JP2016011698A - Tilting pad-type journal bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a tilting pad-type journal bearing capable of keeping lubrication and improving pad temperature reduction effect by oil supply, and suppressing increase of a pad temperature, without increasing an amount of oil supply compared with conventional ones.SOLUTION: A tilting pad 2 has a pair of guide holes 72 formed into the recessed shape at an upstream side in a rotating direction and axial end both sides of a rotating shaft on an inner peripheral face 2a of the pad 2, for taking a part of lubricant flowing into the upstream side in the rotating direction between the inner peripheral face 2a of the pad 2 and an outer peripheral face of the rotating shaft, and a pad internal hole 73 for making the lubricant guided through the guide hole 72 pass through the inside of the pad 2, and flow out to the external of the pad 2 at a downstream side in the rotating direction with respect to the guide hole 72.

Description

  The present invention relates to a tilting pad type journal bearing.

  Some rotary machines, such as a centrifugal compressor, are provided with a tilting pad type journal bearing for supporting the rotary shaft in the radial direction. Tilting pad type journal bearings have extremely high stability against self-excited vibration compared to arc bearings and elliptical bearings. This is because a tilting pad that supports the rotating shaft (hereinafter also simply referred to as “pad”) freely swings, and the oil film coupled spring term that destabilizes the vibration, that is, the rotating shaft, This is because the spring constant acting in the swinging direction becomes smaller.

  Such a tilting pad type journal bearing needs to cope with a high peripheral speed and a high surface pressure in response to a request for improving the efficiency of the rotating machine. However, the higher the peripheral speed and the higher the surface pressure, the more likely the seizure occurs on the sliding surface with the rotating shaft. Therefore, the supply of lubricating oil is important in order to reduce the temperature rise of the sliding surface.

  Lubricating oil supply methods for tilting pad type journal bearings can be broadly divided into two types: oil bath type and direct oil supply type. The direct oil supply type is superior to the oil bath type in that it has excellent pad cooling performance and can achieve a high peripheral speed with a small amount of oil supply.

Examples of conventional tilting pad type journal bearings classified as a direct oil supply type are described in Patent Documents 1 and 2, respectively.
The tilting pad type journal bearing described in Patent Document 1 has a structure in which grooves 190 and 191 are provided on a sliding surface of a direct oil supply type pad. By this groove, the lubricating oil on the sliding surface of the pad is collected in the center in the axial direction on the sliding surface of the pad, and the carryover oil to the next pad coming out from the trailing edge of the pad is intentionally increased to slide. The amount of oil flowing into the surface is increased. Thereby, the shortage of oil amount is prevented.

  The tilting pad type journal bearing described in Patent Document 2 is provided on the lateral side of the pad by providing a seal groove 47 on the outer edge of the side (axial direction of the rotating shaft) on the sliding surface of the directly lubricated pad. The oil is prevented from leaking. Further, by providing a step 41, a scraper 44, or the like, which is a structure for reducing carry-over oil, at the front edge and the rear edge in the circumferential direction on the sliding surface of the pad, carry-over of lubricating oil to the next pad is performed. We are trying to reduce it.

US Pat. No. 6,361,215 JP 2001-132737 A

  In the technique described in Patent Document 1, a groove is provided on the sliding surface of the pad to intentionally increase carry-over oil that has passed through the sliding surface of the pad and has reached a high temperature. Lubricating oil temperature and pad temperature are higher than those without the structure. Therefore, the thing of patent document 1 becomes low compared with the structure which does not provide a groove | channel on the relationship with the heat resistance of a bearing material, and there exists a possibility that it may become difficult to use at high peripheral speed. . Alternatively, there is a possibility that the amount of oil supplied to the pad must be increased in order to reduce the pad temperature under high peripheral speed operating conditions. Further, since the lubricating oil whose temperature has risen through the sliding surface passes through the groove provided on the sliding surface of the pad, it is considered that the effect of reducing the pad temperature by the groove cannot be expected.

  In the technique described in Patent Document 2, there is a possibility that the lubricating oil that flows into the seal groove for preventing leakage provided on the sliding surface of the pad is useful for reducing the pad temperature. However, since it is necessary to provide the seal groove on the sliding surface of the pad, the lubricating oil passing through the seal groove cannot effectively cool the region where the temperature of the pad is highest, and the effect of reducing the pad temperature by the seal groove is It is considered low.

  The present invention has been made in consideration of the above-described circumstances of the prior art. The purpose of the present invention is to maintain lubrication characteristics and to reduce the pad temperature by lubrication without increasing the amount of lubrication compared to the conventional art. It is an object of the present invention to provide a tilting pad type journal bearing capable of improving the pad temperature and suppressing an increase in pad temperature.

  In order to solve the above-described problems, a tilting pad type journal bearing according to the present invention includes a plurality of tilting pads that support a rotating shaft in a radial direction, and a bearing that accommodates the plurality of tilting pads in a swingable manner. A regulating structure that regulates a relative position in the circumferential direction between the tilting pad and the bearing housing, and the tilting pad is upstream in the rotational direction of the rotary shaft on the inner peripheral surface of the tilting pad. And a part of the lubricating oil flowing into the upstream side in the rotational direction between the inner peripheral surface of the tilting pad and the outer peripheral surface of the rotary shaft. A pair of guide holes to be taken into the interior and lubricating oil guided through the guide holes through the inside of the tilting pad and then the guide And having a pad internal bore to flow out of the tilting pad at the downstream side in the rotational direction of the rotary shaft than.

  According to the present invention, a tilting pad type journal capable of maintaining the lubrication characteristics and improving the pad temperature reduction effect by supplying oil without increasing the amount of oil supply compared to the conventional art, and realizing the suppression of the increase in pad temperature. A bearing can be provided.

1 is an axial cross-sectional view of a tilting pad type journal bearing according to a first embodiment of the present invention. It is sectional drawing which follows the AA line of FIG. 3A is a plan view of the tilting pad in the tilting pad type journal bearing shown in FIG. 1, FIG. 3B is a cross-sectional view taken along line BB in FIG. 3A, and FIG. (c) is sectional drawing which follows the CC line of FIG.3 (b). It is a figure which shows the relationship between the circumferential direction position of a tilting pad, and the pad temperature of the sliding surface vicinity. FIG. 5A to FIG. 5D are plan views showing examples of tilting pads in the tilting pad type journal bearing according to the second embodiment of the present invention. FIG. 6A is a plan view of a tilting pad in a tilting pad type journal bearing according to the third embodiment of the present invention, and FIG. 6B is a cross-sectional view taken along line DD in FIG. FIG. 6 and FIG. 6C are cross-sectional views taken along the line EE of FIG. FIGS. 7A to 7D are plan views showing examples of the tilting pad in the tilting pad type journal bearing according to the fourth embodiment of the present invention. FIG. 8A is a plan view of a tilting pad in a tilting pad type journal bearing according to a fifth embodiment of the present invention, and FIG. 8B is a cross section taken along line FF in FIG. FIG. 8 and FIG. 8C are views as seen from G in FIG. It is an axis perpendicular sectional view of a tilting pad type journal bearing concerning a 6th embodiment of the present invention. It is sectional drawing which follows the HH line of FIG. FIG. 10 is a cross-sectional view perpendicular to the axis showing an enlarged periphery of the tilting pad in the tilting pad type journal bearing shown in FIG. 9. 12A is a plan view of the tilting pad in the tilting pad type journal bearing shown in FIG. 9, FIG. 12B is a cross-sectional view taken along the line II of FIG. 12A, and FIG. c) is a cross-sectional view taken along line JJ of FIG. 13A is a view of the nozzle in the tilting pad type journal bearing shown in FIGS. 9 to 11 as viewed from the inside in the radial direction, and FIG. 13B is along the line KK in FIG. 13A. It is sectional drawing. It is an axis perpendicular sectional view of a tilting pad type journal bearing concerning a 7th embodiment of the present invention. FIG. 15A is a view of the nozzle in the tilting pad type journal bearing shown in FIG. 14 as viewed from the inside in the radial direction, and FIG. 15B is a cross-sectional view taken along line LL in FIG. is there. It is an axis perpendicular cross-sectional view which expands and shows the tilting pad periphery in the tilting pad type journal bearing which concerns on 8th Embodiment of this invention. It is an axis perpendicular cross-sectional view which expands and shows the tilting pad periphery in the tilting pad type journal bearing which concerns on 9th Embodiment of this invention. FIG. 18A is a plan view of a tilting pad in a tilting pad type journal bearing according to the tenth embodiment of the present invention, and FIG. 18B is a cross-sectional view taken along line MM in FIG. FIG.

Embodiments of the present invention will be described in detail with reference to the drawings as appropriate.
Note that, in the drawings shown below, the same members or corresponding members are denoted by the same reference numerals, and redundant description is omitted as appropriate. In addition, the size and shape of the member may be schematically represented by being modified or exaggerated for convenience of explanation. For example, in FIG. 1 and the like, the gap between the shaft and the pad is drawn in a size different from the actual size for convenience of explanation.

[First Embodiment]
First, a first embodiment of the present invention will be described with reference to FIGS.
The tilting pad type journal bearing 20 according to the first embodiment of the present invention is suitable for supporting the rotating shaft of a rotating machine that operates at a high speed such as a multistage centrifugal compressor.

  FIG. 1 is a cross-sectional view perpendicular to the axis of a tilting pad type journal bearing according to a first embodiment of the present invention. 2 is a cross-sectional view taken along line AA in FIG.

  As shown in FIGS. 1 to 2, the tilting pad type journal bearing 20 according to the first embodiment of the present invention supports a rotating shaft 1 that rotates at a high speed in a rotating direction 10 in a radial direction of the rotating shaft 1. A plurality (five in FIG. 1) of tilting pads (also simply referred to as “pads”) 2 are provided. The plurality of pads 2 are housed in a cylindrical bearing housing 5 so as to be swingable. Here, the bearing housing 5 includes a first housing 51 and a second housing 52 disposed inside the first housing 51.

  A convex pivot 12 is formed on the outer peripheral surface 2b of the pad 2 so as to support the pad 2 in a swingable manner. The pads 2 are arranged at equal intervals in the circumferential direction in the bearing housing 5 so that the surface of the pivot 12 contacts the inner circumferential surface 5a of the bearing housing 5.

  The pad 2 includes an oil supply groove structure 7 (see also FIGS. 2 and 3) for storing lubricating oil supplied between the inner peripheral surface 2 a of the pad 2 and the outer peripheral surface 1 a of the rotary shaft 1, and the rotary shaft 1 in the pad 2. And an introduction hole 31 for introducing lubricating oil.

  The pad 2 includes an oil supply pipe 3 that connects the pad 2 and the bearing housing 5 and follows the swing of the pad 2. The introduction hole 31 is formed inside the oil supply pipe 3 and passes through the inside of the pad 2 in the radial direction and opens at the groove bottom of the oil supply groove structure 7. The oil supply pipe 3 has a substantially cylindrical shape and is provided so as to protrude outward in the radial direction of the rotary shaft 1 from the outer peripheral surface 2 b of the pad 2, and a tip end portion to which the O-ring 3 a is attached is formed in the bearing housing 5. Inserted into the through-hole. The oil supply pipe 3 is formed integrally with the pad 2 here, but is not limited to this. For example, the oil supply pipe 3 may be formed separately from the pad 2 and attached to the pad 2 by screw fastening or the like. .

  A pair of end plates 16 (see FIG. 2) having a substantially hollow disk shape are fixed to both end surfaces in the axial direction of the bearing housing 5 by screw fastening or the like. The pad 2 is held in the axial direction by the pair of end plates 16.

  The pad 2 is generally shaped by cutting a cylinder along the radial direction and dividing it in the circumferential direction, and the inner peripheral surface 2a serving as a sliding surface with the rotating shaft 1 is made of a bearing material such as white metal. Is formed.

3A is a plan view of the tilting pad in the tilting pad type journal bearing shown in FIG. 1, FIG. 3B is a cross-sectional view taken along line BB in FIG. 3A, and FIG. (c) is sectional drawing which follows the CC line of FIG.3 (b).
3 illustrates the lowermost pad in the tilting pad type journal bearing 20 shown in FIG. 1, and the other pads have the same shape (FIGS. 5 to 8, 11, and 12). The same applies to FIGS. 16 to 18).

  As shown in FIG. 3, the pad 2 has a circumferential front edge side (rotational direction of the rotary shaft 1) between the inner peripheral surface 2 a of the pad 2 and the outer peripheral surface 1 a of the rotary shaft 1 (see FIG. 1, the same applies hereinafter). It has a pair of guide holes 72 for taking in part of the lubricating oil flowing into the upstream side. The pair of guide holes 72 are formed in a concave shape on the circumferential front edge side on the inner circumferential surface 2 a of the pad 2 and on both sides of the axial end portion of the rotary shaft 1.

  The pad 2 is a pad internal hole through which lubricating oil guided through the guide hole 72 passes through the inside of the pad 2 and then flows out of the pad 2 on the downstream side of the guide hole 72 in the rotation direction of the rotary shaft 1. 73. An outlet 77 that is an opening end of the pad inner hole 73 opposite to the guide hole 72 is formed on the rear end surface (downstream end surface) 2c of the pad 2. An inlet 78 that is an open end facing the guide hole 72 of the pad inner hole 73 is formed on the inner end surface 79 on the downstream side in the rotation direction of the rotation shaft 1 of the guide hole 72. However, the inlet 78 of the pad inner hole 73 may be formed so as to open to another inner surface such as the bottom surface of the guide hole 72.

  The oil supply groove structure 7 is formed in a concave shape between the front end side in the circumferential direction on the inner peripheral surface 2 a of the pad 2 and between the pair of guide holes 72, and has a rectangular shape extending in the axial direction of the rotary shaft 1. A pair of wall portions 71 that divide the oil supply groove structure 7 and the guide hole 72 are provided on both sides of the axial end portion of the rotating shaft 1 of the oil supply groove structure 7.

  The gap between the wall 71 and the rotary shaft 1 is set larger than the gap between the inner peripheral surface 2 a of the pad 2 and the rotary shaft 1. In this way, by raising a part of the lubricating oil in the oil supply groove structure 7 beyond the wall portion 71, it is possible to suppress an increase in the temperature of the lubricating oil in the oil supply groove structure 7.

  The pivot 12 is formed to extend in the axial direction on the outer peripheral surface 2b of the pad 2, and the surface of the pivot 12 is a convex surface 12a having a substantially cylindrical surface shape. Here, the radius of curvature of the convex surface 12 a is smaller than the radius of the inner peripheral surface 5 a of the bearing housing 5. Therefore, the pad 2 can swing around the pivot 12 while being accommodated in the bearing housing 5. Further, an engagement hole 12b is formed in the center of the convex surface 12a of the pivot 12 to engage with the cylindrical pin 4 (see FIG. 1).

  As shown in FIGS. 1 to 3, the tilting pad type journal bearing 20 includes a restriction structure that restricts the relative position in the circumferential direction between the pad 2 and the bearing housing 5. In the first embodiment, the restriction structure includes a pin 4 fixed to the bearing housing 5 and an engagement hole 12b formed in the pivot 12 and into which the pin 4 is inserted and engaged. Specifically, the pin 4 is fixed to a through hole 5c provided in the bearing housing 5 by press-fitting or the like, and its tip is inserted into and engaged with the engagement hole 12b of the pivot 12 of the pad 2. Thereby, the positional relationship in the circumferential direction between the pad 2 and the bearing housing 5 is regulated.

  Next, the operation of the tilting pad type journal bearing 20 configured as described above will be described.

  As shown in FIG. 3, the lubricating oil 6 supplied through the introduction hole 31 accumulates in the oil supply groove structure 7, and this lubricating oil 6 is rotated by the rotating shaft 1 to rotate the rotating shaft 1 that becomes a sliding surface. It is drawn between the outer peripheral surface 1 a and the inner peripheral surface 2 a of the pad 2. The lubricating oil 6a that has flowed into the sliding surface of the rotating shaft 1 and the pad 2 forms an oil film on the sliding surface, thereby preventing direct contact between the rotating shaft 1 and the pad 2, and Bear the acting load.

  On the other hand, the lubricating oil 6 b that is not drawn into the sliding surface between the rotary shaft 1 and the pad 2 passes between the rotary shaft 1 and the wall portion 71 and enters the guide hole 72. The lubricating oil 6 c passing through the pad inner hole 73 through the guide hole 72 reduces the internal temperature of the pad 2. That is, it is possible to reduce the internal temperature of the pad 2 with the excess lubricating oil 6c while maintaining the lubricating oil 6a necessary for forming the oil film on the sliding surface of the rotating shaft 1 and the pad 2.

  Moreover, the temperature of the lubricating oil 6a drawn into the sliding surface of the rotating shaft 1 and the pad 2 and the temperature of the lubricating oil 6c passing through the pad inner hole 7c are substantially the same relatively low temperature. For this reason, it is possible to cool from the inside of the pad 2 with the lubricating oil 6 c having the same temperature as the lubricating oil 6 a drawn into the sliding surface of the rotating shaft 1 and the pad 2. That is, it can cool simultaneously from the sliding surface and the inside of the pad 2, and the pad temperature reduction effect by oil supply can be heightened.

  FIG. 4 is a diagram showing the relationship between the circumferential position of the tilting pad and the pad temperature near the sliding surface. In FIG. 4, the pad circumferential position indicates the circumferential position from the downstream end edge 74 (see FIG. 3B) of the oil supply groove structure 7 toward the downstream side. This is expressed as a ratio (%) of the circumferential distance to the corresponding position with respect to the circumferential distance from the downstream end edge 74 to the pad trailing edge 75 (see FIG. 3B).

  As shown in FIG. 4, the pad temperature in the pad 2 into which newly supplied lubricating oil flows is low on the upstream side in the rotational direction of the rotary shaft 1 and increases as it goes downstream, and the pad circumferential position is 75%. It is almost constant in the vicinity. In the first embodiment, a relatively low temperature lubricating oil is taken into the guide hole 72 formed on the upstream side in the rotation direction on the inner peripheral surface 2a of the pad 2 and passes near a region of the pad 2 where the temperature is high. This can increase the pad temperature reduction effect.

  As described above, in the first embodiment, the pad 2 is formed in a concave shape on the inner circumferential surface 2a of the pad 2 on the upstream side in the rotational direction of the rotary shaft 1 and on both sides in the axial direction. And a pair of guide holes 72 for taking in a part of the lubricant flowing into the upstream in the rotational direction between the outer periphery 1a of the rotary shaft 1 and the lubricant guided through the guide holes 72 inside the pad 2 And a pad inner hole 73 that flows out of the pad 2 on the downstream side of the guide hole 72 in the rotation direction.

  According to such a configuration, the tilting pad can maintain the lubrication characteristics and improve the pad temperature reduction effect by supplying the oil without increasing the amount of oil supply compared to the conventional one, and can realize the suppression of the pad temperature rise. A die journal bearing 20 can be provided.

  Further, the pad 2 includes an oil supply groove structure 7 for storing lubricating oil supplied between the inner peripheral surface 2 a of the pad 2 and the outer peripheral surface 1 a of the rotary shaft 1, and an inside of the oil supply groove structure 7 from the radially outer side of the pad 2. And a pair of wall portions 71 provided on both sides of the axial end portion of the oil supply groove structure 7 and partitioning the oil supply groove structure 7 and the guide hole 72. .

  According to such a configuration, since the lubricating oil stored in the oil supply groove structure 7 through the introduction hole 31 of the pad 2 is directly supplied to the sliding surface of the rotating shaft 1 and the pad 2, the axial direction of the supplied lubricating oil Leakage of the sliding surface is suppressed, and the temperature rise of the sliding surface can be reduced with a small amount of oil supply. Further, the lubricating oil that does not enter the sliding surface of the rotating shaft 1 and the pad 2 passes between the rotating shaft 1 and the wall portion 71 and passes through the pad inner hole 73 via the guide hole 72, so The temperature can be reduced.

[Second Embodiment]
Next, referring to FIG. 5, the second embodiment of the present invention will be described with a focus on differences from the first embodiment described above, and description of common points will be omitted as appropriate.
FIG. 5A to FIG. 5D are plan views showing examples of tilting pads in the tilting pad type journal bearing according to the second embodiment of the present invention.

  As shown in FIGS. 5A to 5D, in the second embodiment, the path of the pad inner hole 73a of the pad 2 is changed with respect to the pad inner hole 73 in the first embodiment. The second embodiment is different from the first embodiment in that an intersecting portion 76 where a pair of pad inner holes 73a communicating with the guide holes 72 intersect is formed. In the example shown in FIG. 5D, the outlet 77 that is the opening end of the pad inner hole 73a opposite to the guide hole 72 is formed on the side end face (axial end face) 2d of the pad 2.

  According to this second embodiment, the intersection 76 of the pad inner hole 73a where the flow is the most turbulent and the heat transfer coefficient is increased is effectively cooled in the region where the temperature of the sliding surface is predicted to be highest. It can be arranged at a position where it can be. Thereby, the heat transfer rate from the pad 2 to the lubricating oil can be further increased, and the pad temperature reduction effect can be further increased.

[Third Embodiment]
Next, with reference to FIG. 6, the third embodiment of the present invention will be described with a focus on differences from the first embodiment described above, and description of common points will be omitted as appropriate.
FIG. 6A is a plan view of a tilting pad in a tilting pad type journal bearing according to the third embodiment of the present invention, and FIG. 6B is a cross-sectional view taken along line DD in FIG. FIG. 6 and FIG. 6C are cross-sectional views taken along the line EE of FIG.

  As shown in FIG. 6, in the third embodiment, the circumferential dimension of the guide hole 72a (the rotational direction of the rotary shaft 1) is the same as the axial dimension of the rotary shaft 1 of the guide hole 72a and the guide hole 72a. This is different from the first embodiment in that it is larger than any of the dimensions in the depth direction (radial direction of the rotating shaft 1). That is, in 3rd Embodiment, the area | region of the guide hole 72a connected with the pad internal hole 73 of the pad 2 is expanded rather than 1st Embodiment to the circumferential direction downstream side.

  According to the third embodiment, the guide hole 72a has not only the effect of guiding the lubricating oil 6b passing between the rotary shaft 1 and the wall portion 71 to the pad internal hole 73, but also the lubricating oil 6e in the guide hole 72a. The effect of generating a flow in the rotational direction as the rotary shaft 1 rotates is exhibited. According to this flow, the lubricating oil 6e in the guide hole 72a flows into the pad internal hole 73 from the inlet 78, so that the lubricating oil 6c passing through the pad internal hole 73 is discharged without stagnation. Furthermore, since the flow velocity of the lubricating oil 6c increases and becomes more turbulent, the heat transfer rate from the pad 2 to the lubricating oil 6c can be increased.

  The inlet 78 which is an opening end facing the guide hole 72 of the pad inner hole 73 is formed on the inner end surface 79 on the downstream side in the rotation direction of the rotation shaft 1 of the guide hole 72 as in the first embodiment. The lubricating oil 6e in the guide hole 72a can flow more smoothly into the pad inner hole 73 from the inlet 78 according to the flow in the rotation direction. However, the inlet 78 of the pad inner hole 73 may be formed so as to open to another inner surface such as a bottom surface on the downstream side in the rotation direction of the guide hole 72.

  Further, since the pressure gradually increases along the rotation direction of the rotating shaft 1 on the sliding surface of the rotating shaft 1 and the pad 2, the pad pressure is included in the lubricating oil 6 a entering the sliding surface from the oil supply groove structure 7. Lubricating oil 6d that comes off to the side (side) is present on the front side in the circumferential direction from the maximum position, that is, before passing through the region where the temperature is high. Therefore, by guiding the lubricating oil 6d to the pad internal hole 73 through the guide hole 72a, it becomes possible to reduce the pad temperature with more lubricating oil.

  Further, it is desirable that the inner end surface 79 on the downstream side in the rotation direction of the rotation shaft 1 of the guide hole 72a is located on the upstream side of the center position in the rotation direction of the rotation shaft 1 on the inner peripheral surface 2a of the pad 2. In this way, relatively low temperature lubricating oil is taken into the guide hole 72a from the upstream side in the rotational direction on the inner peripheral surface 2a of the pad 2, and the pad inner hole 73 is near the region where the temperature of the pad 2 is increased. Can be passed, and the pad temperature reduction effect is further enhanced.

[Fourth Embodiment]
Next, with reference to FIG. 7, the fourth embodiment of the present invention will be described with a focus on differences from the third embodiment described above, and description of common points will be omitted as appropriate.
FIGS. 7A to 7D are plan views showing examples of the tilting pad in the tilting pad type journal bearing according to the fourth embodiment of the present invention.

  As shown in FIGS. 7A to 7D, in the fourth embodiment, the path of the pad internal hole 73a of the pad 2 is changed with respect to the pad internal hole 73 in the third embodiment. The third embodiment is different from the third embodiment in that a crossing portion 76 where a pair of pad inner holes 73a communicating with the guide holes 72a intersect is formed. In the example shown in FIG. 7D, the outlet 77 that is the opening end of the pad inner hole 73a opposite to the guide hole 72a is formed on the side end face (axial end face) 2d of the pad 2.

  According to the fourth embodiment, similarly to the second embodiment described above, the intersecting portion 76 of the pad inner hole 73a where the flow is the most turbulent and the heat transfer rate is increased is the highest temperature of the sliding surface. It is possible to arrange the region predicted to be at a position where it can be effectively cooled. Thereby, the heat transfer rate from the pad 2 to the lubricating oil can be further increased, and the pad temperature reduction effect can be further increased.

[Fifth Embodiment]
Next, with reference to FIG. 8, the fifth embodiment of the present invention will be described with a focus on differences from the third embodiment described above, and descriptions of common points will be omitted as appropriate.
FIG. 8A is a plan view of a tilting pad in a tilting pad type journal bearing according to a fifth embodiment of the present invention, and FIG. 8B is a cross section taken along line FF in FIG. FIG. 8 and FIG. 8C are views as seen from G in FIG.

  As shown in FIG. 8, the fifth embodiment is an oiling type tilting pad type journal bearing in which the space between the rotating shaft and the bearing is filled with lubricating oil. This is different from the third embodiment which is a pad type journal bearing.

  The pad 2 of the fifth embodiment has a guide hole 72a and a pad internal hole 73 whose region is enlarged on the downstream side in the circumferential direction, similarly to the one shown in the third embodiment. Note that the upstream side in the circumferential direction of the guide hole 72a opens to the front end surface (upstream end surface) 2e of the pad 2. In the case of the oil supply system of the fifth embodiment, since the entire pad 2 is filled with the lubricating oil, it is not necessary to provide the oil supply groove structure 7 in the pad 2 as in the first embodiment, for example.

  In the fifth embodiment, the lubricating oil is drawn into the sliding surfaces of the rotating shaft 1 and the pad 2 by the rotation of the rotating shaft 1. The lubricating oil 6a flowing into the sliding surface of the rotating shaft 1 and the pad 2 forms an oil film on the sliding surface, thereby preventing direct contact between the rotating shaft 1 and the pad 2 and Bear the acting load.

  On the other hand, the lubricating oil 6b that is not drawn into the sliding surface of the rotating shaft 1 and the pad 2 is guided to the pad internal hole 73 through the guide hole 72a, and the lubricating oil 6c that passes through the pad internal hole 73 is The internal temperature can be reduced. Further, the lubricating oil 6e in the guide hole 72a generates a flow in the rotating direction as the rotating shaft 1 rotates. According to this flow, the lubricating oil 6e in the guide hole 72a flows into the pad internal hole 73 from the inlet 78, so that the lubricating oil 6c passing through the pad internal hole 73 is discharged without stagnation. Furthermore, since the flow velocity of the lubricating oil 6c increases and becomes more turbulent, the heat transfer rate from the pad 2 to the lubricating oil 6c can be increased as shown in the third embodiment.

  Further, since the pressure gradually increases along the rotation direction of the rotating shaft 1 on the sliding surface of the rotating shaft 1 and the pad 2, the pad pressure is included in the lubricating oil 6 a entering the sliding surface from the oil supply groove structure 7. Lubricating oil 6d that comes off to the side is present on the front edge side in the circumferential direction from the maximum position, that is, before passing through a region where the temperature is high. Therefore, by guiding the lubricating oil 6d to the pad internal hole 73 through the guide hole 72a, it becomes possible to reduce the pad temperature with more lubricating oil.

  As long as the pad 2 of the fifth embodiment is used, an oil supply method is used in which the space between the rotating shaft and the bearing is filled with lubricating oil, but the method of supplying the lubricating oil between the rotating shaft and the bearing is particularly limited. Is not to be done.

[Sixth Embodiment]
Next, with reference to FIGS. 9 to 13, the sixth embodiment of the present invention will be described with a focus on differences from the third embodiment described above, and descriptions of common points will be omitted as appropriate.
FIG. 9 is a cross-sectional view perpendicular to the axis of a tilting pad type journal bearing according to a sixth embodiment of the present invention. 10 is a cross-sectional view taken along line HH in FIG. FIG. 11 is an enlarged cross-sectional view perpendicular to the axis showing the periphery of the tilting pad in the tilting pad type journal bearing shown in FIG. 12A is a plan view of the tilting pad in the tilting pad type journal bearing shown in FIG. 9, FIG. 12B is a cross-sectional view taken along the line II of FIG. 12A, and FIG. c) is a cross-sectional view taken along line JJ of FIG. 13A is a view of the nozzle in the tilting pad type journal bearing shown in FIGS. 9 to 11 as viewed from the inside in the radial direction, and FIG. 13B is along the line KK in FIG. 13A. It is sectional drawing.

  As shown in FIGS. 9 to 10, the tilting pad type journal bearing 20 a according to the sixth embodiment of the present invention supports the rotating shaft 1 rotating in the rotating direction 10 at a high speed in the radial direction of the rotating shaft 1. Plural (five in FIG. 9) pads 2 are provided. The plurality of pads 2 are housed in a cylindrical bearing housing 5 so as to be swingable.

  Further, the tilting pad type journal bearing 20a includes a plurality (five in FIG. 9) of nozzles 9 for supplying lubricating oil between the inner peripheral surface 2a of the plurality of pads 2 and the outer peripheral surface 1a of the rotating shaft 1. I have.

  As shown in FIGS. 11 to 12, the pad 2 has a through-hole 11 having a substantially rectangular cross section penetrating from the outer peripheral surface 2 b to the inner peripheral surface 2 a of the pad 2 in order to arrange the nozzle 9 therein. The through hole 11 is formed on the circumferential front edge side of the pad 2 (upstream side in the rotational direction of the rotating shaft 1).

  As shown in FIG. 11, the nozzle 9 passes through the inside of the through hole 11 of the pad 2, and its base end is fixed to a through hole 5 b provided in the bearing housing 5 by screw fastening or the like, and its distal end Is configured to face the outer peripheral surface 1 a of the rotating shaft 1.

  A gap 8 is formed between the nozzle 9 and the inner surface of the through-hole 11 of the pad 2 to avoid contact between the nozzle 9 and the pad 2 even if the pad 2 swings around the pivot 12. .

  As shown in FIG. 12, the pad 2 has a guide hole 72a and a pad internal hole 73 whose region is enlarged on the downstream side in the circumferential direction, as in the third embodiment. Note that the upstream side in the circumferential direction of the guide hole 72 a opens to the inner surface of the through hole 11.

  Further, the tilting pad type journal bearing 20a is provided with a restricting structure for restricting the relative position in the circumferential direction between the pad 2 and the bearing housing 5 as in the third embodiment. And a pin 4 that is formed on the pivot 12 and an engagement hole 12b into which the pin 4 is inserted and engaged. Thereby, the positional relationship in the circumferential direction between the pad 2 and the bearing housing 5 is restricted, and the gap 8 between the nozzle 9 and the pad 2 can be more reliably held. The pin 4 works so as to restrict the movement of the pad 2 in the circumferential direction on the inner peripheral surface of the bearing housing 5, but does not restrain the movement (swing) of the pad 2 tilting.

  Usually, the radial gap (pin) between the pin 4 and the engagement hole 12b is smaller than the circumferential gap 8 between the nozzle 9 and the inner surface of the through hole 11 of the pad 2, and the pad 2 is larger than the radial gap (bearing gap) between the inner circumferential surface 2a of the rotary shaft 1 and the outer circumferential surface 1a of the rotary shaft 1. With such a configuration, free swinging of the pad 2 and avoidance of contact between the nozzle 9 and the pad 2 are further ensured. In addition, in FIG. 11 etc., the above-mentioned three gaps are drawn in a size different from the actual size for convenience of explanation.

  As shown in FIG. 13, the nozzle 9 has a rectangular plate shape. In the sixth embodiment, a plurality of jet outlets 9 a for jetting lubricating oil are provided at the tip of the nozzle 9. Here, the plurality of jet nozzles 9 a are formed in a line in the axial direction of the rotary shaft 1. The opening end of the jet outlet 9a of the nozzle 9 is disposed close to the outer peripheral surface 1a of the rotating shaft 1 within a range that does not protrude to the inner diameter side of the inner peripheral surface 2a of the pad 2 (see FIG. 11). On the other hand, an inlet 9b for introducing lubricating oil is provided at the base end portion of the nozzle 9, and the lubricating oil introduced from the inlet 9b is collected in the distribution chamber 9c and then into the plurality of jets 9a. It is designed to be sent stably.

  Here, the nozzle 9 is formed by joining two parts divided in the vertical direction of FIG. 13B in the vicinity of the center of the distribution chamber 9c in FIG. 13B, but is not limited thereto. For example, it may be formed by joining two parts divided in the thickness direction at the center of the nozzle 9 in FIG. 13A in the thickness direction.

  Next, the operation of the tilting pad type journal bearing 20a configured as described above will be described.

  As shown in FIG. 11, the lubricating oil 6 a supplied from the nozzle 9 in which a plurality of jets 9 a (see FIG. 13) is formed is formed between the inner peripheral surface 2 a of the pad 2 that is a sliding surface and the rotating shaft 1. It is directly sprayed (sprayed) between the outer peripheral surface 1a and supplied. Since the nozzle 9 is disposed so as to pass through the inside of the through hole 11 of the pad 2 and is surrounded by the pad 2, the lubricating oil 6 a ejected from the ejection port 9 a is in the axial direction of the rotary shaft 1. Without being leaked, it is pulled in toward the sliding surface.

  Note that the tilting pad type journal bearing 20a of the sixth embodiment supplies oil directly to the sliding surfaces of the rotating shaft 1 and the pad 2, but the outer peripheral surface 1a of the rotating shaft 1 and the end plate 16 (see FIG. 10). ) Can be used even in an oil supply system in which the space between the rotary shaft and the bearing is filled with lubricating oil.

  As shown in FIG. 12, the lubricating oil is drawn into the sliding surface between the rotating shaft 1 and the pad 2 by the rotation of the rotating shaft 1. The lubricating oil 6a that has flowed into the sliding surface of the rotating shaft 1 and the pad 2 forms an oil film on the sliding surface, thereby preventing direct contact between the rotating shaft 1 and the pad 2, and Bear the acting load.

  On the other hand, the lubricating oil 6b that is not drawn into the sliding surface of the rotating shaft 1 and the pad 2 is guided to the pad internal hole 73 through the guide hole 72a, and the lubricating oil 6c that passes through the pad internal hole 73 is The internal temperature can be reduced. That is, it is possible to reduce the internal temperature of the pad 2 with the excess lubricating oil 6c while maintaining the lubricating oil 6a necessary for forming the oil film on the sliding surface of the rotating shaft 1 and the pad 2.

  In addition, the guide hole 72a exhibits not only the effect of guiding the lubricant to the pad inner hole 73, but also the effect of causing the lubricant 6e in the guide hole 72a to generate a flow in the rotational direction as the rotary shaft 1 rotates. . According to this flow, the lubricating oil 6e in the guide hole 72a flows into the pad internal hole 73 from the inlet 78, so that the lubricating oil 6c passing through the pad internal hole 73 is discharged without stagnation. Furthermore, since the flow velocity of the lubricating oil 6c increases and becomes more turbulent, the heat transfer rate from the pad 2 to the lubricating oil 6c can be increased.

  Further, since the pressure gradually increases along the rotation direction of the rotating shaft 1 on the sliding surface of the rotating shaft 1 and the pad 2, the pad pressure is included in the lubricating oil 6 a entering the sliding surface from the oil supply groove structure 7. Lubricating oil 6d that comes off to the side is present on the front edge side in the circumferential direction from the maximum position, that is, before passing through a region where the temperature is high. Therefore, by guiding the lubricating oil 6d to the pad internal hole 73 through the guide hole 72a, it becomes possible to reduce the pad temperature with more lubricating oil.

  Further, since the gap 8 is formed so that the nozzle 9 and the pad 2 do not come into contact with each other even when the pad 2 swings, the pad 2 can be freely moved without being suppressed. As a result, the destabilizing force against vibration can be reduced, so that the limit of occurrence of self-excited vibration (limit of stability against vibration) is improved, and the rotating machine rotates the rotating shaft to a higher rotational speed. Driving.

  Moreover, even if the oil supply to the nozzle 9 is stopped due to a failure or the like, if the oil supply method fills the space between the rotary shaft and the bearing with the lubricating oil, it is between the nozzle 9 and the inner surface of the through hole 11 of the pad 2. Through the gap 8, the rotary shaft 1 is drawn into the sliding surface of the rotary shaft 1 and the pad 2 by the rotation of the rotary shaft 1 and supplied for a predetermined time. That is, even when the oil supply to the nozzle 9 is stopped for some reason, it is possible to supply the lubricating oil to the sliding surface through the gap 8 for a certain period of time.

  As described above, in the sixth embodiment, the pad 2 has the through hole 11 penetrating from the outer peripheral surface 2 b to the inner peripheral surface 2 a of the pad 2, and the nozzle 9 passes through the through hole 11 of the pad 2. The base end portion is fixed to the bearing housing 5, and the tip end portion is configured to face the outer peripheral surface 1 a of the rotating shaft 1. A gap 8 is formed between the nozzle 9 and the inner surface of the through hole 11 of the pad 2 to avoid contact between the nozzle 9 and the pad 2 even if the pad 2 swings.

  According to the sixth embodiment, in the tilting pad type journal bearing 20a, the lubricating oil is directly supplied from the nozzle 9 passing through the through hole 11 of the pad 2 to the sliding surface of the rotary shaft 1 and the pad 2. Therefore, leakage of the supplied lubricating oil in the axial direction is suppressed, and the temperature rise of the sliding surface can be reduced with a small amount of oil supply. Further, the lubricating oil that does not enter the sliding surface between the rotating shaft 1 and the pad 2 passes through the pad inner hole 73 through the guide hole 72a, and the internal temperature of the pad 2 can be reduced. Further, the effect of not suppressing the swing of the pad 2 due to the formation of the gap 8 can reduce the destabilizing force against vibration and improve the stability limit against vibration. Moreover, even when the oil supply to the nozzle 9 is stopped for some reason, if the oil supply system fills the space between the rotating shaft and the bearing with the lubricant oil, the lubricant oil can be supplied to the sliding surface through the gap 8 for a certain period of time. Secured. That is, it is possible to achieve a reduction in the amount of oil supply and a suppression of the increase in the oil film temperature while maintaining a stabilization function against vibration.

  In the sixth embodiment, the nozzle 9 is provided with a jet port 9 a that jets the lubricating oil at the tip portion. According to such a configuration, the lubricating oil introduced into the nozzle 9 from the introduction port 9 b can be directly jetted and supplied to the sliding surfaces of the rotating shaft 1 and the pad 2.

[Seventh Embodiment]
Next, with reference to FIGS. 14 to 15, the seventh embodiment of the present invention will be described with a focus on differences from the above-described sixth embodiment, and description of common points will be omitted as appropriate.
FIG. 14 is a cross-sectional view perpendicular to the axis of a tilting pad type journal bearing according to a seventh embodiment of the present invention. FIG. 15A is a view of the nozzle in the tilting pad type journal bearing shown in FIG. 14 as viewed from the inside in the radial direction, and FIG. 15B is a cross-sectional view taken along line LL in FIG. is there.

  As shown in FIGS. 14 to 15, the tilting pad type journal bearing 20 b according to the seventh embodiment is different from the sixth embodiment in that the nozzle 17 is different from the nozzle 9 of the sixth embodiment. The others are the same.

  In 7th Embodiment, the oil storage part 17a provided with the opening which faces the outer peripheral surface 1a of the rotating shaft 1 in the front-end | tip part of the nozzle 17 and which can store lubricating oil is provided. The open end of the oil reservoir 17a of the nozzle 17 is disposed close to the outer peripheral surface 1a of the rotating shaft 1 within a range that does not protrude to the inner diameter side of the inner peripheral surface 2a of the pad 2. An inlet 17b for introducing lubricating oil is provided at the base end of the nozzle 17, and the lubricating oil introduced from the inlet 17b is stored in the oil reservoir 17a.

  According to the seventh embodiment, the lubricating oil introduced into the nozzle 17 from the introduction port 17b can be stored in the oil storage portion 17a in the vicinity of the sliding surface of the rotary shaft 1 and the pad 2, and this oil storage Lubricating oil can be supplied to the sliding surface of the rotating shaft 1 and the pad 2 from the part 17a. Therefore, according to the seventh embodiment, in addition to being able to achieve the same operational effects as the sixth embodiment, it is not necessary to adjust the hydraulic pressure as in the case of the nozzle 9 of the sixth embodiment, and the shape is further improved. The nozzle 17 can have a simple structure, and the cost can be reduced.

[Eighth Embodiment]
Next, with reference to FIG. 16, the eighth embodiment of the present invention will be described focusing on the differences from the sixth embodiment described above, and the common points will be omitted as appropriate.
FIG. 16 is a cross-sectional view perpendicular to the axis showing the periphery of the tilting pad in the tilting pad type journal bearing according to the eighth embodiment of the present invention.

  As shown in FIG. 16, in the tilting pad type journal bearing 20c according to the eighth embodiment, the pad 2 is the front edge of the pad 2, that is, the upstream end of the pad 2 in the rotational direction of the rotating shaft 1. Although it differs from 6th Embodiment by the point which has the processus | protrusion 14 provided in, other is the same.

  The protrusion 14 has an inner peripheral extension surface 14a formed by extending the inner peripheral surface 2a of the pad 2 to the upstream side, and an acute angle with respect to the inner peripheral extension surface 14a from the tip edge of the inner peripheral extension surface 14a. And an inclined surface 14b.

  According to the eighth embodiment, the carry-over oil 6f lubricated through the sliding surface of the pad 2 located on the upstream side in the rotation direction of the rotating shaft 1 is converted into an edge-like shape having an acute tip edge. The projection 14 can be scraped off the rotary shaft 1. Therefore, according to the eighth embodiment, in addition to being able to achieve the same functions and effects as those of the sixth embodiment, the carry-over oil 6f whose temperature has risen is reduced from flowing into the sliding surface of the next pad 2. This makes it easier for new lubricating oil with a low temperature supplied from the nozzle 9 to be drawn into the sliding surface. As a result, the oil film temperature on the sliding surface can be further reduced.

[Ninth Embodiment]
Next, with reference to FIG. 17, the ninth embodiment of the present invention will be described with a focus on differences from the above-described sixth embodiment, and description of common points will be omitted as appropriate.
FIG. 17 is a cross-sectional view perpendicular to the axis showing the periphery of the tilting pad in the tilting pad type journal bearing according to the ninth embodiment of the present invention.

  As shown in FIG. 17, in the tilting pad type journal bearing 20d according to the ninth embodiment, the restricting structure for restricting the relative position in the circumferential direction between the pad 2 and the bearing housing 5 is different from that in the sixth embodiment. But others are similar.

  In the ninth embodiment, the restricting structure has a concave surface 5 d that is formed on the inner peripheral surface 5 a of the bearing housing 5 and engages with the convex surface 12 a of the pivot 12. Here, the radius of curvature of the concave surface 5d is equal to or larger than the radius of curvature of the convex surface 12a and is smaller than the radius of the inner peripheral surface 5a. With such a configuration, the circumferential positional relationship between the pad 2 and the bearing housing 5 is restricted, and the gap 8 between the nozzle 9 and the pad 2 can be reliably held with a simple configuration. Also according to the ninth embodiment, the same operational effects as those of the sixth embodiment can be obtained.

[Tenth embodiment]
Next, with reference to FIG. 18, the tenth embodiment of the present invention will be described with a focus on differences from the first embodiment described above, and description of common points will be omitted as appropriate.
FIG. 18A is a plan view of a tilting pad in a tilting pad type journal bearing according to the tenth embodiment of the present invention, and FIG. 18B is a cross-sectional view taken along line MM in FIG. FIG.

  As illustrated in FIG. 18, the tilting pad type journal bearing 20 e according to the tenth embodiment includes an oil discharge nozzle 15 that discharges the lubricating oil that has passed through the pad inner hole 73 from the inside of the guide hole 72 to the outside of the bearing housing 5. It is different from the first embodiment in that it is provided, but the others are the same.

  The oil discharge nozzle 15 is connected to an outlet 77 which is an open end of the pad inner hole 73 on the side opposite to the guide hole 72. The oil discharge nozzle 15 has an L-shaped bent shape, and the tip side thereof is inserted into a hole 5 e formed so as to penetrate the bearing housing 5 in the radial direction. A gap 18 is formed between the oil discharge nozzle 15 and the inner surface of the hole 5 e of the bearing housing 5 to avoid contact between the oil discharge nozzle 15 and the bearing housing 5 even if the pad 2 swings.

  According to such a tenth embodiment, since there is a gap 18 between the oil discharge nozzle 15 and the bearing housing 5, the oil discharge nozzle 15 can swing the pad 2 without contacting the bearing housing 5. Tracking is possible and does not limit the movement of the pad 2. Further, the lubricating oil 6c that has contributed to the reduction of the pad internal temperature through the pad internal hole 73 can be reliably discharged to the outside of the tilting pad type journal bearing 20e. Thereby, it is possible to prevent the lubricating oil 6g drained through the pad internal hole 73 from touching the pad 2 again, and to reliably prevent the pad 2 from being heated.

  As mentioned above, although this invention was demonstrated based on embodiment, this invention is not limited to above-described embodiment, Various modifications are included. For example, the above-described embodiment has been described in detail for easy understanding of the present invention, and is not necessarily limited to one having all the configurations described. Further, a part of the configuration of an embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of an embodiment. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

  In the above-described embodiment, the case where the tilting pad type journal bearing is applied to a rotary machine such as a centrifugal compressor has been described. However, the present invention is not limited to this, and various types of steam turbines, gas turbines, and the like can be used. Applicable to rotating machinery.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 1a Outer peripheral surface 2 Tilting pad 2a Inner peripheral surface 2b Outer peripheral surface 3 Oil supply pipe 3a O-ring 31 Introduction hole 4 Pin (regulation structure)
5 Bearing housing 5a Inner peripheral surface 5d Concave surface (regulatory structure)
5e Hole 6 Lubricating oil 6a Lubricating oil drawn into the sliding surface 6b Lubricating oil not drawn into the sliding surface 6c Lubricating oil passing through the internal hole 6d Lubricating oil coming off to the side 6e Flowing with rotation of the shaft Lubricating oil 6f Carry-over oil 6g Drained lubricating oil 7 Oil supply groove structure 71 Wall 72, 72a Guide hole 73, 73a Pad internal hole 76 Intersection of pad internal hole 77 Outlet 78 Inlet 79 Inner end face 8 Clearance 9 Nozzle 9a Spout 9b Inlet 9c Distribution chamber 10 Rotating direction 11 Through hole 12 Pivot 12a Convex surface 12b Engagement hole (regulation structure)
14 Protrusion 14a Inner peripheral extension surface 14b Inclined surface 15 Oil drain nozzle 16 End plate 17 Nozzle 17a Oil reservoir 17b Inlet 18 Clearance 20, 20a-20e Tilting pad type journal bearing

Claims (13)

A plurality of tilting pads that radially support the rotation axis;
A bearing housing that houses the plurality of tilting pads in a swingable manner;
A regulation structure that regulates a relative position in the circumferential direction between the tilting pad and the bearing housing, and
The tilting pad is
It is formed in a concave shape on the inner peripheral surface of the tilting pad on the upstream side in the rotational direction of the rotary shaft and on both sides of the axial end of the rotary shaft, and the inner peripheral surface of the tilting pad and the outer peripheral surface of the rotary shaft A pair of guide holes for taking in a part of the lubricating oil flowing into the upstream side in the rotational direction between,
A pad internal hole for allowing the lubricant guided through the guide hole to pass through the inside of the tilting pad and then to flow out of the tilting pad on the downstream side in the rotation direction of the rotary shaft with respect to the guide hole; A tilting pad type journal bearing characterized by comprising: The dimension of the rotation direction of the rotating shaft of the guide hole is larger than both the dimension of the guide hole in the axial direction of the rotation shaft and the dimension of the guide hole in the depth direction. The tilting pad type journal bearing described in 1. The inner end surface of the guide hole on the downstream side in the rotation direction of the rotation shaft is located upstream of the center position in the rotation direction of the rotation shaft on the inner peripheral surface of the tilting pad. Item 3. A tilting pad type journal bearing according to Item 2. 2. The tilting pad type journal bearing according to claim 1, wherein a crossing portion where a pair of the pad inner holes communicating with the pair of guide holes respectively intersect is formed. The tilting pad is
It is formed in a concave shape between the pair of guide holes on the upstream side in the rotation direction of the rotary shaft on the inner peripheral surface of the tilting pad, and between the inner peripheral surface of the tilting pad and the outer peripheral surface of the rotary shaft. An oil groove structure for storing the lubricating oil to be supplied;
An introduction hole for introducing lubricating oil, which is formed from the radially outer side of the rotating shaft in the tilting pad to the oil supply groove structure;
5. The oil supply groove structure according to claim 1, further comprising: a pair of wall portions provided on both sides of an axial end portion of the rotation shaft of the oil supply groove structure and partitioning the oil supply groove structure and the guide hole. The tilting pad type journal bearing according to any one of the above. The clearance between the radially inner end surface of the wall and the outer peripheral surface of the rotating shaft is larger than the clearance between the inner peripheral surface of the tilting pad and the outer peripheral surface of the rotating shaft. The tilting pad type journal bearing according to claim 5. A nozzle for supplying lubricating oil between the inner peripheral surface of the tilting pad and the outer peripheral surface of the rotary shaft;
The tilting pad has a through-hole penetrating from the outer peripheral surface to the inner peripheral surface of the tilting pad,
The nozzle passes through the through-hole of the tilting pad, a base end is fixed to the bearing housing, and a tip end faces the outer peripheral surface of the rotating shaft,
A gap is formed between the nozzle and the inner surface of the through hole of the tilting pad so as to avoid contact between the nozzle and the tilting pad even if the tilting pad swings. The tilting pad type journal bearing according to any one of claims 1 to 4. The tilting pad type journal bearing according to claim 7, wherein a jet port for jetting lubricating oil is provided at the tip portion of the nozzle. The tilting pad type journal according to claim 7, wherein an oil reservoir that has an opening that faces the outer peripheral surface of the rotating shaft and that can store lubricating oil is provided at the tip of the nozzle. bearing. The tilting pad has a protrusion provided at an upstream end portion of the tilting pad in the rotation direction of the rotation shaft,
The protrusion includes an inner peripheral extension surface formed by extending the inner peripheral surface of the tilting pad to the upstream side, and an acute angle from a tip edge of the inner peripheral extension surface to the inner peripheral extension surface. The tilting pad type journal bearing according to any one of claims 1 to 4, further comprising an inclined surface. A convex pivot is formed on the outer peripheral surface of the tilting pad to support the tilting pad so as to be swingable.
The said restriction | limiting structure has a pin fixed to the said bearing housing, and an engagement hole which is formed in the said pivot and the said pin inserts and engages with any one of Claim 1 to 4 characterized by the above-mentioned. The tilting pad type journal bearing described in the item. A convex pivot is formed on the outer peripheral surface of the tilting pad to support the tilting pad so as to be swingable.
5. The tilting pad type journal bearing according to claim 1, wherein the restricting structure has a concave surface that is formed on an inner peripheral surface of the bearing housing and engages with the pivot. . An oil discharge nozzle that is connected to an outlet that is an opening end of the pad inner hole opposite to the guide hole, and that discharges lubricating oil that has passed through the pad inner hole from the inside of the guide hole to the outside of the bearing housing;
The front end side of the oil discharge nozzle is inserted into a hole formed through the bearing housing in the radial direction,
A gap is formed between the oil discharge nozzle and the inner surface of the hole of the bearing housing to avoid contact between the oil discharge nozzle and the bearing housing even if the tilting pad swings. The tilting pad type journal bearing according to any one of claims 1 to 4, wherein the tilting pad type journal bearing is provided.

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