JP6440516B2 - Bearing device and rotating machine - Google Patents

Description

  The present disclosure relates to a bearing device and a rotating machine for rotatably supporting a rotating shaft.

  In general, a rotary machine such as a steam turbine or a gas turbine includes a bearing device for rotatably supporting a rotor shaft (rotating shaft). Usually, lubricating oil is interposed between the outer peripheral surface of the rotor shaft and the bearing surface of the bearing portion that supports the rotor shaft in order to ensure lubricity therebetween.

  For example, Patent Document 1 describes a tilting pad bearing configured to support a rotor shaft by a plurality of bearing pads arranged in a circumferential direction of a rotating shaft. In this tilting pad bearing, lubricating oil is supplied between the outer peripheral surface of the rotor shaft and the bearing surface of the bearing pad from a plurality of oil supply nozzles provided upstream and downstream of the bearing pad. ing. Note that side plates are arranged on both end faces of the lower half carrier ring so as to suppress leakage of the lubricating oil supplied from the oil supply nozzle to the outside.

International Publication No. 2010/097990

However, in the tilting pad bearing described in Patent Document 1, the oil flowing from the upstream side toward the downstream side between the bearing surface of the bearing pad and the outer peripheral surface of the rotor shaft as the rotor shaft rotates, The temperature is raised by friction with the bearing surface of the bearing pad or the outer peripheral surface of the rotor shaft. For this reason, as the bearing pad on the downstream side accumulates frictional heat and oil having a higher temperature flows, the temperature rises remarkably. Since an excessive temperature rise of the bearing pad may be one of the factors that cause a malfunction of the bearing device, a technique for suppressing the temperature rise of the bearing pad is required.
In this regard, Patent Document 1 does not disclose any specific measures for suppressing the temperature rise of the bearing pad.

  In view of the above-described circumstances, at least one embodiment of the present invention aims to provide a bearing device and a rotary machine that can effectively suppress the temperature rise of the bearing portion.

(1) A bearing device according to at least one embodiment of the present invention includes:
With carrier ring,
A first bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring;
A second bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring on the downstream side in the rotational direction of the rotor shaft from the first bearing portion;
On both sides in the axial direction of the carrier ring, a pair of side plates installed along the outer periphery of the rotor shaft;
The flow direction of the oil that is provided on the downstream side of the first bearing portion and the upstream side of the second bearing portion and that has passed between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft. A first oil guide configured to change and guide the oil;
An oil discharge port portion provided on the carrier ring or each of the side plates, and configured to discharge the oil guided by the first oil guide portion to the outside;
It is characterized by providing.

  According to the bearing device of the above (1), the inner peripheral surface of the first bearing portion and the rotor shaft are provided by the first oil guide portion provided on the downstream side of the first bearing portion and the upstream side of the second bearing portion. The flow direction of the oil that has passed through and between the outer peripheral surfaces and increased in temperature changes, and the oil is guided. And the high temperature oil guided by the 1st oil guide part is discharged | emitted outside from the drain port provided in the carrier ring or each side plate. As a result, at least a portion of the oil that has been heated between the first bearing portion and the rotor shaft does not flow between the second bearing portion and the rotor shaft, but is discharged to the outside. Therefore, the temperature rise of the second bearing portion can be effectively suppressed.

(2) In one embodiment, in the configuration of (1) above,
The first oil guide part includes a scraper provided on the downstream side of the first bearing part,
Of the upstream end surface of the scraper, the regions at both ends in the axial direction are offset with respect to the axial direction so as to shift toward the downstream side in the rotational direction of the rotor shaft with increasing distance from the central portion in the axial width of the first bearing portion. Is inclined.
According to the configuration of (2) above, the high-temperature oil flowing in the circumferential direction of the rotor shaft between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft changes its flow direction by the scraper. And guided to both sides in the axial direction along the inclined surface of the scraper. Therefore, inflow of high-temperature oil into the second bearing portion can be avoided, and the temperature rise of the second bearing portion can be effectively suppressed.

(3) In another embodiment, in the configuration of (1) above,
The first oil guide part includes an oil recovery box provided on the downstream side of the first bearing part,
The oil recovery box is
An oil inlet provided on an upper surface of the oil recovery box and opening in a gap between an inner peripheral surface of the first bearing portion and an outer peripheral surface of the rotor shaft;
An internal flow path provided to extend in the axial direction inside the oil recovery box, and communicated with the oil inlet;
An oil outlet provided on a side surface or a bottom surface of the oil recovery box, for communicating the internal flow path and the oil outlet;
including.
According to the configuration of (3) above, the high-temperature oil flowing in the circumferential direction of the rotor shaft between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft flows from the oil inlet portion to the oil recovery box. The oil flows into the interior of the oil recovery box, passes through the internal flow path portion, and is discharged from the oil discharge port portion through the oil outlet portion provided on the side surface or bottom surface of the oil recovery box. Therefore, inflow of high-temperature oil into the second bearing portion can be avoided, and the temperature rise of the second bearing portion can be effectively suppressed.

(4) In some embodiments, in any one of the above configurations (1) to (3),
The oil drain port includes an opening formed in each of the side plates on the downstream side of the first bearing portion and the upstream side of the second bearing portion.
According to the configuration of (4) above, the high-temperature oil flowing in the circumferential direction of the rotor shaft between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft is allowed to flow to the inner peripheral surface of the second bearing portion. Before flowing between the outer peripheral surface of the rotor shaft and the rotor shaft, it can be smoothly discharged to the outside through an opening formed in the side plate.

(5) In some embodiments, in any one of the above configurations (1) to (4),
The oil drain port includes a hole provided in the carrier ring on the downstream side of the first bearing portion and on the upstream side of the second bearing portion.
According to the configuration of (5) above, the high-temperature oil that flows in the circumferential direction of the rotor shaft between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft Before flowing between the rotor shaft and the outer peripheral surface of the rotor shaft, it can be smoothly discharged through a hole provided in the carrier ring.

(6) In some embodiments, in any one of the above configurations (1) to (5),
The region on the carrier ring side of the inner peripheral surface of each side plate extends in the circumferential direction along the side surface of the first bearing portion in at least a part of the extending range of the first bearing portion. A groove is formed,
Oil that has flowed into the groove through a gap between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft is guided, and the downstream end of the first bearing portion and the upstream of the second bearing portion A second oil guide portion configured to return the oil between the side end portions is further provided.
According to the configuration of (6) above, the relatively low-temperature oil flowing in the groove extending in the circumferential direction along the side surface of the first bearing portion is caused to flow downstream from the downstream end portion of the first bearing portion by the second oil guide portion. And the upstream end portion of the second bearing portion. Therefore, relatively low temperature oil can be supplied between the inner peripheral surface of the second bearing portion and the outer peripheral surface of the rotor shaft, and the temperature increase of the second bearing portion can be more effectively suppressed. In the configuration of (1), the second oil guide is used instead of the oil that flows between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft and is discharged to the outside from the oil discharge port portion. The amount of oil supplied from the outside can also be reduced by returning relatively low temperature oil by the unit.

(7) In one embodiment, in the configuration of (6) above,
The first oil guide portion and the second oil guide portion are formed by two flow paths that intersect each other through different positions in the radial direction of the carrier ring.
As described above, the first oil guide portion is configured to change the flow direction of the oil that has passed between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft and guide the oil to be discharged to the outside. It has become. On the other hand, the 2nd oil guide part is constituted so that the oil which flows through the groove formed along the side of the 1st bearing part may be returned between the 1st bearing part and the 2nd bearing part. That is, by the first oil guide portion and the second oil guide portion, mainstream oil that flows toward the downstream side in the rotation direction of the rotor shaft along the outer peripheral surface of the rotor shaft is supplied to the inner peripheral surface of the first bearing portion and the rotor shaft. The relatively high-temperature oil that has passed between the outer peripheral surfaces of the first and second outer peripheral surfaces is replaced with a relatively low-temperature oil that flows through a groove formed along the side surface of the first bearing portion.
In this regard, as in the above (7), if the first oil guide portion and the second oil guide portion are formed by two flow passages that intersect each other, it becomes possible to smoothly replace the mainstream oil. .

(8) In some embodiments, in the above configuration (6) or (7),
The second oil guide portion includes a rectifying wall provided on each side plate so as to protrude toward the carrier ring in the groove,
The rectifying wall is inclined with respect to a direction orthogonal to the axial direction of the rotor shaft so as to approach the carrier ring toward the downstream side in the rotational direction of the rotor shaft.
According to the configuration of (8) above, the second oil guide portion includes the rectifying walls provided on the respective side plates so as to protrude toward the carrier ring in the groove, so that the oil flowing in the groove by the rectifying wall The flow direction can be changed to face the center side in the width direction of the second bearing portion. Further, the flow straightening wall is inclined with respect to the direction orthogonal to the axial direction of the rotor shaft so as to approach the carrier ring as it goes downstream in the rotational direction of the rotor shaft, so that the flow of oil in the groove is obstructed. The flow direction can be changed smoothly.

(9) In some embodiments, in any one of (6) to (8) above,
The second oil guide part includes an internal flow path provided inside the side plate so as to communicate between an oil inlet hole and an oil outlet hole respectively opened in the groove,
The oil inlet hole is provided to be located on a side of the first bearing portion,
The oil outlet hole is provided at a circumferential position between a downstream end portion of the first bearing portion and an upstream end portion of the second bearing portion.
According to the configuration of (9) above, the second oil guide portion does not obstruct the flow of the relatively high temperature oil that is guided by the first oil guide portion and discharged from the oil discharge port portion. The oil flowing through the groove can be guided from the side of the first bearing portion to the upstream end portion of the second bearing portion via the internal flow path.

(10) In some embodiments, in any one of the above configurations (6) to (9),
The groove extends along the outer periphery of the rotor shaft in a circumferential range including an extending range of the first bearing portion and the second bearing portion.
According to the configuration of (10) above, leakage occurs to the side of the first bearing portion through the groove provided in the side plate in the circumferential range including the extending range of the first bearing portion and the second bearing portion. The relatively low temperature oil can be guided downstream toward the upstream end of the second bearing portion.

(11) In some embodiments, in any one of the above configurations (6) to (10),
When the total width in the axial direction of each side plate is W and the axial width of the groove is W _g , 0.15W ≦ W _g is satisfied.
As a result, the flow passage cross-sectional area of the groove can be sufficiently ensured, and relatively low temperature oil leaked laterally from the gap between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft can be obtained. It can be effectively guided downstream toward the second oil guide.

(12) In some embodiments, in any one of the above configurations (6) to (11),
A fin provided on an inner peripheral surface of each of the side plates and extending along the outer periphery of the rotor shaft on both sides in the rotational direction of the rotor shaft across the downstream end portion of the first bearing portion; ,
The groove is formed by a recess defined by the fin and an inner peripheral surface of the side plate closer to the carrier ring than the fin.
According to the configuration of (12) above, the grooves (recesses) can be formed with a simple configuration by providing the fins on the inner peripheral surface of the side plate along the outer periphery of the rotor shaft. Further, since the portions other than the fins on the outer peripheral surface of the side plate function as grooves, the relatively low temperature leaked sideways from the gap between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft. It is possible to sufficiently secure the flow path cross-sectional area of the groove for guiding the oil.

(13) In some embodiments, in any one of the above configurations (6) to (12),
The clearance between the inner peripheral surface of each of the side plates and the outer peripheral surface of the rotor shaft is such that at least a part of the circumferential region in the extending range of the first bearing portion is closer to the first bearing portion. It is narrower than at least a part of the circumferential range upstream from the upstream end and downstream from the downstream end of the second bearing portion.
As described in (6) above, in at least a part of the extended range of the first bearing portion, leakage occurs laterally from the gap between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft. A groove for guiding relatively low temperature oil is provided in the side plate. Therefore, as in (13) above, by relatively reducing the gap between the inner peripheral surface of the side plate and the outer peripheral surface of the rotor shaft in the circumferential region of at least a part of the extending range of the first bearing portion, The relatively low temperature oil in the groove can be prevented from being discharged to the outside through the gap. Thereby, the flow rate of the relatively low temperature oil (oil flowing in the groove) guided toward the second bearing portion by the second oil guide portion can be sufficiently ensured.

(14) In some embodiments, in any one of the above configurations (6) to (13),
The bottom surface of the groove is located on the inner side in the radial direction of the carrier ring as compared with the outer peripheral surface of the first bearing portion.
According to the configuration of (14) above, since the groove is located on the radially inner side of the carrier ring with respect to the outer peripheral surface of the first bearing portion, the groove is surrounded by the bottom and side surfaces of the side plate groove and the side surface of the first bearing portion. The relatively low temperature oil leaked to the side from the first bearing portion can be received in the space.

(15) In some embodiments, in any one of the above configurations (1) to (14),
A semi-annular bearing portion provided on the inner peripheral side of the upper half region of the carrier ring, and configured to hold down the rotor shaft from above;
Each of the first bearing portion and the second bearing portion is a pair of bearing pads provided on the inner peripheral side of the lower half region of the carrier ring and configured to support the rotor shaft from below.
According to the configuration of (15) above, since the semi-annular bearing portion is provided on the inner circumferential side of the upper half region of the carrier ring, the semi-annular bearing portion can suppress the jumping of the rotor shaft, and the rotor It is possible to prevent damage to each part of the rotating machine due to the shaft bouncing. Further, since the first bearing portion and the second bearing portion (a pair of bearing pads) are provided in the lower half region of the carrier ring, the rotor shaft can be appropriately supported by the pair of bearing pads.

(16) A rotating machine according to at least one embodiment of the present invention includes:
The bearing device according to any one of (1) to (15) above;
A rotating shaft supported by the bearing device.
According to the rotating machine of (16) above, since the temperature rise of the second bearing portion of the bearing device can be suppressed, the rotating machine can be smoothly operated.

  According to at least one embodiment of the present invention, the oil that has passed through between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft and is heated to the outside is discharged to the outside. The temperature rise can be effectively suppressed.

It is sectional drawing along the axial direction of the bearing apparatus which concerns on one Embodiment. It is the sectional view on the AA line of FIG. It is a perspective view which shows partially the lower half area | region of the bearing apparatus which concerns on one Embodiment. FIG. 4 is a development view in which a lower half region of the bearing device shown in FIG. 3 is viewed from a C direction. FIG. 4 is a cross-sectional view of the lower half area of the bearing device shown in FIG. 3 taken along the line DD. FIG. 4 is an arrow view in the E direction of the lower half region of the bearing device shown in FIG. 3. It is a perspective view which shows partially the lower half area | region of the bearing apparatus which concerns on other embodiment. It is the expanded view which looked at the lower half area | region of the bearing apparatus shown in FIG. 7 from the F direction. It is the GG sectional view taken on the lower half area | region of the bearing apparatus shown in FIG. It is the HH sectional view taken on the lower half area | region of the bearing apparatus shown in FIG. FIG. 8 is a cross-sectional view (corresponding to a cross section taken along line GG in FIG. 7) showing a modification of the bearing device shown in FIG. 7. FIG. 10 is a cross-sectional view (corresponding to a cross section taken along line GG in FIG. 7) showing another modification of the bearing device shown in FIG. 7. It is sectional drawing which shows the structural example of the side plate in other embodiment. It is sectional drawing (corresponding to GG of FIG. 7) which shows partially the lower half area | region of the bearing apparatus in other embodiment. FIG. 10 is a cross-sectional view (corresponding to GG in FIG. 7) partially showing a lower half region of the bearing device in still another embodiment.

  Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described in the embodiments or shown in the drawings are not intended to limit the scope of the present invention, but are merely illustrative examples. Absent.

First, an overall configuration common to the bearing device 10 according to some embodiments will be described with reference to FIGS. 1 and 2.
FIG. 1 is a cross-sectional view along the axial direction of a bearing device 10 according to an embodiment. 2 is a cross-sectional view taken along line AA in FIG. FIG. 2 is a cross section orthogonal to the axial direction. In the present embodiment, the axial direction is the direction of the central axis O of the rotor shaft 2 supported by the bearing device 10, the radial direction is the radial direction of the rotor shaft 2, and the circumferential direction is the rotor shaft 2. In the circumferential direction.

  The bearing device 10 shown in FIGS. 1 and 2 is a tilting pad bearing (journal bearing) that employs a direct lubrication method as a lubrication method (oil supply method), and a first bearing portion (first bearing pad 30) in a lower half region. ) And the second bearing portion (second bearing pad 32). Hereinafter, the illustrated bearing device 10 will be described as an example, but the bearing device 10 according to the present embodiment is not limited to this configuration. For example, the bearing device 10 according to another embodiment may be a thrust bearing, or may employ an oil bath method or another lubrication method as a lubrication method. In another embodiment, two additional bearing pads may be arranged in the upper half region, and a total of four bearing pads may be attached in the circumferential direction. A configuration in which more than one bearing pad is attached may be used.

The rotating machine 1 to which the bearing device 10 according to the present embodiment is applied includes a turbine such as a gas turbine or a steam turbine (for example, a steam turbine of a nuclear power plant) or a turbine for driving a machine, a wind machine such as a wind power generator, Or a supercharger etc. are mentioned.
Here, the rotary machine 1 includes a rotor shaft 2 that is rotationally driven, a bearing housing (not shown) that houses the rotor shaft 2, and a bearing device 10 that supports the rotor shaft 2.

  In one embodiment, the bearing device 10 includes a carrier ring 11 attached to a bearing housing (not shown) of the rotating machine 1, and a first bearing pad 30 and a second bearing pad arranged on the inner peripheral side of the carrier ring 11. 32.

  The bearing device 10 further includes first oil guide portions 40 and 50 and oil discharge port portions 42 and 52 (see FIGS. 3 to 7) as a configuration for suppressing the temperature rise of the second bearing pad 32. . A configuration including the first oil guide portions 40 and 50 and the oil discharge port portions 42 and 52 will be described later.

Hereinafter, a specific configuration example of each member of the bearing device 10 will be described.
The carrier ring 11 includes an upper half carrier ring 12 and a lower half carrier ring 13. The upper half carrier ring 12 and the lower half carrier ring 13 have inner circumferential surfaces 12a and 13a and outer circumferential surfaces 12b and 13b, respectively, such that the cross section perpendicular to the axial direction is a semicircular arc. In the illustrated example, the carrier ring 11 is divided into an upper half carrier ring 12 and a lower half carrier ring 13. However, the carrier ring 11 may be an integral structure.

  A pair of side plates 17 and 18 are disposed along the outer periphery of the rotor shaft 2 on both ends of the carrier ring 11 in the axial direction. The side plates 17 and 18 are formed in a disc shape, and a hole through which the rotor shaft 2 passes is formed in the center. By these side plates 17 and 18, leakage of lubricating oil supplied from oil supply nozzles 25 to 28 described later is appropriately suppressed.

In the upper half carrier ring 12, guide metals (semi-annular bearing portions) 20 and 21 are attached to the inner peripheral surface 12a in order to mainly suppress the bounce of the rotor shaft 2 from above. For example, a pair of guide metals 20 and 21 are attached to both ends of the upper half carrier ring 12 in the axial direction and inside the side plates 17 and 18 in the axial direction. The guide metals 20 and 21 are formed in a semicircular shape.
Thus, since the guide metals 20 and 21 are provided on the inner peripheral side of the upper half carrier ring 12, the guide metal 20 and 21 can suppress the jumping of the rotor shaft 2. Parts can be prevented from being damaged. In the case where the carrier ring 11 is not a structure divided into the upper half carrier ring 12 and the lower half carrier ring 13 but an integral structure, or a structure divided into three or more, the guide metals 20, 21 May be provided in the upper half region of the carrier ring 11.

The upper half carrier ring 12 and the lower half carrier ring 13 are provided with at least one oil supply nozzle 25 to 28.
In the example shown in FIG. 2, when the rotor shaft 2 rotates clockwise as indicated by an arrow S in the figure, the first oil supply nozzle 25, the second oil supply nozzle 26, the first oil supply nozzle 25 from the upstream side in the rotation direction S of the rotor shaft 2. A total of four oil supply nozzles including three oil supply nozzles 27 and a fourth oil supply nozzle 28 are provided. The first oil supply nozzle 25 and the second oil supply nozzle 26 are arranged side by side in the circumferential direction on the upstream side of the first bearing pad 30 located on the upstream side. A gap may be provided between the second oil supply nozzle 26 and the upstream end of the bearing pad 30. The third oil supply nozzle 27 is disposed between the first bearing pad 30 and the second bearing pad 32 located on the downstream side of the first bearing pad 30. A gap may be provided between the third oil supply nozzle 27 and the second bearing pad 32. The fourth oil supply nozzle 28 is disposed on the downstream side of the second bearing pad 32. A gap may be provided between the fourth oil supply nozzle 28 and the second bearing pad 32.

  A lubricating oil supply path (not shown) is formed inside the carrier ring 11. The lubricating oil supplied to the lubricating oil supply path is sent to each of the oil supply nozzles 25 to 29, and is ejected from the oil supply nozzles 25 to 29 in the vicinity of the bearing pads 30 and 32.

The 1st bearing pad 30 and the 2nd bearing pad 32 are provided in the inner peripheral side of the lower half carrier ring 13, and are comprised so that the rotor shaft 2 may be supported from the downward direction.
The first bearing pad 30 is provided along the outer periphery of the rotor shaft 2 on the inner peripheral side of the lower half carrier ring 13.
The second bearing pad 32 is provided along the outer periphery of the rotor shaft 2 on the inner peripheral side of the lower half carrier ring 13 and downstream of the first bearing pad 30 in the rotational direction S of the rotor shaft 2.
Thus, since the first bearing pad 30 and the second bearing pad 32 are provided on the lower half carrier ring 13, the rotor shaft 2 can be appropriately supported by the first bearing pad 30 and the second bearing pad 32.

In addition, when the carrier ring 11 is not a structure divided into the upper half carrier ring 12 and the lower half carrier ring 13 but is an integral structure, or a structure divided into three or more, the first bearing pad 30. The second bearing pad 32 may be provided in the lower half region of the carrier ring 11.
Moreover, the 1st bearing pad 30 and the 2nd bearing pad 32 point out the two bearing pads adjacent to the circumferential direction, Comprising: It does not point out a specific bearing pad. For example, in a configuration in which three bearing pads are provided in order from the upstream side in the rotation direction S, when attention is paid to the most upstream bearing pad and the intermediate bearing pad, the most upstream bearing pad becomes the first bearing pad 30, The intermediate bearing pad becomes the second bearing pad 32. Alternatively, when attention is paid to the intermediate bearing pad and the most downstream bearing pad, the intermediate bearing pad becomes the first bearing pad 30, and the most downstream bearing pad becomes the second bearing pad 32.

  Next, the configurations of the first oil guide portions 40 and 50 and the oil discharge port portions 42 and 52 will be specifically described with reference to FIGS.

In some embodiments, as shown in FIGS. 3, 4, 7 and 8, the first oil guides 40, 50 are located downstream of the first bearing pad 30 and on the second bearing pad 32. It is provided on the upstream side, and is configured to guide the oil by changing the flow direction of the oil that has passed between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2.
The oil discharge ports 42 and 52 are provided in the carrier ring 11 (lower half carrier ring 13) or the respective side plates 17 and 18, and discharge the oil guided by the first oil guide portions 40 and 50 to the outside. It is configured as follows.

  According to this configuration, the first oil guide portions 40 and 50 provided on the downstream side of the first bearing pad 30 and the upstream side of the second bearing pad 32, and the inner peripheral surface 30 a of the first bearing pad 30. The flow direction of the oil that has passed through the outer peripheral surface of the rotor shaft 2 and increased in temperature changes, and the oil is guided. The high-temperature oil guided by the first oil guide portions 40 and 50 is discharged to the outside from the lower half carrier ring 13 or the oil drain ports 42 and 52 provided in the side plates 17 and 18. . As a result, at least a portion of the oil that has been heated between the first bearing pad 30 and the rotor shaft 2 does not flow between the second bearing pad 32 and the rotor shaft 2 and is discharged to the outside. The Therefore, the temperature rise of the second bearing pad 32 can be effectively suppressed.

  The above-described oil supply nozzle (third oil supply nozzle) 27 is provided between the first oil guide portions 40 and 50 and the upstream end portion of the second bearing pad 32. The oil ejected from the oil ejection hole 27 b of the oil supply nozzle 27 is supplied between the inner peripheral surface 32 a of the second bearing pad 32 and the outer peripheral surface of the rotor shaft 2. Therefore, the amount of oil that is deficient due to the oil being discharged to the outside by the first oil guide portions 40 and 50 and the oil discharge port portions 42 and 52 is compensated by the oil newly supplied from the oil supply nozzle 27. Therefore, a sufficient amount of oil that can ensure good lubricity can be supplied between the inner peripheral surface 32 a of the second bearing pad 32 and the outer peripheral surface of the rotor shaft 2.

  In one embodiment, the bearing device 10 includes a first bearing at least part of the extending range of the first bearing pad 30 in the region on the lower half carrier ring 13 side of the inner peripheral surfaces of the side plates 17 and 18. Grooves 17b and 18b extending in the circumferential direction along the side surface of the pad 30 are formed. For example, the grooves 17b and 18b are formed by protruding portions 17a and 18a provided on the inner peripheral surfaces of the side plates 17 and 18, and the side plates 17 and 18a on the lower half carrier ring 13 side of the protruding portions 17a and 18a. It is formed by a recess defined by 18 inner peripheral surfaces. The protrusions 17 a and 18 a extend along the outer periphery of the rotor shaft 2 on both sides in the rotational direction S of the rotor shaft 2 across the downstream end portion of the first bearing pad 30. Thus, by providing the protrusions 17a and 18a on the inner peripheral surfaces of the side plates 17 and 18 along the outer periphery of the rotor shaft 2, the grooves (recesses) 17b and 18b can be formed with a simple configuration. Can do.

The grooves 17b and 18b may extend along the outer periphery of the rotor shaft 2 in a circumferential range including the extending range of the first bearing pad 30 and the second bearing pad 32.
Thereby, in the circumferential direction range including the extending range of the first bearing pad 30 and the second bearing pad 32, the grooves 17 b and 18 b provided in the side plates 17 and 18 are provided to the side of the first bearing pad 30. The leaked relatively low temperature oil can be guided downstream toward the upstream end of the second bearing pad 32.

The bottom surfaces of the grooves 17 b and 18 b (surfaces facing the outer peripheral surface of the rotor shaft 2) are located on the inner side in the radial direction of the lower half carrier ring 13 compared to the outer peripheral surface 30 b of the first bearing pad 30.
According to this configuration, since the grooves 17b and 18b are located radially inward from the outer peripheral surface 30b of the first bearing pad 30, the oil flowing through the grooves 17b and 18b flows into the outer peripheral surface 30b of the first bearing pad 30. I can prevent that.
Note that the bottom surfaces of the grooves 17 b and 18 b may be positioned on the inner side in the radial direction of the lower half carrier ring 13 as compared with the outer peripheral surface 32 b of the second bearing pad 32.

As shown in FIGS. 4 and 8, when the total width in the axial direction of each of the side plates 17 and 18 is W and the axial width of the grooves 17b and 18b is W _g , 0.15 W ≦ W _g is satisfied. You may make it satisfy | fill.
Thereby, the flow path cross-sectional area of the grooves 17b and 18b can be sufficiently ensured, and leaked laterally from the gap between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2. The relatively low temperature oil can be effectively guided downstream toward the second oil guide portion 60.

As shown in FIGS. 3 to 12, in some embodiments, the bearing device 10 further includes second oil guide portions 60 and 70 in addition to the above configuration.
The second oil guide portions 60 and 70 guide oil flowing into the grooves 17b and 18b from the gap between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2, and the first bearing pad 30 Between the downstream end of the second bearing pad 32 and the upstream end of the second bearing pad 32.

  According to the above configuration, the relatively low temperature oil flowing in the grooves 17 b and 18 b extending in the circumferential direction along the side surface of the first bearing pad 30 is caused to flow into the first bearing pad 30 by the second oil guide portions 60 and 70. It is returned between the downstream end and the upstream end of the second bearing pad 32. Therefore, relatively low temperature oil can be supplied between the inner peripheral surface 32a of the second bearing pad 32 and the outer peripheral surface of the rotor shaft 2, and the temperature rise of the second bearing pad 32 can be more effectively suppressed. . Further, instead of the oil that flows between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 and is discharged to the outside from the oil discharge port portions 42 and 52, the second oil guide portion 60 is provided. , 70 to return the relatively low temperature oil, the amount of oil supplied from the outside via the oil supply nozzle 27 can be reduced.

As shown in FIGS. 3 and 7, in one embodiment, the first oil guide portions 40, 50 and the second oil guide portions 60, 70 pass each other through different positions in the radial direction of the lower half carrier ring 13. It is formed by two intersecting flow paths (first flow paths 43 and 53 and second flow paths 63 and 73).
The first flow paths 43 and 53 are formed by the first oil guide portions 40 and 50. The high-temperature oil that has passed between the inner peripheral surface 30 a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 passes along the rotation direction S of the rotor shaft 2 by passing through the first flow paths 43 and 53. The flow direction changes from the flowing main flow and is guided to the oil drain ports 42 and 52. On the other hand, the second flow paths 63 and 73 are formed by the second oil guide portions 60 and 70. The relatively low temperature oil (side flow) flowing in the grooves 17b and 18b along the rotation direction S passes between the first bearing pad 30 and the second bearing pad 32 by passing through the second flow paths 63 and 73. Returned to the mainstream. That is, the main oil flowing through the outer circumferential surface of the rotor shaft 2 toward the downstream side in the rotational direction S of the rotor shaft 2 by the first oil guide portions 40 and 50 and the second oil guide portions 60 and 70 is The relatively high temperature oil that has passed between the inner peripheral surface 30a of the one bearing pad 30 and the outer peripheral surface of the rotor shaft 2 flows through the grooves 17b and 18b formed along the side surface of the first bearing pad 30 relatively. It is designed to be replaced with low temperature oil.
Therefore, as in the above-described configuration, the first oil guide portions 40 and 50 and the second oil guide portions 60 and 70 are divided into two flow passages (first flow passages 43 and 53 and second flow passage 63, 73), the mainstream oil can be replaced smoothly.

In one embodiment, the gap between the inner peripheral surface of each side plate 17, 18 and the outer peripheral surface of the rotor shaft 2 is in the circumferential region of at least a part of the extended range of the first bearing pad 30. The first bearing pad 30 is narrower than at least part of the circumferential range on the upstream side of the upstream end portion and on the downstream side of the downstream end portion of the second bearing pad 32.
Accordingly, the oil is prevented from leaking to the outside from the side plates 17 and 18 on both sides of the first bearing pad 30, and the oil between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 is suppressed. The amount can be secured.

  Next, the bearing device 10 according to each embodiment will be described in detail.

  FIG. 3 is a perspective view partially showing a lower half region of the bearing device 10 according to the embodiment. 4 is a developed view of the lower half region of the bearing device 10 shown in FIG. 3 as viewed from the C direction. FIG. 5 is a cross-sectional view of the lower half area of the bearing device 10 shown in FIG. 6 is a view in the direction of the arrow E of the lower half region of the bearing device 10 shown in FIG.

In the bearing device 10 according to the embodiment, the first oil guide portion 40 includes a scraper 41 provided on the downstream side of the first bearing pad 30.
The scraper 41 is configured to change the flow direction of the main flow of oil flowing between the inner peripheral surface 30 a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 and guide the oil to the oil discharge port portion 42. Yes. The regions of both ends in the axial direction of the upstream side end surface of the scraper 41 are axially shifted so as to be shifted to the downstream side in the rotational direction S of the rotor shaft 2 as they move away from the central portion in the axial width of the first bearing pad 30. It becomes the inclined surfaces 41a and 41a inclined with respect to. The scraper 41 may be fastened to the lower half carrier ring 13 with a bolt (not shown). Further, another scraper 41 may be provided on the downstream side of the second bearing pad 32. In this case, the other scraper 41 provided on the downstream side of the second bearing pad 32 has the same configuration as the scraper 41 provided on the downstream side of the first bearing pad 30 and the upstream side of the second bearing pad 32. .

  The oil drain port 42 includes openings 42 a formed in the side plates 17 and 18 on the downstream side of the first bearing pad 30 and the upstream side of the second bearing pad 32. Specifically, the protrusions 17a and 18a formed on the side plates 17 and 18 are interrupted on the downstream side of the first bearing pad 30 and on the upstream side of the second bearing pad 32, and the protrusions 17a and 18a. Convex portions 17c, 18c and convex portions 17d, 18d projecting inward in the axial direction from the interrupted end portions are provided. The convex portion 17c and the convex portion 17d are arranged so as to be separated from each other in the circumferential direction, and an opening 42a is formed by the respective wall surfaces of the convex portion 17c and the convex portion 17d and the inner peripheral surface of the side plate 17. Similarly, the convex part 18c and the convex part 18d are spaced apart from each other in the circumferential direction, and an opening 42a is formed by the respective wall surfaces of the convex part 18c and the convex part 18d and the inner peripheral surface of the side plate 18. .

  According to the above configuration, the high-temperature oil flowing in the circumferential direction of the rotor shaft 2 between the inner peripheral surface 30 a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 is changed in the flow direction by the scraper 41. It is changed and guided to both sides in the axial direction along the inclined surfaces 41a and 41a of the scraper 41. Therefore, inflow of high-temperature oil into the second bearing pad 32 can be avoided, and the temperature rise of the second bearing pad 32 can be effectively suppressed. Further, high-temperature oil that flows in the circumferential direction of the rotor shaft 2 between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 is removed from the inner peripheral surface 32a of the second bearing pad 32 and the rotor. Before flowing into the space between the outer peripheral surface of the shaft 2, it can be smoothly discharged through the opening 42 a formed in the side plates 17 and 18.

On the other hand, the second oil guide portion 60 is provided with an internal flow path (inside of the side plates 17, 18 provided so as to communicate between the oil inlet hole 44 and the oil outlet hole 45 respectively opened in the grooves 17 b, 18 b. A second flow path 63). The oil inlet hole 44 is provided so as to be located on the side of the first bearing pad 30. Specifically, the oil inlet hole 44 opens at the bottom surface (surface facing the rotor) of the grooves 17b and 18b, and is provided with at least one. The oil outlet hole 45 is provided at a circumferential position between the downstream end of the first bearing pad 30 and the upstream end of the second bearing pad 32. Specifically, the oil outlet hole 45 opens to the bottom surface (surface facing the rotor) of the grooves 17b and 18b, and is provided with at least one. When the oil supply nozzle 27 is provided in the vicinity, the oil outlet hole 45 may be provided downstream of the oil supply nozzle 27 in the rotation direction S and upstream of the second bearing pad 32. . In the illustrated example, the second flow path 63 includes a plurality of first radial flow paths 63a extending radially outward from the plurality of oil inlet holes 44, and a radially outward direction from the plurality of oil outlet holes 45. One circumferential flow that extends in the circumferential direction and communicates with the plurality of second radial flow paths 63b, the plurality of first radial flow paths 63a, and the plurality of second radial flow paths 63b. And a path 63c.
According to this configuration, the side plate 17, the second oil guide portion 60 does not hinder the flow of relatively high temperature oil guided by the first oil guide portion 40 and discharged from the oil discharge port portion 42. The oil flowing through the grooves 17b and 18b can be guided from the side of the first bearing pad 30 to the upstream end of the second bearing pad 32 via the 18 internal flow paths (second flow path 63).

  FIG. 7 is a perspective view partially showing a lower half region of the bearing device 10 according to another embodiment. FIG. 8 is a developed view of the lower half region of the bearing device 10 shown in FIG. 7 as viewed from the F direction. 9 is a cross-sectional view of the lower half region of the bearing device 10 shown in FIG. 10 is a cross-sectional view of the lower half region of the bearing device 10 shown in FIG. FIG. 11 is a cross-sectional view (corresponding to a cross section taken along line GG in FIG. 7) showing a modification of the bearing device 10 shown in FIG. 7. FIG. 12 is a cross-sectional view (corresponding to a cross section taken along line GG in FIG. 7) showing another modification of the bearing device 10 shown in FIG. 7.

In the bearing device 10 according to another embodiment, the first oil guide portion 50 includes an oil recovery box 51 provided on the downstream side of the first bearing pad 30.
The oil recovery box 51 includes an oil inlet 51a provided on the upper surface of the oil recovery box 51, an internal flow path 51b provided in the oil recovery box 51, and a side surface or a bottom surface of the oil recovery box 51. And an oil outlet 51c. The oil recovery box 51 may be fastened to the lower half carrier ring 13 with a bolt 58.

The oil inlet 51 a is opened in a gap between the inner peripheral surface 30 a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2. Then, high-temperature oil flowing between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 flows into the oil recovery box 51 from the oil inlet portion 51a.
The internal flow path portion 51 b communicates with the oil inlet portion 51 a and is provided so as to extend in the axial direction inside the oil recovery box 51. In the example shown in the figure, the internal flow path portion 51 b extends radially outward from the oil inlet portion 51 a and extends in the axial direction inside the oil recovery box 51. The high temperature oil that has flowed from the oil inlet 51a flows through the internal flow path 51b.
The oil outlet 51c is configured to communicate the internal flow path 51b and the oil outlet 52. The high-temperature oil flowing through the internal flow path 51b is discharged from the oil discharge port 52 to the outside through the oil outlet 51c.

  In other embodiments shown in FIGS. 7 to 10, the oil outlet 51c is formed so as to penetrate the side surface of the oil recovery box 51 in the axial direction. On the other hand, the side plates 17 and 18 are provided with oil drain ports 52 formed so as to penetrate the side plates 17 and 18 in the axial direction corresponding to the oil outlet 51c. That is, all the flow paths from the internal flow path portion 51b to the oil discharge port portion 52 through the oil outlet portion 51c extend in the axial direction. In this configuration, high-temperature oil flowing between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 is introduced from the oil inlet portion 51a to the internal flow passage portion 51b, and the internal flow passage portion 51b. Is discharged from the oil discharge port 52 to the outside through the oil outlet 51c.

  In the modification shown in FIG. 11, the oil outlet 51c is formed so as to penetrate the side surface of the oil recovery box 51 in the axial direction. On the other hand, in the side plates 17 and 18, an oil drain port portion 52 is formed corresponding to the oil outlet portion 51c. The oil drain port 52 has an axial oil drain passage 52a formed so as to extend in the axial direction from the surfaces of the side plates 17 and 18 facing the oil recovery box 51, and an axial oil drain passage 52a. And a radial oil drainage passage 52b extending radially outward from the end of each. In this configuration, high-temperature oil flowing between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 is introduced from the oil inlet portion 51a to the internal flow passage portion 51b, and the internal flow passage portion 51b. From the oil outlet 51c through the oil outlet 51c to the axial oil drain passage 52a and then through the radial oil drain passage 52b in the radial direction and discharged to the outside.

  In another modification shown in FIG. 12, the oil outlet 51c is formed so as to penetrate the bottom surface of the oil recovery box 51 in the radial direction. On the other hand, the lower half carrier ring 13 is formed with an oil drain port 52 corresponding to the oil outlet 51c. The oil drain port 52 includes a hole extending along the radial direction in at least a part of the region connected to the oil outlet 51c. In this configuration, high-temperature oil flowing between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 is introduced from the oil inlet portion 51a to the internal flow passage portion 51b, and the internal flow passage portion 51b. From the bottom through the oil outlet portion 51c and the oil outlet portion 52 on the bottom surface to the outside in the radial direction and discharged to the outside.

  According to these configurations, high-temperature oil that flows between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 in the circumferential direction of the rotor shaft 2 flows from the oil inlet 51a to the oil. The oil flows into the collection box 51, passes through the internal flow path portion 51 b, and is discharged from the oil discharge port portion 52 through the oil outlet portion 51 c provided on the side surface or bottom surface of the oil collection box 51. Therefore, inflow of high-temperature oil into the second bearing pad 32 can be avoided, and the temperature rise of the second bearing pad 32 can be effectively suppressed.

Returning to FIGS. 7 to 10, in some embodiments, the second oil guide portion 70 is provided on each side plate 17 and 18 so as to protrude toward the lower half carrier ring 13 in the grooves 17b and 18b. The flow straightening wall 71 is included.
The rectifying wall 71 has an inclined surface 71 a that is inclined with respect to a direction orthogonal to the axial direction of the rotor shaft 2 so as to approach the lower half carrier ring 13 toward the downstream side in the rotational direction S of the rotor shaft 2. ing. In the illustrated example, the rectifying wall 71 has a triangular shape whose one side is an inclined surface 71a in plan view (in the direction of arrow F in FIG. 7). Alternatively, although not shown, the rectifying wall 71 may be formed in a plate shape having an inclined surface 71a. In the illustrated example, the inclined surface 71a has a planar shape. Alternatively, although not shown, the inclined surface 71a may have a curved surface shape that protrudes downstream in the rotation direction S in plan view.

  According to the above configuration, the second oil guide portion 70 includes the rectifying walls 71 provided on the side plates 17 and 18 so as to protrude toward the lower half carrier ring 13 side in the grooves 17b and 18b. The flow direction of the oil flowing through the grooves 17 b and 18 b can be changed by the rectifying wall 71 so as to be directed to the center side in the width direction of the second bearing pad 32. Further, the rectifying wall 71 has an inclined surface 71a inclined with respect to a direction orthogonal to the axial direction of the rotor shaft 2 so as to approach the lower half carrier ring 13 toward the downstream side in the rotational direction S of the rotor shaft 2. Therefore, the flow direction can be smoothly changed without obstructing the oil flow in the grooves 17b and 18b.

  As described above, according to the embodiment of the present invention, oil that has passed through the space between the inner peripheral surface 30a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2 and is heated is discharged to the outside. Therefore, the temperature rise of the second bearing pad 32 can be effectively suppressed.

The present invention is not limited to the above-described embodiments, and includes forms obtained by modifying the above-described embodiments and forms obtained by appropriately combining these forms.
For example, in the embodiment shown in FIGS. 3 to 6, the configuration of the first oil guide portion 40 including the scraper 41 is adopted, but instead of the first oil guide portion 40, FIGS. 7 to 12 are used. You may employ | adopt the structure of the 1st oil guide part 50 containing the oil collection | recovery box 51 in other embodiment shown to these. Moreover, in one Embodiment shown in FIG. 3 thru | or FIG. 6, although the structure of the 2nd oil guide part 60 containing the internal flow path in the side plates 17 and 18 is employ | adopted, Instead, the configuration of the second oil guide portion 70 including the rectifying wall 71 in another embodiment shown in FIGS. 7 to 12 may be adopted. As described above, the constituent elements of the embodiment shown in FIGS. 3 to 6 and the constituent elements of the other embodiments shown in FIGS. 7 to 12 can be appropriately combined.

  Further, in the embodiment shown in FIGS. 3 to 12, the grooves 17b and 18b are formed by the protrusions 17a and 18a provided on the side plates 17 and 18. However, as shown in FIG. The groove 17b may be formed by the provided fin 17a ′. Here, FIG. 13 is a cross-sectional view along the axial direction of the side plate 17 in another embodiment. With reference to FIGS. 3, 7, and 13 described above, the fin 17 a ′ is provided on the inner peripheral surface of the side plate 17, and rotates the rotor shaft 2 across the downstream end portion of the first bearing pad 30. It extends along the outer periphery of the rotor shaft 2 on both sides in the direction. The groove 17b is formed by a recess defined by the fin, 17a ', and the inner peripheral surface of the side plate 17 on the lower half carrier ring 13 side than the fin 17a'. Although the side plate 18 is omitted in the figure, the side plate 18 also has a groove 18b formed by fins. According to this configuration, by providing the fins 17 a ′ on the inner peripheral surfaces of the side plates 17 and 18 along the outer periphery of the rotor shaft 2, grooves (concave portions) can be formed with a simple configuration. Further, since the portions other than the fins 17 a ′ of the outer peripheral surfaces of the side plates 17 and 18 function as the grooves 17 b and 18 b, a gap between the inner peripheral surface 30 a of the first bearing pad 30 and the outer peripheral surface of the rotor shaft 2. It is possible to sufficiently secure the flow path cross-sectional area of the grooves 17b and 18b for guiding the relatively low temperature oil leaking from the side to the side.

Further, in the embodiment shown in FIGS. 3 to 12, the first oil guide portions 40 and 50 and the oil discharge port portions 42 and 52 are provided between the first bearing pad 30 and the second bearing pad 32. The first oil guide portions 40, 50 and the oil discharge port portions 42, 52 may be installed between adjacent arbitrary bearing portions (20, 21, 30, 32).
For example, as shown in FIGS. 14 and 15, two bearing portions adjacent in the circumferential direction among a plurality of bearing portions including a semi-annular bearing portion (guide metal 20, 21) and a bearing pad (30, 32). You may provide the 1st oil guide parts 40 and 50 and the oil drain opening parts 42 and 52 in between. In the exemplary embodiment shown in FIG. 14, between the semi-annular bearing portion (guide metal 20, 21) and the first bearing pad 30, between the first bearing pad 30 and the second bearing pad 32, and A first oil guide portion 40 and an oil discharge port portion 42 are provided between the second bearing pad 32 and the semi-annular bearing portions (guide metals 20, 21). Further, in the exemplary embodiment shown in FIG. 14, between the semi-annular bearing portion (guide metal 20, 21) and the first bearing pad 30, between the first bearing pad 30 and the second bearing pad 32, A first oil guide portion 50 and an oil discharge port portion 52 are provided between the second bearing pad 32 and the semi-annular bearing portions (guide metals 20 and 21).

For example, expressions expressing relative or absolute arrangements such as “in a certain direction”, “along a certain direction”, “parallel”, “orthogonal”, “center”, “concentric” or “coaxial” are strictly In addition to such an arrangement, it is also possible to represent a state of relative displacement with an angle or a distance such that tolerance or the same function can be obtained.
For example, an expression indicating that things such as “identical”, “equal”, and “homogeneous” are in an equal state not only represents an exactly equal state, but also has a tolerance or a difference that can provide the same function. It also represents the existing state.
For example, expressions representing shapes such as quadrangular shapes and cylindrical shapes represent not only geometrically strict shapes such as quadrangular shapes and cylindrical shapes, but also irregularities and chamfers as long as the same effects can be obtained. A shape including a part or the like is also expressed.
On the other hand, the expression “comprising”, “including”, or “having” one constituent element is not an exclusive expression that excludes the presence of the other constituent elements.

DESCRIPTION OF SYMBOLS 1 Rotating machine 2 Rotor shaft 10 Bearing device 11 Carrier ring 12 Upper half carrier ring 13 Lower half carrier ring 17, 18 Side plate 17a, 18a Projection part 17b, 18b Groove 18 Side plate 20, 21 Guide metal (semi-annular ring) Bearing)
25 to 28 Oil supply nozzle 30 First bearing pad 32 Second bearing pad 40, first oil guide portion 41 Scraper 41a Inclined surface 42, 52 Oil discharge port portion 42a Opening portion 43, 53 First flow path 44 Oil inlet hole 45 Oil Outlet hole 51 Oil recovery box 51a Oil inlet 51b Internal channel 51c Oil outlet 52 Oil outlet 52a Axial oil outlet 52b Radial oil outlet 58 Bolt 60, 70 Second oil guide 63, 73 Second flow path 71 Rectifying wall 71a Inclined surface

Claims (17)

With carrier ring,
A first bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring;
A second bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring on the downstream side in the rotational direction of the rotor shaft from the first bearing portion;
On both sides in the axial direction of the carrier ring, a pair of side plates installed along the outer periphery of the rotor shaft;
The flow direction of the oil that is provided on the downstream side of the first bearing portion and the upstream side of the second bearing portion and that has passed between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft. A first oil guide configured to change and guide the oil;
An oil discharge port portion provided on the carrier ring or each of the side plates and configured to discharge the oil guided by the first oil guide portion to the outside ;
The region on the carrier ring side of the inner peripheral surface of each side plate extends in the circumferential direction along the side surface of the first bearing portion in at least a part of the extending range of the first bearing portion. A groove is formed,
Oil that has flowed into the groove through a gap between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft is guided, and the downstream end of the first bearing portion and the upstream of the second bearing portion A bearing device , further comprising a second oil guide portion configured to return the oil between the side end portions . The first oil guide part includes a scraper provided on the downstream side of the first bearing part,
Of the upstream end surface of the scraper, the regions at both ends in the axial direction are offset with respect to the axial direction so as to shift toward the downstream side in the rotational direction of the rotor shaft with increasing distance from the central portion in the axial width of the first bearing portion. The bearing device according to claim 1, wherein the bearing device is inclined. The first oil guide part includes an oil recovery box provided on the downstream side of the first bearing part,
The oil recovery box is
An oil inlet provided on an upper surface of the oil recovery box and opening in a gap between an inner peripheral surface of the first bearing portion and an outer peripheral surface of the rotor shaft;
An internal flow path provided to extend in the axial direction inside the oil recovery box, and communicated with the oil inlet;
An oil outlet provided on a side surface or a bottom surface of the oil recovery box, for communicating the internal flow path and the oil outlet;
The bearing device according to claim 1, comprising:   The oil drain port portion includes an opening formed in each of the side plates on the downstream side of the first bearing portion and on the upstream side of the second bearing portion. The bearing device according to any one of the above.   The oil drain port portion includes a hole provided in the carrier ring on the downstream side of the first bearing portion and on the upstream side of the second bearing portion. A bearing device according to claim 1. The said 1st oil guide part and the said 2nd oil guide part are formed of the two flow paths which cross | intersect each other through the different position in the radial direction of the said carrier ring, The 1st thru | or 5 characterized by the above-mentioned. The bearing apparatus as described in any one . The second oil guide portion includes a rectifying wall provided on each side plate so as to protrude toward the carrier ring in the groove,
The baffle wall is closer to the carrier ring as the rotation direction downstream side toward said rotor shaft, to claim 1, characterized in that it is inclined with respect to a direction perpendicular to the axial direction of the rotor shaft The bearing device according to any one of claims 6 to 6 . The second oil guide part includes an internal flow path provided inside the side plate so as to communicate between an oil inlet hole and an oil outlet hole respectively opened in the groove,
The oil inlet hole is provided to be located on a side of the first bearing portion,
The oil outlet holes, one of claims 1 to 7, characterized in that provided in the circumferential position between the upstream end portion of the second bearing portion and the downstream end of the first bearing part A bearing device according to claim 1. The groove in the circumferential direction range including the extended range of the first bearing and the second bearing portion of claim 1 to 8, characterized in that extending along the outer periphery of the rotor shaft The bearing apparatus as described in any one. The full width in the axial direction of each said side plate and is W, when the axial width of the groove was set to W _g, any one of claims 1 to 9, characterized in that satisfy 0.15 W ≦ W _g The bearing device described in 1. A fin provided on an inner peripheral surface of each of the side plates and extending along the outer periphery of the rotor shaft on both sides in the rotational direction of the rotor shaft across the downstream end portion of the first bearing portion; ,
The groove according to any one of claims 1 to 10, characterized in that it is formed by a recess which is also defined by the inner peripheral surface of the side plate of the carrier ring side of the fin and the fin Bearing device. The clearance between the inner peripheral surface of each of the side plates and the outer peripheral surface of the rotor shaft is such that at least a part of the circumferential region in the extending range of the first bearing portion is closer to the first bearing portion. upstream of the upstream edge, and, any one of claims 1 to 11, characterized in that narrower than at least a portion of the circumferential extent of the downstream side of the downstream end of the second bearing portion The bearing device according to one item. Bottom of the groove, the first compared to the outer peripheral surface of the bearing portion, a bearing apparatus according to any one of claims 1 to 12, characterized in that located inside in the radial direction of the carrier ring. A semi-annular bearing portion provided on the inner peripheral side of the upper half region of the carrier ring, and configured to hold down the rotor shaft from above;
Each of the first bearing portion and the second bearing portion is a pair of bearing pads provided on the inner peripheral side of the lower half region of the carrier ring and configured to support the rotor shaft from below. The bearing device according to any one of claims 1 to 13 , wherein the bearing device is a feature. With carrier ring,
A first bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring;
A second bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring on the downstream side in the rotational direction of the rotor shaft from the first bearing portion;
On both sides in the axial direction of the carrier ring, a pair of side plates installed along the outer periphery of the rotor shaft;
The flow direction of the oil that is provided on the downstream side of the first bearing portion and the upstream side of the second bearing portion and that has passed between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft. A first oil guide configured to change and guide the oil;
An oil discharge port portion provided on each of the side plates and configured to discharge the oil guided by the first oil guide portion to the outside;
For supplying oil between the inner peripheral surface of the second bearing portion and the outer peripheral surface of the rotor shaft, provided on the downstream side of the first oil guide portion and upstream of the second bearing portion. An oil supply nozzle,
The first oil guide part includes a scraper provided on the downstream side of the first bearing part,
Of the upstream end surface of the scraper, the regions at both ends in the axial direction are offset with respect to the axial direction so as to shift toward the downstream side in the rotational direction of the rotor shaft with increasing distance from the central portion in the axial width of the first bearing portion. Is inclined,
The oil drain port includes an opening provided on the inner periphery of each side plate,
The oil supply nozzle includes a space between the first bearing portion and the second bearing portion, an upstream space provided with the scraper and communicating with the opening portion, and the opening portion of each of the side plates. Extending in the axial direction so as to be divided into a radially inward projecting portion located on the downstream side, and a downstream space surrounded by the oil supply nozzle and the second bearing portion
A bearing device characterized by that. With carrier ring,
A first bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring;
A second bearing portion provided along the outer periphery of the rotor shaft on the inner peripheral side of the carrier ring on the downstream side in the rotational direction of the rotor shaft from the first bearing portion;
On both sides in the axial direction of the carrier ring, a pair of side plates installed along the outer periphery of the rotor shaft;
The flow direction of the oil that is provided on the downstream side of the first bearing portion and the upstream side of the second bearing portion and that has passed between the inner peripheral surface of the first bearing portion and the outer peripheral surface of the rotor shaft. A first oil guide configured to change and guide the oil;
An oil discharge port portion provided on the carrier ring or each of the side plates and configured to discharge the oil guided by the first oil guide portion to the outside;
The first oil guide part includes an oil recovery box provided on the downstream side of the first bearing part,
The oil recovery box is
An oil inlet provided on an upper surface of the oil recovery box and opening in a gap between an inner peripheral surface of the first bearing portion and an outer peripheral surface of the rotor shaft;
An internal flow path provided to extend in the axial direction inside the oil recovery box, and communicated with the oil inlet;
An oil outlet provided on a side surface or a bottom surface of the oil recovery box, for communicating the internal flow path and the oil outlet;
Including
The oil recovery box includes a pair of side wall portions provided so as to face each other with the internal flow path portion interposed therebetween in the circumferential direction,
The height of the first side wall portion on the upstream side in the rotational direction of the pair of side wall portions is lower than the height of the second side wall portion on the downstream side in the rotational direction among the pair of side wall portions.
A bearing device characterized by that. A bearing device according to any one of claims 1 to 16 ,
And a rotating shaft supported by the bearing device.

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