KR20090114460A - Journal bearing device - Google Patents

Abstract

A journal bearing device (10) has upper half pads (21) on an upper half bearing section (20) of a bearing supporting a rotating shaft (50), and also has lower half pads (31) on a lower half bearing section (30). The lower half pads (31) are arranged on the inner peripheral surface of the lower half bearing section (30) with intervals in the circumferential direction of the surface. One of the lower half pads (31) is placed at a position perpendicularly below the rotating shaft (50).

Description

Journal Bearing Device {JOURNAL BEARING DEVICE}

The present invention relates to a journal bearing device for supporting a rotating shaft in a rotating machine.

The journal bearing used for a rotating machine is assembled so that the center axis of a bearing and the center axis of a rotating shaft may become parallel. However, at the time of rotation, the misalignment in the state which shifted so that the center axis of a bearing and the center axis of a rotating shaft may not become parallel by the direction of a load, a deformation of a rotating shaft, etc. may arise. Moreover, when a rotational load acts, conical oscillation rotation may arise, for example which makes the intersection of the center axis of a bearing and the center axis of a rotating shaft. In such a driving state, there is a possibility that damage (sticking) due to piece contact occurs at the sliding end of the bearing. Thus, various techniques have been reported so far in order to prevent damage to the rotating shaft as described above. 11-13 is a figure which shows the cross-sectional structure of the conventional journal bearing apparatus.

Japanese Patent Laid-Open No. 9-25932 discloses a journal bearing device 300 shown in FIG. 11. The journal bearing device 300 has a concave spherical surface slid with a spherical bearing 301 whose back surface is convex and a spherical surface of the bearing 301. The bearing stand 302 is provided. And in this journal bearing apparatus 300, when the rotating shaft 303 inclines during operation, both spherical surfaces slide and follow the rotating shaft 303, and the bearing 301 self-aligns.

Japanese Patent Laid-Open No. 5-32797 discloses a journal bearing device 320 shown in FIG. 12. The journal bearing device 320 is a sliding layer 322 made of a resin-based composite material having excellent sliding properties on a sliding surface of a bearing 321 sliding with the rotating shaft 323. Equipped with. This structure prevents abrasion and seizure of the rotating shaft 323 even when one-sided contact of the rotating shaft 323 occurs, and can be used as a large bearing. In addition, Japanese Patent Laid-Open No. 2001-173659 discloses a technique in which the sliding layer 322 is provided in an elliptical bearing in a region excluding a part of the bearing sliding surface of the bearing 321.

Japanese Laid-Open Patent Publication No. 2004-197890 discloses a journal bearing device 330 shown in FIG. This journal bearing device 330 is a tilting pad bearing generally used as a bearing having excellent self-alignment in the past. The tilting pad 331 is supported by the pivot 332 or the like so as to be inclined in the circumferential direction and the axial direction, so that the tilting pad 331 can easily follow the inclination of the rotation shaft 333.

As described above, in the conventional journal bearing device, a technique for preventing damage to the bearing by following the inclination of the rotating shaft during operation is proposed, but the following problems remain.

In the journal bearing device shown in FIG. 11, when the load to a bearing is large, there exists a problem that the friction force between spherical surfaces becomes excessive, a bearing becomes difficult to incline, and trackability worsens. Therefore, when the amount of misalignment increases, there exists a possibility that the one side contact of a rotating shaft and a bearing may arise, and the surface of a rotating shaft and a bearing may be damaged (pressed).

In addition, in the journal bearing device shown in FIG. 12, wear on the bearing side has evolved over time, and the characteristics of the bearing gradually decrease, making it difficult to form a lubricant film on the sliding surface. If a lubricating oil film is not formed, an abnormal temperature rise may occur due to frictional heat, the sliding layer may deteriorate by exceeding the heat resistance temperature of the resin, and the surface of the bearing may come in contact with the rotating shaft, resulting in damage. In addition, in the elliptical bearing, when the sliding layer is provided in an area excluding a part of the sliding surface of the bearing, the area in which the lubricant moves is wide, so that energy loss due to stirring of the lubricant and gap adjustment for misalignment can be achieved. There was a problem such as difficulty.

In addition, in the journal bearing device shown in FIG. 13, when used as a bearing for low rotational speed under high load, such as a large capacity valve aberration generator, the inherent self-alignment with respect to the inclination of a rotating shaft is hard to be exhibited by a load. there is a problem. In addition, there are also problems such as poor load performance compared to cylindrical bearings, difficulty in forming a sufficient lubricating oil film, and large bearing dimensions because the sliding surfaces are divided into a plurality of sliding surfaces.

Patent Document 1: Japanese Patent Application Laid-Open No. 9-25932

Patent Document 2: Japanese Patent Application Laid-Open No. 5-32797

Patent Document 3: Japanese Patent Application Laid-Open No. 2001-173659

Patent Document 4: Japanese Patent Application Laid-Open No. 2004-197890

Accordingly, an object of the present invention is to prevent damage to a bearing, a rotating shaft, and the like caused by the inclination of the rotating shaft generated during operation, even at a low rotational speed under a large load, so that a bearing of a large diameter rotating shaft can be prevented. To provide a sufficiently applicable journal bearing device.

According to one aspect of the present invention, there is provided a journal bearing device including an upper half pad in an upper half bearing of a bearing supporting a rotating shaft, and a lower half pad in a lower half bearing. A plurality of the lower half pads are disposed at predetermined intervals along a circumferential direction, and one of the plurality of lower half pads is disposed vertically downward of the rotation shaft. do.

Moreover, according to one aspect of the present invention, there is provided a journal bearing device having an upper half pad in a bearing supporting a rotating shaft and a lower half pad in a lower half bearing, the journal bearing device having a predetermined circumferential direction along an inner circumferential surface of the lower half bearing. A plurality of rows of pads in which a plurality of the lower half pads are disposed at intervals is provided in a plurality of rows at predetermined intervals in the axial direction of the rotation axis, and one of the plurality of lower half pads in each of the pad rows is perpendicular to the rotation axis. A journal bearing device is provided which is disposed below.

1 is a view showing a cross section perpendicular to the axis of rotation in the journal bearing device of the first embodiment according to the present invention;

Fig. 2 is a view showing a cross section (A-A cross section in Fig. 1) horizontal to the axis of rotation in the journal bearing device of the first embodiment according to the present invention.

FIG. 3 is a diagram showing a cross section horizontal to the axis of rotation in the lower half bearing portion when a liner is interposed between the lower half pad and the inner circumferential surface of the lower half bearing portion. FIG.

Fig. 4 is a diagram showing a cross section perpendicular to the rotation axis in the journal bearing device in the case where the lower half pad is provided corresponding to the eccentric angle θ of the oil film pressure distribution.

Fig. 5 is a diagram showing a cross section perpendicular to the rotation axis in the journal bearing device in the case where the lower half pad is provided corresponding to the eccentric angle θ of the oil film pressure distribution.

Fig. 6 is a view showing a section perpendicular to the axis of rotation in the journal bearing device of the second embodiment according to the present invention.

Fig. 7 is a view showing a cross section (B-B cross section in Fig. 6) horizontal to the axis of rotation in the journal bearing device of the second embodiment according to the present invention.

FIG. 8 is a diagram showing the flow of lubricating oil in the lower half bearing portion when the lower half bearing portion is seen from above; FIG.

Fig. 9 is a plan view showing an example of a shape when the upper half pad and the lower half pad disposed on the inner circumferential surface of the journal bearing body are viewed from the rotation axis side.

FIG. 10 is a cross-sectional view taken along the line C-C in FIG. 9; FIG.

Fig. 11 is a diagram showing the structure of a cross section of a conventional journal bearing device.

12 is a view showing a structure of a cross section of a conventional journal bearing device.

Fig. 13 is a diagram showing the structure of a cross section of a conventional journal bearing device.

Explanation of the sign

10: journal bearing device 20: upper half bearing portion

21: upper half pad 21a, 31a: surface layer

21b, 31b: base material 30: lower half bearing part

31: lower half pad 31a, 31b, 35: liner

40: journal bearing body 50: rotating shaft

W: gravity load.

EMBODIMENT OF THE INVENTION Hereinafter, one Example of this invention is described with reference to drawings.

(First embodiment)

1 is a view showing a cross section perpendicular to the rotation axis 50 in the journal bearing device 10 of the first embodiment according to the present invention. FIG. 2 is a view showing a cross section (A-A cross section in FIG. 1) horizontal to the rotation axis 50 in the journal bearing device 10 of the first embodiment according to the present invention. 3 is a cross section (axial cross section) horizontal to the rotation shaft 50 in the lower half bearing portion 30 when the liner 35 is interposed between the lower half pad 31 and the inner circumferential surface of the lower half bearing portion 30. Figure is a diagram.

As shown in FIG. 1, the journal bearing device 10 includes an upper half bearing portion 20 having the upper half pad 21 on the inner circumferential surface and a lower half bearing portion 30 having the lower half pad 31 on the inner circumferential surface. The journal bearing main body 40 which consists of these is comprised, and the structure which supports the rotating shaft 50 with the upper half pad 21 and the lower half pad 31 is provided. The upper half bearing part 20 is an upper half bearing part when the journal bearing main body 40 is divided into two in the horizontal plane which passes through the center of the journal bearing main body 40, and the lower half bearing part 30 is It is a bearing part of the lower half.

1 and 2, the upper half pad 21 is disposed on the inner circumferential surface of the upper half bearing portion 20 at predetermined intervals along the circumferential direction, and the lower half pad 31 is the lower half bearing portion 30. Exposed at predetermined intervals along the circumferential direction on the inner peripheral surface of the. That is, the upper half pad 21 and the lower half pad 31 are respectively disposed along the circumferential direction in a divided state. In addition, the upper half pad 21 and the lower half pad 31 are attached to the inner peripheral surface of the upper half bearing part 20 and the lower half bearing part 30 so that attachment or detachment is possible. One of the lower half pads 31 arranged in multiple numbers is arrange | positioned perpendicularly under the rotating shaft 50. As shown in FIG. Moreover, it is preferable to arrange | position the upper half pad 21 and the lower half pad 31 especially in the inner peripheral surface on which radial load acts remarkably. By arranging the upper half pad 21 and the lower half pad 31 in this way, in the case where the rotating shaft 50 is at a low rotational speed at a large load, even when the gravity direction load W greatly increases and rotates, sufficient load capacity is achieved. Can be secured. In addition, load capacity here means the maximum load which can be supported by the bearing.

The radius of curvature of the upper half pad 21 and the lower half pad 31 has a curvature slightly larger than the radius of the rotation shaft 50 in order to form an oil film between the surfaces of the rotating shaft 50.

The predetermined interval between the lower half pads 31 provided in the lower half bearing portion 30 is preferably such that the lubricating oil can flow through the gap formed between the lower half pads 31, and the viscosity of the lubricating oil, It sets suitably based on the temperature conditions etc. which are used.

In addition, the upper half pad 21 and the lower half pad 31 contain a thermoplastic resin containing at least one of particles made of a thermoplastic resin material, ceramic fibers, molybdenum disulfide, graphite, and the like on the surfaces of the substrates 21b and 31b. It consists of surface layers 21a and 31a formed of a material. The base materials 21b and 31b are comprised of steel materials, such as ordinary steel and stainless steel. As resin which comprises surface layers 21a and 31a, polytetrafluoroethylene (PTFE) resin, polyether ether ketone (PEEK) resin, polyimide (PI) resin, etc. are mentioned specifically ,. Moreover, as a thermoplastic resin material containing the particle | grains which consist of ceramic fiber, molybdenum disulfide, graphite, etc., specifically, similarly to the above-mentioned resin, polytetrafluoroethylene (PTFE) resin, polyether ether ketone (PEEK) resin, polyei Mid (PI) resin etc. are mentioned. It is preferable that the content rate of the material contained in a thermoplastic resin material, ie, the ratio of the weight of the material contained with respect to the weight of resin containing the material contained is 10-20 weight%. This range is preferable because the effect of the contained material is not remarkable when the content is less than 10% by weight. When the content is more than 20% by weight, an effect proportional to the amount cannot be expected. Here, when it contains a ceramic fiber, mechanical strength and abrasion resistance improve, and when it contains the particle | grains which consist of molybdenum disulfide, graphite, etc., a friction coefficient reduces.

Thus, by forming the surface of the upper half pad 21 and the lower half pad 31 with the resin material, the friction coefficient is drastically reduced compared with the case where the soft metal material conventionally used for the surface is used. Thereby, for example, the axial movement of the rotating shaft 50 on the lower half pad 31 at the time of an assembling operation can be made easy. In particular, the lower half pad 31 disposed below the rotary shaft 50 can support the surface below the vertical axis of the rotary shaft 50, so that the axial movement of the rotary shaft 50 can be facilitated. . In addition, since the surface is formed of a resin material, it has excellent wear resistance. Therefore, even when the oil film thickness is thin or the oil film is not formed at the start of the rotation shaft 50, the contact between the surface of the rotation shaft and the pad surface is Local wear and damage of the rotating shaft 50 and the sliding surface of the pad due to one-sided contact with the rotating shaft 50 can be suppressed without using an oil lifter.

In addition, the surface layer 21a of the upper half pad 21 may be made of a soft metal material having a hardness lower than that of the material constituting the rotating shaft 50, that is, flexible, withstanding the formed oil film pressure, and having wear resistance. As this soft metal material, a white metal etc. are mentioned, for example. Thus, when using a soft metal material as a surface layer, since the manufacturing method of a conventional bearing pad can be applied, manufacturing cost can be reduced. Moreover, also in the lower half pad 31, when arrange | positioning on the inner peripheral surface with a small radial load, it is also possible to comprise the surface layer 31a of the lower half pad 31 from soft metal materials, such as a white metal.

Here, when a misalignment in which the center axis of the journal bearing main body 40 and the center axis of the rotating shaft 50 do not become parallel and shifted is produced, the center axis of the journal bearing main body 40 and the rotating shaft 50 There may be cases where a conical oscillation occurs with the intersection of the central axis as the vertex. In order to avoid such a state, between the rear surface of the predetermined upper half pad 21 and the inner peripheral surface of the upper half bearing part 20, and / or between the rear surface of the predetermined lower half pad 31 and the inner peripheral surface of the lower half bearing part 30. The pads 21 and 31 may be fixed via the liner 35 functioning as a thin plate to adjust the bearing gap. As a result, the rigidity of the bearing is increased, and the vibration can be suppressed. In addition, since the upper half pad 21 and the lower half pad 31 are fixed to a bearing part so that attachment or detachment is possible, the position where the upper half pad 21 and the lower half pad 31 are moved or the number of pads is increased or decreased, One vibration may be suppressed. The liner is composed of, for example, a thin plate or foil made of steel such as ordinary steel or stainless steel.

Here, the case where the liner 35 is fixed between the back surface of the lower half pad 31 and the inner peripheral surface of the lower half bearing part 30 is demonstrated as an example. As shown in FIG. 3, the lower half pad 31 fixes the fixing member 36 from the outer circumferential side of the lower half bearing portion 30 by, for example, a screw 37 to lower the lower half bearing portion 30. It is fixed to the inner circumferential surface of the. When the thin plate is interposed between the rear surface of the lower half pad 31 and the inner circumferential surface of the lower half bearing portion 30, first, the fixing member 36 is separated, and the rear side of the lower half pad 31 and the lower half bearing portion 30 are provided. The liner 35 is inserted between the inner circumferential surfaces of Subsequently, the fixing member 36 is fixed by the screw 37. In addition, the above-described liner 35 is mounted in a state in which the rotation shaft 50 is lifted up, that is, in a state in which the load of the rotation shaft 50 is not bound to the journal bearing body 40. In addition, the fixing method of the lower half pad 31 is not limited to the above-mentioned method, It does not matter in particular if it is a method which can fix the lower half pad 31 to the inner peripheral surface of the lower half bearing part 30. The upper half pad 21 is also fixed in the same manner as the lower half pad 31.

Next, the pressure distribution of the oil film formed between the rotating shaft 50 and the lower half pad 31 is demonstrated.

4 and 5 show a cross section perpendicular to the rotation axis 50 in the journal bearing device 10 when the lower half pad 31 is provided corresponding to the eccentric angle θ of the oil film pressure distribution 60. One drawing. In addition, lubricating oil is supplied in the journal bearing main body 40 from the top part of the upper half bearing part 20, and also between two upper half pads 21, for example.

Usually, in the journal bearing apparatus 10, when the rotating shaft 50 rotates, the oil film by lubricating oil is formed between the journal bearing apparatus 10 and the rotating shaft 50, and lubrication of the rotating shaft 50 is maintained, and the journal The load on the rotating shaft is supported by the bearing device 10. The oil film pressure distribution 60 and, in other words, the region in which the oil film pressure shows a peak value are shifted in the rotation direction 65 of the rotation shaft 50 by the eccentric angle θ with respect to the static load.

As shown in FIG. 4, the lower half pad 31 arrange | positioned under the vertical direction of the rotating shaft 50 is 10-15 degrees (eccentric angle (theta) = 10-15 degrees) in the rotation direction of the rotating shaft 50. As shown in FIG. ) Move about. In addition, since this movement range (eccentric angle) is largely changed by the amount of clearance between the rotation shaft 50 and the pads 21 and 31, the movement range (eccentric angle) is set to the optimum position by the apparatus to which the journal bearing main body 40 is applied. It is preferable to adjust.

When the eccentric angle becomes large by such adjustment, as shown in FIG. 5, you may install the lower half pad 31 arrange | positioned under the vertical direction of the rotating shaft 50 in the rotation direction of the rotating shaft 50. As shown in FIG. . In this case, the surface area of the lower half pad 31 disposed below the vertical axis of the rotation shaft 50 increases, and the oil film pressure distribution can be spread over a wide range.

As described above, by appropriately changing the installation position and size of the lower half pad 31 in correspondence with the oil film pressure distribution 60, an oil film can be sufficiently formed between the rotation shaft 50 and the lower half pad 31. The load capacity can be increased.

According to the journal bearing device 10 of the first embodiment described above, the upper half pad 21 and the lower half pad 31 are divided into a plurality of circumferential directions of the inner circumferential surface of the journal bearing main body 40 and provided at an arbitrary position. It becomes possible to arrange | position, and to follow the misalignment of the rotating shaft 50 easily. In addition, the upper half pad 21 and the lower half pad 31 can be selectively disposed on the inner circumferential surface in which the load W acts remarkably in the gravity direction. In addition, the thickness of the pad can be locally adjusted by inserting the liner 35 between the back surface of the predetermined pad and the inner circumferential surface of the bearing portion among the upper half pad 21 and / or the lower half pad 31 provided in a plurality. have. Thereby, adjustment of a bearing gap etc. can be performed easily.

In addition, the upper half pad 21 and the lower half pad 31 are provided by dividing the plurality of the upper half pads 21 and the lower half pads 31 in the circumferential direction of the inner circumferential surface of the journal bearing main body 40 at predetermined intervals, thereby providing a flow of lubricating oil so as to flow the gap between the pads. Is mainly the flow that is fed over the pads. Here, since the lubricating oil which flows between pads is lower than the lubricating oil which flows on a pad, it becomes possible to always supply low temperature lubricating oil to a pad. Thus, since the low temperature lubricating oil can be supplied on the upper half pad 21 and the lower half pad 31, that is, between the upper half pad 21 and the lower half pad 31 and the rotary shaft 50, each pad and journal bearing Cooling of the main body 40 can be promoted to increase the load capacity.

In addition, the upper half pad 21 and the lower half pad 31 can be produced in any size, and the pad can be disposed in the circumferential direction of the inner circumferential surface of the journal bearing body 40. Therefore, even if the diameter of the rotating shaft 50 becomes large, the journal bearing apparatus 10 can be manufactured regardless of the manufacture limit of the journal bearing main body 40. FIG. In addition, in consideration of the eccentric angle of the oil film pressure distribution, the pad excretion position and the area of the surface of each pad can be arbitrarily set, so that the oil film pressure distribution can be spread over a wide range. Thereby, since an oil film can fully be formed, load capacity can be increased. In addition, since the upper half pad 21 and the lower half pad 31 are fixed by directly contacting the back surface of the pad with the inner circumferential surface of the journal bearing main body 40, the rigidity of the journal bearing main body 40 increases, and a large load is obtained. Can also cope with.

(Second embodiment)

6 is a view showing a cross section perpendicular to the rotation axis 50 in the journal bearing device 100 of the second embodiment according to the present invention. FIG. 7 is a view showing a cross section (B-B cross section in FIG. 6) horizontal to the rotation axis 50 in the journal bearing device 100 of the second embodiment according to the present invention. FIG. 8: is a figure which shows the form of the flow of lubricating oil in the lower half bearing part 30 when the lower half bearing part 30 is seen from above (rotation shaft 50 side). FIG. 9: is a top view which shows an example of the shape when the upper half pad 21 and the lower half pad 31 provided in the inner peripheral surface of the journal bearing main body 40 were seen from the rotating shaft 50 side. 10 is a cross-sectional view taken along the line C-C of FIG. In addition, the description which attaches | subjects the same code | symbol to the same component part as the journal bearing apparatus 10 of 1st Example, and overlaps is abbreviate | omitted or simplified.

As shown in FIG. 6 and FIG. 7, the journal bearing device 100 has a predetermined distance along the circumferential direction on the inner circumferential surface of the upper half bearing portion 20 in the journal bearing device 10 of the first embodiment. A pad row formed of a plurality of lower half pads 31 disposed at a predetermined interval along the circumferential direction on a pad row formed of the plurality of upper half pads 21 disposed in the circumferential direction, in an axial direction. Two rows are provided at predetermined intervals. Moreover, in each pad row in the lower half bearing part 30, one of the several lower half pads 31 is arrange | positioned under the rotation axis 50 perpendicularly. The pad rows may be provided in three or more rows at predetermined axial intervals.

Here, the pad row of the upper half pad 21 in the upper half bearing part 20 and the pad row of the lower half pad 31 in the lower half bearing part 30 are arranged in series in the circumferential direction, that is, on the same circumference. Although an example provided in one line is shown, it is not limited to this excretion structure. For example, in the circumferential direction, that is, the row of pads of the upper half pad 21 in the upper half bearing part 20 and the row of pads of the lower half pad 31 in the lower half bearing part 30 are arranged on the same circumference. The configuration may not be sufficient. In addition, in the upper half bearing part 20 and the lower half bearing part 30, when providing several pad row | line | column in an axial direction, the arrangement | positioning structure from which the pad number of each pad row | line | column differs may be sufficient. Specifically, for example, the number of pads in the pad row of one lower half pad 31 is three, and the number of pads in the pad row of the other lower half pad 31 adjacent to each other at predetermined intervals is two. You may also. Thus, the arrangement | positioning structure of the pad divided | segmented and divided into the inner peripheral surface of the upper half bearing part 20 and the lower half bearing part 30 can be set suitably corresponding to misalignment etc., for example.

Moreover, it is preferable that the predetermined space | interval between the pad rows provided in the axial direction is a grade in which the lubricating oil can flow through the clearance gap formed between the pad rows, and is set suitably based on the viscosity of lubricating oil, the temperature conditions used, etc.

In addition, when the misalignment which the center axis | shaft of the journal bearing main body 40 and the center axis | shaft of the rotation shaft 50 are not parallel and shifted | deviated has arisen, similarly to the case of the journal bearing apparatus 10 of 1st Example, a predetermined | prescribed A liner functioning as a thin plate is interposed between the rear surface of the upper half pad 21 and the inner circumferential surface of the upper half bearing portion 20 and / or between the rear surface of the predetermined lower half pad 31 and the inner circumferential surface of the lower half bearing portion 30. Each of the pads 21 and 31 may be fixed to adjust the bearing gap. In the journal bearing apparatus 100, since a plurality of rows of pads can be provided in the axial direction, for example, different bearing gaps can be adjusted for each row.

Next, the form of the flow of lubricating oil in the lower half bearing part 30 of the journal bearing apparatus 100 is demonstrated with reference to FIG.

In FIG. 8, two pad rows of the lower half pads 31, which are disposed at predetermined intervals along the circumferential direction on the inner circumferential surface of the lower half bearing portion 30 in the longitudinal direction of the drawing, are shown in a plan view. Therefore, for example, the lower half pad 31 arrange | positioned under the vertical direction of the rotating shaft 50 turns into the 2nd lower half pad 31 from the upper half of the lower half pad 31 shown in FIG. In addition, lubricating oil is supplied in the journal bearing main body 40 from the top part of the upper half bearing part 20, and also between pad rows, for example.

As shown in FIG. 8, the lubricating oil flowing through the gaps 110 between the rows of pads becomes the main stream 120, and from this main stream 120, on each lower half pad 31 and each lower half of each pad row. Classification is made in the gap between the pads 31. Moreover, the lubricating oil classified in the clearance gap of each lower half pad 31 of each pad row | line | column flows in on the lower half pad 31, too. Since the lubricating oil flowing through the liquor 120 is lower than the lubricating oil flowing on the lower half pad 31, it becomes possible to always supply a low temperature lubricating oil onto the lower half pad 31. Moreover, also in the upper half pad 21, it becomes the flow of lubricating oil similar to the case of the lower half pad 31. FIG. Thus, since the low temperature lubricating oil can be supplied on the upper half pad 21 and the lower half pad 31, that is, between the upper half pad 21 and the lower half pad 31 and the rotary shaft 50, each pad and journal bearing Cooling of the main body 40 can be promoted to increase the load capacity.

In addition, an example of the shape of the upper half pad 21 and the lower half pad 31 is demonstrated with reference to FIG. 9 and FIG.

As shown in FIG. 9 and FIG. 10, in the upper half pad 21 and the lower half pad 31 described above, the edges of the side on which the lubricant 121 flows over the upper half pad 21 and the lower half pad 31. The inclined surface 150 is formed. This inclined surface is inclined downward toward the outer side of the upper half pad 21 and the lower half pad 31. By constituting the edge of the side on which the lubricating oil 121 flows into the inclined surface 150, the lubricating oil 121 can be smoothly guided onto the upper half pad 21 and the lower half pad 31. In addition, you may provide the structure of this upper half pad 21 and the lower half pad 31 to the upper half pad 21 and the lower half pad 31 of the journal bearing apparatus 10 of 1st Example mentioned above.

According to the journal bearing device 100 of the second embodiment described above, the pad row and the lower half bearing portion are formed of a plurality of upper half pads 21 disposed on the inner circumferential surface of the upper half bearing portion 20 at predetermined intervals along the circumferential direction. The bearing gap is provided by a plurality of rows of pads formed of a plurality of lower half pads 31 disposed at predetermined intervals along the circumferential direction on the inner circumferential surface of the column 30 at predetermined intervals in the axial direction of the rotation shaft 50. Can be easily and accurately adjusted.

In addition, the low temperature lubricating oil flowing through the gap 110 between the rows of pads becomes the mainstream 120, and is classified from the mainstream 120 to guide the low temperature lubricating oil onto the upper half pad 21 or the lower half pad 31. Therefore, cooling of a pad and a bearing can be performed efficiently. Thereby, increase in the load capacity of the journal bearing apparatus 100, etc. can be aimed at. In addition, by constituting the edges of the side into which the lubricant oil flows over the upper half pad 21 and the lower half pad 31 as the inclined surface 150, the lubricating oil is smoothly guided over the upper half pad 21 and the lower half pad 31, The cooling efficiency of the pad can be further improved.

In addition, the upper half pad 21 and the lower half pad 31 can be produced in any size, and the pad can be disposed in the circumferential direction of the inner circumferential surface of the journal bearing main body 40. Therefore, even if the diameter of the rotating shaft 50 becomes large, the journal bearing apparatus 100 can be manufactured irrespective of the manufacturing limit of the journal bearing main body 40. FIG. In addition, in consideration of the eccentric angle of the oil film pressure distribution, the position of pad excretion and the area of the surface of each pad can be arbitrarily set, so that the oil film pressure distribution can be spread over a wide range. Thereby, since an oil film can fully be formed, load capacity can be increased. In addition, since the upper half pad 21 and the lower half pad 31 are fixed by directly contacting the back surface of the pad with the inner circumferential surface of the journal bearing main body 40, the rigidity of the journal bearing main body 40 increases, and a large load is obtained. Can also cope with.

In addition, this invention is not limited only to the said Example, At the implementation stage, a component can be modified and embodied in the range which does not deviate from the summary. Moreover, various inventions can be formed by appropriate combination of the some component disclosed by the said Example. For example, some components may be deleted from all the components shown in the embodiment. Moreover, you may combine suitably the component which concerns on other embodiment.

According to the journal bearing device according to the aspect of the present invention, the upper and lower pads can be disposed in any size at any position by dividing the upper and lower pads in the circumferential direction of the inner circumferential surface of the journal bearing main body. Therefore, it becomes easy to follow the misalignment of a rotating shaft. In addition, in consideration of the eccentric angle of the oil film pressure distribution, the pad excretion position and the area of the surface of each pad can be arbitrarily set, so that the oil film pressure distribution can be spread over a wide range. Thereby, since an oil film can fully be formed, load capacity can be increased. The journal bearing device according to the aspect of the present invention is effectively used, for example, as a bearing of a large diameter rotating shaft.

Claims (18)

A journal bearing device comprising an upper half pad in an upper half bearing of a bearing supporting a rotating shaft and a lower half pad in a lower half bearing, A plurality of the lower half pads are disposed at predetermined intervals along a circumferential direction of the inner peripheral surface of the lower half bearing, and one of the plurality of lower half pads is disposed below the vertical axis of the rotation shaft. Journal bearing device. A journal bearing device comprising an upper half pad of a bearing supporting a rotating shaft, and a lower half pad of a lower half bearing, A plurality of pad rows in which a plurality of lower half pads are disposed at predetermined intervals along a circumferential direction of the inner circumferential surface of the lower half bearing, and a plurality of rows are provided at predetermined intervals in an axial direction of the rotation axis, and the respective pad rows The journal bearing device according to claim 1, wherein one of the plurality of lower half pads is disposed vertically below the rotating shaft. The method of claim 1, At least the surface of the lower half pad is formed of a thermoplastic resin material. The method of claim 2, At least the surface of the lower half pad is formed of a thermoplastic resin material. The method of claim 1, At least the surface of the lower half pad is formed of a thermoplastic resin material containing at least one of ceramic fibers, molybdenum disulfide particles, and graphite particles. The method of claim 2, At least the surface of the lower half pad is formed of a thermoplastic resin material containing at least one of ceramic fibers, molybdenum disulfide particles, and graphite particles. The method of claim 1, Journal surface device characterized in that the surface of the upper half pad is formed of a soft metal material. The method of claim 2, Journal surface device characterized in that the surface of the upper half pad is formed of a soft metal material. The method of claim 1, The upper half pad and the lower half pad are detachably installed. The method of claim 2, The upper half pad and the lower half pad are detachably installed. The method of claim 1, A journal bearing device characterized in that the upper half pad can be fixed between a predetermined upper half pad and an inner circumferential surface of the upper half bearing through a thin plate. The method of claim 2, A journal bearing device, wherein the upper half pad can be fixed between a predetermined upper half pad and an inner circumferential surface of the upper half bearing through a thin plate. The method of claim 1, A journal bearing device, wherein the lower half pad can be fixed between a predetermined lower half pad and an inner circumferential surface of the lower half bearing through a thin plate. The method of claim 2, A journal bearing device, wherein the lower half pad can be fixed between a predetermined lower half pad and an inner circumferential surface of the lower half bearing through a thin plate. The method of claim 1, In the upper half pad, at least the edge of the side which introduces lubricating oil over the surface of the upper half pad is comprised by the inclined surface, The journal bearing apparatus characterized by the above-mentioned. The method of claim 2, In the upper half pad, at least the edge of the side which introduces lubricating oil over the surface of the upper half pad is comprised by the inclined surface, The journal bearing apparatus characterized by the above-mentioned. The method of claim 1, In the lower half pad, at least the edge of the side which introduces lubricating oil on the surface of the lower half pad is comprised by the inclined surface, The journal bearing apparatus characterized by the above-mentioned. The method of claim 2, In the lower half pad, at least the edge of the side which introduces lubricating oil on the surface of the lower half pad is comprised by the inclined surface, The journal bearing apparatus characterized by the above-mentioned.

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