functions similar to the impeller of the pump when the oil cut-off ring 370 rotates together with the main shaft 30, and the gap 392 between the bearing cover 60 and the oil cut-off ring 370 ), it creates an airflow that goes outward in the radial direction. In particular, in the embodiment, as shown in Fig. 10A, the end portion on the inner circumferential side of the oil cut-off ring 370 is cut out over the entire circumferential direction, and a cutout portion 372 is formed. The notch 372 makes it easy for air to be introduced into the groove 371.

FIG. 10(b) shows an oil cut-off ring 470 as a modified example. In this example, a plurality of grooves 471 are formed in a wing shape. That is, extending obliquely in the radial direction from the outside to the inside, a plurality of sharp non-groove portions 473 from the inside are formed to surround the through hole 474, and a groove 471 between neighboring non-groove portions 473 Is formed. A notch 472 is formed over the entire circumferential direction of the end of the oil cut-off ring 470 on the inner circumferential side. This oil break ring 470 performs the same function as the oil break ring 370.

Such an oil break ring 370 is disposed so as to protrude toward the bearing cover 60 with respect to the oil cover 380 in the axial line AL direction. In this embodiment, the bottom 373 (see FIG. 8) of the groove 371 is disposed on the bearing cover 60 side rather than the oil cover 380 in the axial line AL direction.

According to the oil break ring 370 and the oil cover 380, it is possible to effectively suppress the intrusion of lubricating oil into the through hole 361 of the bearing cover 60. As described above, the scattering of lubricating oil from the bearing 52 is remarkably suppressed by the crossing surface 381 of the oil cover 380, but still, a small amount of lubricating oil is contained in the inner surface 382 of the oil cover 380. It is assumed that intrusion into the gap 391 between the outer surface 375 of the and oil break ring 370. Even in this case, since the inner surface 382 and the outer surface 375 extend in the direction of the axis line AL, the gap 391 between them extends in the direction of the axis line AL, that is, the small gap 391 is a predetermined distance. Since it extends, it is possible to suppress that the lubricating oil that has penetrated into the gap 391 also moves toward the bearing cover 60 and exits from the gap 391. In addition, even if a small amount of lubricating oil has moved to the bearing cover 60 side rather than the gap 391 by riding the oil cut-off ring 370, the lubricating oil on the oil cut-off ring 370 is caused by rotation of the oil cut-off ring 370. It is blown outward in the radial direction by the centrifugal force. In addition, since the end surface 376 of the oil cut-off ring 370 creates an airflow toward the radially outward side by the groove 371, the lubricating oil is more easily blown outward in the radial direction. For this reason, it is possible to suppress the lubricating oil from entering the gap 392 between the bearing cover 60 and the oil break ring 370 and flowing out from the through hole 61 to the outside. In addition, the airflow created by the groove 371 suitably suppresses the movement of the lubricant oil to the main shaft 30 side even if the lubricant oil enters the gap 392.

As shown in Figs. 8 and 3 (Fig. 3 is common to the first embodiment), an oil relief groove 62 is formed on the inner surface of the bearing cover 60 that faces the bearing 52. Has been. The said site|part is formed as a surface orthogonal to the axis line AL in this embodiment. The oil relief groove 62 surrounds the outside of the through hole 61 and is formed in an annular shape in the present embodiment. The oil relief groove 62 is formed to suppress the lubricating oil blown radially outward by the oil break ring 370 from entering the through hole 61 through the gap 392 as described above.

According to this oil relief groove 62, as in the first embodiment, the lubricating oil scattered on the outer surface 63 outside the oil relief groove 62 moves downward by gravity on the outer surface 63. In the case, the lubricating oil can be captured. The lubricating oil trapped in the oil relief groove 62 moves below the through hole 61 along the annular oil relief groove 62 by gravity and returns to the oil reservoir region 41a, so that the through hole 61 ) Do not invade.

In particular, in this embodiment, as shown in Fig. 8, the outer surface 375 of the oil break ring 370 and the top portion 62b on the inner circumferential side of the oil relief groove 62 are at the same position in the radial direction. Is in. For this reason, the lubricating oil blown radially outward from the oil break ring 370 is located outside the oil relief groove 62, for example, even if the blown lubricating oil has a velocity component in the axial line AL direction. It hits the outer surface 63 or the oil relief groove 62. For this reason, the lubricating oil can be captured more reliably in the oil relief groove 62. In addition, compared to the case where the top portion 62b is on the axis AL side than the outer surface 375, it is difficult for the lubricant to enter the clearance 392 between the bearing cover 60 and the oil break ring 370, so that the through hole ( 61) intrusion of the lubricant is further suppressed. However, the configuration in which the top portion 62b is located on the axis line AL side than the outer surface 375 is not excluded. Similarly, the configuration in which the outer surface 375 is located on the axis line AL side than the top portion 62b is not excluded.

8 and 3, a groove 68 is formed in the lower end of the inner surface of the bearing cover 60. The groove 68 is formed in order to further guide the lubricating oil guided downward by the oil relief groove 62 downward. That is, the lubricating oil returned from the oil relief groove 62 to the oil reservoir region 41a is, as shown by arrow A1 in FIG. 8, between the groove 383 of the oil cover 380 and the bearing cover 60. Passing through the groove 68, it can be returned to the oil reservoir 41 located between the bearing 52 and the bearing 51. Thereby, the oil level OL of the oil reservoir region 41a does not rise above the oil level OL of the oil reservoir 41 other than the oil reservoir region 41a.

Similarly, a groove 69 is formed in the upper end of the bearing cover 60. As shown in FIG. 8, this groove 69 communicates with the groove 384 of the oil cover 380, and together with the groove 384, it provides an air discharge path. This air discharge path promotes heat dissipation in the oil reservoir region 41a and promotes the formation of an airflow by the groove 371 of the oil break ring 370. In addition, the air discharge path has an effect of balancing the oil level of the oil reservoir region 41a and the oil level of the oil reservoir 41.

According to the lubricating oil leakage suppression device 390 described above, the scattering of lubricating oil to the bearing cover 60 side accompanying the rotation of the bearing 52 is significantly suppressed in the scattering source by the crossing surface 381. . Further, even if a small amount of lubricating oil has penetrated into the gap 391 between the oil cut-off ring 370 and the oil cover 380, the movement toward the bearing cover 60 is suppressed. For example, even if the lubricating oil has moved toward the bearing cover 60, the lubricating oil is blown outward in the radial direction by the oil break ring 370, and through the groove 62 of the bearing cover 60, the oil reservoir region ( 41a). Further, even if an extremely small amount of lubricating oil reaches the main shaft 30 from the gap 392 between the bearing cover 60 and the oil break ring 370, it is supplemented by the groove 65 constituting the labyrinth seal. In this way, the lubricating oil outflow suppression device 390 exhibits a remarkable lubricating oil outflow suppression effect by having several layers of structures for suppressing outflow of lubricating oil while a plurality of members are functionally related to each other.

E. Fourth embodiment:

Fig. 11 shows a schematic configuration around the lubricating oil leakage suppression device 590 as the fourth embodiment. In FIG. 11, among the components of the lubricating oil outflow suppressing device 590, components identical to those of the lubricating oil outflow suppressing device 390 according to the third embodiment are denoted by the same reference numerals as in FIG. 8. The lubricating oil leakage suppressing device 590 differs from the lubricating oil leakage suppressing device 390 only in the shape of the oil cover 580. As shown in FIG. 11, the oil cover 580 includes an intersection surface 581, an inner wall surface 582, and an outer wall surface 583.

The crossing surface 581 has a disk shape having a through hole in the center, and is arranged so as to surround the main shaft 30. The inner wall surface 582 extends from the radially inner end of the crossing surface 581 toward the bearing cover 60 side over the entire circumferential direction. The outer wall surface 583 extends from the radially outer end of the crossing surface 581 toward the bearing cover 60 side over the entire circumferential direction.

FIG. 12A is a view of the oil cover 580 viewed from the bearing cover 60 side, and FIG. 12B is an arrow A-A of FIG. 12A. As shown, in the vertical lower part (lower part in this embodiment) of the outer wall surface 583, the crossing surface located on the bearing cover 60 side and at the end of the oil cover 580 on the bearing 52 side ( In a range not penetrating 581, a through hole 584 penetrating in the radial direction is formed along the axis line AL direction. This through hole 584 functions as an oil return groove, similarly to the groove 383 of the third embodiment. Similarly, a through hole 585 is formed symmetrically with respect to the axis AL in the vertical upper portion (the upper end portion in this embodiment) of the outer wall surface 583. This through hole 585 functions as an air discharge groove, similarly to the groove 384 of the third embodiment.

According to this oil cover 580, the same effect as the oil cover 380 of the third embodiment is exhibited. In addition, compared to the oil cover 380, the oil cover 580 is easier to manufacture and has fewer materials.

F. Variation:

F-1. Modification Example 1:

The oil cover 380 may be formed to block almost all of the oil reservoir region 41a formed on the bearing cover 60 side rather than the bearing 52 from the bearing 52, and its shape may be an arbitrary shape. can do. For example, the oil cover 380 may have a disk shape in which a through hole is formed in the center. In this case, the oil cover 380 may be fitted inside the bearing casing 40 and disposed in the vicinity of the bearing 52.

E-2. Variation 2:

Each of the constituent elements of the above-described lubricating oil outflow suppression devices 390 and 590 can be used independently, and specific constituent elements can be appropriately omitted. For example, the oil cut-off ring 370 may be omitted. In this case, in the direction orthogonal to the axis line AL, the oil cover 380 is preferably formed to extend to the vicinity of the main axis 30.

It is also possible to apply the configuration described as a modified example of the first and second embodiments to the lubricant oil leakage suppression devices 390 and 590.

As described above, embodiments of the present invention have been described, but the embodiments of the present invention are intended to facilitate understanding of the present invention and do not limit the present invention. It goes without saying that the present invention can be changed and improved without departing from the spirit thereof, and equivalents thereof are included in the present invention. In addition, in the range in which at least part of the above-described problems can be solved, or in the range in which at least part of the effect is exhibited, any combination or omission of each constituent element described in the claims and the specification may be possible.

20: pump
30: spindle
35: impeller
40: bearing casing
41: oil reservoir
41a: oil reservoir area
51: bearing
52: bearing
52a: outer ring
52b: inner ring
52c: ball
60: bearing cover
61, 361: through hole
62: home
62a, 62b: top
62c: bottom
63: outer surface
64: inner side
65: home
66: notch
67: step
68, 69: home
70, 170, 370, 470: Oil break ring
71, 171: first part
72, 172: second site
72a: end face
73: home
73a, 73b: groove end
74: through hole
80, 180, 280, 380, 580: oil cover
81, 281: bottom
82: outer side
83: second through hole
83a: the lowest end
83b: top end
84: second through hole
85, 86: bend
87, 88: notch
89: first through hole
90, 190, 390, 590: Lubricating oil spill suppression device
101: inner side
287: home
371, 471: home
372, 472: notch
373: bottom
374, 474: through hole
375: exterior
376: end face
381, 581: cross section
382: Inner
383, 384: home
391, 392, 393: gap
473: non-groove part
582: inner wall surface
583: outer wall surface
584, 585: through hole
AL: axis line
OL: oil level

Claims (14)

A main axis extending in the axial direction,
A bearing rotatably supporting the main shaft, and a bearing using lubricating oil,
Bearing casing in which an oil reservoir for storing the lubricating oil is formed therein
It is a lubricant leakage suppression device used in a rotating machine equipped with,
A bearing cover for covering one side of the bearing, and a bearing cover having a through hole for penetrating the main shaft in the axial direction;
An oil cover disposed to be spaced apart from the main shaft between the bearing and the bearing cover,
An oil break ring installed along the circumferential direction on the outer periphery of the main shaft between the bearing and the bearing cover
And,
The oil cover has an intersecting surface crossing the axial direction,
The crossing surface is disposed adjacent to the bearing so as to isolate the bearing from the lubricating oil stored in a region on the bearing cover side than in the crossing surface as a part of the oil reservoir, and a part of the lubricating oil is prevented from rotating the bearing. Suppressing being scratched by
The oil cover is spaced apart from the oil break ring and is disposed at a position surrounding the oil break ring,
The oil break ring has a surface parallel to the axial direction while facing an end surface inside the oil cover in a radial direction. The method of claim 1,
Between the oil cover and the oil break ring, a cylindrical gap extending in the axial direction is formed, the lubricant leakage suppression device. The method according to claim 1 or 2,
The crossing surface of the oil cover is disposed to surround the circumference of the main shaft,
The oil cover has a cylindrical shape extending in the axial direction. The method according to claim 1 or 2,
The crossing surface of the oil cover is disposed to surround the circumference of the main shaft,
The oil cover,
An inner wall extending from the radially inner end of the crossing surface toward the bearing cover over the entire circumferential direction;
A lubricant oil outflow suppression device comprising an outer wall extending toward the bearing cover side from an end portion of the crossing surface radially outward to the entire circumferential direction. The lubrication rate outflow suppression device according to claim 1 or 2, wherein the oil cover is fitted into a step portion formed inside the bearing cover. The lubrication rate leakage suppression device according to claim 1 or 2, wherein the oil cut-off ring is disposed to protrude from the oil cover to the bearing cover side. The method of claim 6,
Lubricant oil outflow suppression device, wherein the end surface of the oil break ring on the bearing cover side has a groove for the end surface to function as a centrifugal blade. The method of claim 7,
Lubricating oil outflow suppression device in which a plurality of radially formed grooves extending in a radial direction are formed on an end surface of the oil break ring on the bearing cover side. The method of claim 7,
Lubricant oil outflow suppression device, wherein a plurality of grooves are formed in a blade shape on an end surface of the oil break ring on the bearing cover side. The method according to claim 1 or 2,
Lubricant oil outflow suppression device in which an oil relief groove surrounding the outer side of the through hole is formed at a position on the inner surface of the bearing cover facing the bearing at least at a position above the center of the through hole of the bearing cover . The method of claim 10,
The oil relief groove is formed by an inclined surface facing the side of the axis and crossing obliquely with respect to the axis. The method of claim 10,
An outer surface of the oil break ring and a top surface of the inner circumferential side of the oil relief groove are at the same position in the radial direction. A rotating machine comprising the lubricant oil leakage suppression device according to claim 1 or 2, the main shaft, the bearing, and the bearing casing. A main axis extending in the axial direction,
A bearing rotatably supporting the main shaft, and a bearing using lubricating oil,
Bearing casing in which an oil reservoir for storing the lubricating oil is formed therein
It is a method of suppressing the leakage of lubricating oil in a rotating machine equipped with,
An oil cover having an intersecting surface crossing the axial direction between the bearing and a bearing cover for covering one side of the bearing, and in which a through hole for penetrating the main shaft in the axial direction is formed. Is spaced apart from the main shaft, and the crossing surface is disposed adjacent to the bearing so as to isolate the bearing from the lubricating oil stored in a region on the bearing cover side than the crossing surface as a part of the oil reservoir, It suppresses that a part is scraped up by the rotation of the bearing,
An oil break ring having a surface parallel to the axial direction while facing an end surface in the radial direction of the oil cover, so that the oil cover is spaced apart from the oil break ring and surrounds the oil break ring, A method for suppressing lubricating oil outflow, arranged between the bearing and the bearing cover in a circumferential direction on an outer periphery of the main shaft to prevent the lubricating oil from flowing out from the through hole.

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