WO2012165540A1

WO2012165540A1 - Sliding member for slide bearing device

Info

Publication number: WO2012165540A1
Application number: PCT/JP2012/064067
Authority: WO
Inventors: 衛介小川
Original assignee: 日立金属株式会社
Priority date: 2011-05-31
Filing date: 2012-05-31
Publication date: 2012-12-06
Also published as: JPWO2012165540A1; JP5664777B2

Abstract

Provided is a low-abrasion sliding member for a slide bearing device. An almost fan-shaped groove (1p) extending in a direction of a center line corresponding to a shape of a sectional view of a bearing portion (1a) is disposed at a shaft insertion portion (1q) so that an opening is made at a left side of an upper surface (1r) having an almost semicircular shape. The bearing portion (1a) inserted into the groove (1p) is fixed by a fixing member (1f) from the direction of the center line. In this fixed state, a sliding surface (1k) of the bearing portion (1a) is disposed further inward than the upper surface (1r) of the shaft insertion portion (1q). Since a step is disposed between the sliding surface (1k) of the bearing portion (1a) and the upper surface (1r) of the shaft insertion portion (1q), a gap is disposed between a sliding surface (outer circumferential surface, 27k) of a sliding portion (27c) which slides with the sliding surface (1k) of the bearing portion (1a) and rotates in the direction of an arrow (E) and both side surfaces (1g, 1s) and the upper surface (1r) of the shaft insertion portion (1q).

Description

Sliding member for sliding bearing device

The present invention relates to a sliding member constituting a slide bearing device that rotates through a liquid lubricating medium, and more particularly to a molten metal plating apparatus such as a slide bearing device in which molten metal is immersed in a molten metal plating bath acting as a lubricating medium. This invention is suitable for the sliding member which is a member to be incorporated.

An example of the bearing structure of a roll in a molten metal plating bath according to the above technical field is disclosed in Patent Document 1 below. According to this patent document 1, "the bearing structure of a roll in a molten metal plating bath of an apparatus for continuously immersing a steel strip in molten metal and plating treatment, and one or both of a rotary shaft and a bearing of the roll is used. In the bearing structure in which a groove is provided at the axial center of the sliding load surface, both ends are closed with a bending portion or a bending portion having an angle opened in the rotational direction of the rotating shaft or the sliding direction of the bearing. There is disclosed a bearing structure of a roll in a molten metal plating bath, characterized in that a plurality of grooves (hereinafter referred to as central grooves) are provided in a plurality of rows in the rotational direction and / or the sliding direction. And, according to the bearing structure of the roll in the molten metal plating bath, “the bearing of the roll in the molten metal plating bath can be used stably for a long period of time, and the molten metal plating operation is stabilized and the cost is reduced. Also, even when the plating process is speeded up, a low friction and stable rotational state can be obtained, and such a bearing structure makes it possible to efficiently produce a molten metal plated product of stable quality. ing.

JP, 2009-120890, A

The object of the present invention is to provide a sliding member for a sliding bearing, which has been further reduced in wear and improved as compared with the bearing structure described in Patent Document 1 mentioned above.

One aspect of the present invention for achieving the above object is a sliding member for a sliding bearing device having at least one sliding surface, which constitutes a bearing portion or a shaft portion of the sliding bearing device rotatably supporting a rotating body. A groove having a first groove, a second groove, and a connection recess directly or indirectly connecting one end of each of the first groove and the second groove, formed in the sliding surface; The other end of each of the first groove and the second groove is an opening having an open end, and in the case where the sliding member for a sliding bearing device constitutes a bearing, the rotational direction of the shaft is In each of the first groove and the second groove, the opening of each of the first groove and the second groove is disposed rearward of the connection recess, and in the case where the sliding member for a sliding bearing device constitutes a shaft portion, the shaft portion In the direction of rotation, the openings of each of the first groove and the second groove both More is disposed forward further, the surface of the groove is a slide member for a sliding bearing device, characterized in that fine irregularities are formed. The shape of the groove portion in a plan view can be substantially V-shaped, substantially U-shaped or substantially W-shaped.

The coefficient of friction loss of at least one of the first groove and the second groove is 0.01 to 0.05 when flowing a liquid having a kinematic viscosity of 4890 St measured in accordance with JIS Z 8803 in the groove portion. Is desirable.

Furthermore, it is desirable that arithmetic mean roughness Ra according to JIS-B0601 of the surface of the groove part where the minute unevenness is formed be 0.3 to 15.0 μm.

In addition, it is preferable that the micro-concavities and convexities be formed on the surface of at least one of the first groove and the second groove, and it is more preferable that the micro-concavities and convexities be formed on the entire surface of the groove. As described above, when micro unevenness is formed on the entire surface of the groove, the surface roughness of the first groove or the second groove of the groove is roughened from the opening toward the connection recess. In particular, the arithmetic mean roughness Ra according to JIS-B0601 of the surface at the opening of the first groove or the second groove is 0.3 to 5.0 μm, and the rough at one end of the first groove or the second groove Desirably, the height Ra is 5.0 to 15.0 μm.

Furthermore, it is desirable that the depth of at least one of the first groove and the second groove is deeper from the opening toward the connection recess, and in addition, the first groove and the second groove are Preferably, at least one of the groove widths narrows from the opening toward the connecting recess.

Furthermore, if the sliding member for a sliding bearing device is made of a ceramic, it is suitable particularly for a sliding bearing device used in a highly corrosive atmosphere such as a molten metal plating device.

One specific embodiment of the present invention is a slide bearing in which any one of the slide members for a slide bearing device described above is incorporated as a bearing portion, the sliding surface being along the rotation direction of the shaft portion, A sliding bearing characterized in that a plurality of grooves are formed. Preferably, a plurality of groove portions are formed in a zigzag shape in parallel with the direction along the center line.

Here, the bearing portion has a segment shape that forms a part of an annular ring, and includes a holding portion to which the bearing portion is inserted, and the shaft portion in a state in which the bearing portion is inserted to the holding portion It is desirable to have one end located on the opposite side to the rotational direction of the above, and have a pouring basin disposed outward of one end of the bearing in a state where the bearing is attached to the holding part. Specifically, the holding portion has an exposed surface which is located outward of one end of the bearing portion in a state where the bearing portion is mounted and is formed on the side on which the bearing portion is mounted. In a cross-sectional view intersecting the center line, it is preferable that the mounting portion be mounted in a state where it protrudes from one surface of the holding portion, and a reservoir portion is formed on the one surface of the holding portion. In this case, it is preferable that one surface of the holding portion has a surface that is inclined toward the sliding surface of the bearing portion.

The holding portion has an exposed surface which is located on the outside of one end of the bearing portion while the bearing portion is mounted and is formed on the side where the bearing portion is inserted and attached, and the sliding of the bearing portion The surface is inserted in a state of being positioned inward of one surface of the holding portion in a cross sectional view intersecting the center line, and a step is formed between the exposed surface of the holding portion and the sliding surface. It may be

Another specific aspect of the present invention is a rotating body having a shaft portion to which any of the sliding members for a sliding bearing device described above is attached integrally or separately, and the sliding member for a sliding bearing device The outer surface of the sliding surface has a substantially cylindrical shape, and a plurality of the groove portions are formed at the same pitch along the circumferential direction on the sliding surface. It is a body.

Here, it is preferable that a plurality of the groove portions be formed in the sliding surface in parallel or in a staggered manner in a direction along the center line.

Since the present invention is configured as described above, the object of the present invention can be achieved.

It is a figure which shows schematic structure of the molten metal plating apparatus with which the slide bearing which is the 1st aspect of this invention was integrated. It is a front view which is a cross-sectional view of a part of the sink roll and slide bearing of FIG. It is an expanded sectional view of the part of the slide bearing of FIG. FIG. 4 is a cross-sectional view taken along the line AA of FIG. It is an expanded view of B arrow of FIG.3 (b). It is C arrow line view of Fig.4 (a). It is the elements on larger scale of the groove part of Fig.4 (a). It is the elements on larger scale of the 1st modification of the slot of Drawing 4 (a). It is the elements on larger scale of the 2nd modification of the slot of Drawing 4 (a). It is the elements on larger scale of the 3rd modification of the slot of Drawing 4 (a). It is the elements on larger scale of the 4th modification of the slot of Drawing 4 (a). FIG. 5 is a cross-sectional view taken along the line F-F in FIG. 4A and is a conceptual diagram illustrating a generation state of dynamic pressure in the slide bearing. It is an expanded view of the 1st modification of the bearing part of Fig.4 (a). It is an expanded view of the 2nd modification of the bearing part of Fig.4 (a). It is the elements on larger scale of the groove part of Fig.8 (a). It is front sectional drawing of the slide bearing which is a 2nd aspect of this invention. FIG. 10 is a cross-sectional view taken along the line DD of FIG. 9 (a). It is front sectional drawing of the sink roll and slide bearing provided with the axial part which is the 3rd aspect of this invention. It is the elements on larger scale of the groove part of Fig.4 (a). It is a top view which shows schematic structure of the measuring apparatus which measures the friction loss coefficient of a 1st groove | channel or a 2nd groove | channel. 11 is a cross-sectional view taken along the line HH of FIG.

Hereinafter, the present invention will be specifically described with reference to a sliding member for a sliding bearing device, which is immersed in a hot-dip galvanizing bath, a hot-dip aluminum plating bath, or other hot-dip metal plating baths.

[Mold metal plating system]
First, a hot metal plating apparatus having a slide bearing device incorporating a slide bearing as an example of a slide member for a slide bearing device according to the present invention (hereinafter sometimes referred to as "sliding member"). The description will be made with reference to. As shown in FIG. 1, the molten metal plating apparatus 20 is immersed in a plating tank 22 in which a molten metal plating bath (hereinafter simply referred to as “plating bath”) 21 is stored and a surface layer portion of the plating bath 21. Snout 23 for preventing oxidation of the steel plate W introduced into the plating bath 21, the sink roll 27 disposed in the plating bath 21, and the upper side of the sink roll 27 within the plating bath 21. And a gas wiping nozzle 26 located slightly above the surface of the plating bath 21. The external driving force is not applied to the sink roll 27 itself, and is driven counterclockwise as shown by the arrow E by the frictional force due to the contact with the traveling steel plate W. The support roll 28 is also typically a drive roll connected to an external motor (not shown). There is also a non-drive type in which no external driving force is applied to the support roll 28. The sink roll 27 and the pair of support rolls 28, which are rolls for a molten metal plating bath, are each rotatably supported by the

slide bearings

1 and 1 attached to the

frames

24 and 25 and always integrated in the plating bath 21 integrally. Be soaked.

The steel plate W obliquely enters the plating bath 21 through the snout 23 and is allowed to change its traveling direction upward through the sink roll 27. The steel plate W rising in the plating bath 21 is sandwiched between the pair of support rolls 28, and the pass line is maintained, and warpage and vibration are prevented. The gas wiping nozzle 26 sprays high-speed gas onto the steel plate W coming out of the plating bath 21 and uniformly adjusts the thickness of the molten metal plating attached to the steel plate W by the gas pressure of the high-speed gas. Thus, the steel plate W to which the molten metal plating has been applied can be obtained. Here, due to the buoyancy in the plating bath 21 and the tension applied to the steel plate W, a force directed upward and leftward acts on the sink roll 27 as shown by the arrow G, and a slide bearing device for supporting the sink roll 27 The force to the upper left is to be loaded.

First Embodiment
The configuration of the sliding bearing 1 of FIG. 1 in which the sliding member of the first aspect is incorporated will be described with reference to FIGS. 2 to 4, 5 (a) and 6. Here, FIG. 2 is a front view showing a part of the sink roll and slide bearing of FIG. 1 in cross section, FIG. 3 (a) is an enlarged cross section of the slide bearing of FIG. 1 and FIG. 3 (b) is FIG. It is AA sectional drawing of (a). 4 (a) is a developed view of arrow B in FIG. 3 (b), FIG. 4 (b) is a arrow C in FIG. 4 (a), and FIG. 5 (a) is FIG. 4 (a). FIG. 6 is a cross-sectional view taken along the line F--F of FIG. 4A and is a conceptual view for explaining a generation state of dynamic pressure in the slide bearing. In addition, in FIG. 6, the sliding part 27c of the axial part not shown is also displayed in FIG. 4 (a) for understanding.

The slide bearing device is configured by a combination of the shaft portion 27b of the sink roll 27 and the slide bearing 1 including a bearing portion sliding with the shaft portion 27b, including the second and third embodiments described below. Although a slide bearing device for supporting a sink roll will be described below as an example, the slide bearing and the shaft portion incorporated in the slide bearing device can also be applied to a support roll. In addition, since the right side sliding bearing 1 and the left side sliding bearing 1 shown in FIG. 2 are the same, the configuration of the right side sliding bearing 1 will be described (a sliding bearing which is a sliding member of the second embodiment described below, The same applies to the shaft portion which is the sliding member of the third aspect).

[Sink roll, shaft part]
First, the sink roll 27 having the shaft portion 27b which is a sliding member constituting the slide bearing device will be described with reference to FIGS. 2 and 3 (a). As shown in FIG. 2, the sink roll 27 has a body 27a having a substantially cylindrical shape and an outer appearance having an outer peripheral surface with which a steel plate traveling in a plating bath contacts for direction change, and is coaxial with the body 27a. The disposed shaft portions 27 b extend from both ends of the trunk portion 27 a in a direction along the center line I of the trunk portion 27 a serving as the rotation center (hereinafter may be referred to as a center line direction). The shaft portion 27b is provided with a substantially cylindrical sliding portion 27c having an outer peripheral surface formed with a predetermined radius around the center line I on the opposite side to the trunk portion 27a in the center line direction. The outer peripheral surface is a sliding surface 27k that slides on the sliding surface 1k of the slide bearing 1. In FIG. 3A, reference numeral 27d denotes a thrust receiving portion for supporting the sink roll 27 in the center line direction. For smooth rotation of the sink roll 27, it is desirable that the end of the thrust receiving portion 27d be a convexly curved R surface as illustrated.

The material constituting the body 27a and the shaft 27b of the sink roll 27 is not particularly limited as long as it is a material having low chemical reactivity with the plating bath and high corrosion resistance, but as described in detail below, it is particularly suitable for the plating bath It is desirable to form the sink roll 27 with a ceramic excellent in corrosion resistance. On the other hand, ceramics have lower thermal conductivity and fracture toughness than metals. Therefore, when the sink roll 27 is made of ceramics, there is a possibility that the body 27a and the shaft 27b may be broken due to rapid heat and rapid cooling at the time of immersion in a plating bath heated to a high temperature and at the time of pulling up. is there. Therefore, in order to suppress the occurrence of an excessive temperature gradient due to rapid heating and rapid cooling, the body 27a and the shaft 27b are formed into a cylindrical body having a hollow portion as shown in the figure and a direction crossing the center line I of the body 27a In the following, it may be referred to as “radial direction.” It is preferable to use a form having a constant thickness, and for example, the outer peripheral surface or the inner peripheral surface of the shaft portion 27b and the corner portion of the end surface have a gentle R shape. It is desirable to do. In addition, the external appearance of the part which contacts a steel plate should just be substantially cylindrical shape, and the trunk | drum 27a should be set as appropriate shape in consideration of prevention of adhesion of slag in a plating bath, adjustment of rotation balance, etc. do it.

[Slide bearing]
Next, the slide bearing 1 in which a bearing portion, which is a sliding member constituting the slide bearing device, is incorporated with the shaft portion 27b will be described. The slide bearing 1 of the present embodiment has, as main components, a holding portion 1d attached to the tip of a pair of arms 24 extending into the plating bath 21 and a bearing portion 1a attached to the holding portion 1d. . The holding portion 1d formed of a metal such as stainless steel having relatively high corrosion resistance to the plating bath 21 is, as shown in FIG. It has a shaft insertion portion 1q extending from the bottom to the center. The shaft insertion portion 1q has a substantially semicircular upper surface on the load side of the force shown by the arrow G, and has a left side surface 1g and a right side surface 1s extending downward from both ends, and the shaft portion The sliding portion 27c of 27b is inserted into the shaft insertion portion 1q.

As shown in FIG. 3A, the substantially fan-shaped, segment-shaped bearing portion 1a having a quarter (a part) of a cross section in the radial direction is a quarter of the annular portion. The inner circumferential surface, which is the surface of the two ridges 1b, has a strip 1b, and serves as a sliding surface 1k that slides on the sliding surface 27k of the shaft 27b. The number of projections 1b may be one, but in order to prevent uneven wear of the sliding surface 1k in the centerline direction due to the inclination of the shaft 27b during operation, a plurality of projections should be provided. Is desirable. The sliding surface 1k of the bearing portion 1a formed around the center line I with a predetermined radius preferably has a radius larger by 1.0 to 3.0 mm than the sliding surface 27k of the sliding portion 27c. The plating bath 21 functions as a lubricating medium by being interposed at the sliding interface between the sliding

surfaces

1k and 27k.

Here, as shown in FIG. 3 (b), the shaft insertion portion 1q has a center line direction corresponding to the sectional view of the bearing portion 1a so as to open on the left side of the substantially semicircular upper surface 1r. A substantially fan-shaped concave groove 1p extending in the shape of a circle is formed. The bearing portion 1a inserted into and attached to the recessed groove 1p is fixed by the fixing member 1f from the center line direction, but in a fixed state, the sliding surface 1k of the bearing portion 1a is the upper surface 1r of the shaft insertion portion 1q. It is located more inward. In this manner, a step is provided between the sliding surface 1k of the bearing portion 1a and the upper surface 1r of the shaft insertion portion 1q, so that an arrow E is shown while sliding with the sliding surface 1k of the bearing portion 1a. A fixed gap is formed between the sliding surface (peripheral surface) 27k of the sliding portion 27c rotating in the direction, and the top surface 1r and both side surfaces 1g and 1s of the shaft insertion portion 1q. Then, with the rotation of the sliding portion 27c, the plating bath 21 present at the sliding interface between the sliding faces 1k and 27k is discharged into the gap, and the plating bath 21 present in the gap is the sliding face 1k. And 27 k sliding interface. In this way, the plating bath 21 present at the sliding interface between the sliding

surfaces

1k and 27k is successively replaced, so that, for example, high hardness micro foreign matter such as so-called dross which is a reactant of the plating bath 21 Staying at the interface is suppressed. By arranging the bearing portion 1a having a groove portion described later in this manner, the wear of the bearing portion 1a and the shaft portion 27b can be more effectively reduced.

In order to supply the plating bath 21 smoothly to the sliding interface between the sliding

surfaces

1k and 27k, it is preferable that a sufficient plating bath 21 be present in the previous stage of the bearing portion 1a, as shown in FIG. Plating outward in the circumferential direction of the end (one end) 1i of the bearing portion 1a located on the opposite side to the rotational direction of the sliding portion 27c indicated by E, that is, the flow direction E of the plating bath (lubricating medium) 21 It is preferable to provide a well portion 1 h for storing the bath 21. Specifically, the pouring basin 1h of this embodiment is held as described above with the exposed upper surface 1r formed outward in the circumferential direction of the end 1i of the bearing 1a attached to the holding portion 1d. It is a region defined by the end face 1i of the bearing portion 1a inserted and attached to the portion 1d and the sliding surface 27k of the sliding portion 27c, preferably the distance from the center line I is larger than the right side surface 1s It is arrange | positioned on the surface of the formed upper surface 1r. In order to supply the plating bath 21 more smoothly to the sliding interface, as shown in FIG. 3B, the upper surface 1r of the holding portion 1d is directed to the sliding surface 1k of the bearing portion 1a, preferably. It is desirable to form an inclined surface 1x which is inclined at an inclination angle of 5 to 85 degrees, preferably 30 to 60 degrees with respect to the horizontal direction.

In the slide bearing 1 of the present embodiment, although the bearing portion 1a is inserted and fixed in the recessed groove 1p provided in the holding portion 1d as described above, it enters the insertion gap between the recessed groove 1p and the bearing portion 1a Since the plating bath 21 is a molten metal, it may solidify after removing the slide bearing 1 from the plating bath 21 and may damage the bearing portion 1a. Therefore, a seal portion is provided to prevent the plating bath from entering the insertion gap between the bearing portion 1a and the recessed groove 1p, or a gap or a groove portion is provided so that the plating bath can be easily discharged when the slide bearing 1 is taken out. Is preferable.

In FIG. 3A, reference numeral 1e denotes a thrust receiver disposed at a position opposed to the end of the shaft portion 27b in a state where the sliding portion 27c is disposed in the shaft insertion portion 1q. The thrust receiver 1 e contacts the thrust receiver 27 d of the shaft portion 27 b of the sink roll 27 moving in the center line direction during operation to position the sink roll 27 in the center line direction.

Next, the configuration of the groove portion 1c formed in the sliding surface 1k of the slide bearing 1 will be described in detail with reference to FIG. 4, FIG. 5 (a) and FIG. As shown in FIG. 4A (the same applies to FIGS. 7 to 10 referred to in the following description) in which the groove 1c is hatched for easy understanding, the groove 1c of this embodiment is a first groove 1m, Each of the first groove 1m and the second groove 1n has a connecting recess 1L connecting the second groove 1n and the inner end (one end) of each of the first groove 1m and the second groove 1n The outer end (the other end) of the is an opening 1 u · 1 v having an open end. The “opening”, which is the outer end of the first groove 1m and the second groove 1n, refers to the direction along the flow direction of the plating bath flowing in the grooves (hereinafter referred to as “the opening”) In addition, the direction perpendicular to the flow direction of the plating bath may be called the latitudinal direction), which means a range of 10 mm from the other end (outer end) that is the open end, “Inner end portion” refers to a range of 10 mm from one end (inner end).

Specifically, although the groove portion 1c of this aspect is formed on the sliding surface 1k which is the inner peripheral surface of the protruding portion 1b, the groove portion 1t having a concave shape is formed on both sides of the protruding portion 1b in the center line direction. It is arranged. That is, as shown in FIG. 4 (b) which is a CC arrow view of FIG. 4 (a), the bearing portion 1a is disposed at one end of the sliding surface 1k in the center line direction and the sliding surface The first side 1x directly or indirectly intersects with 1k, and the second side 1y disposed at the other end of the sliding surface 1k and directly or indirectly intersecting with the sliding surface 1k The opening 1u of the first groove 1m has an open end opening to the first side 1x, and the opening 1v of the second groove 1n has an open end opening to the second side 1y . The

openings

1u and 1v of each of the first groove 1m and the second groove 1n thus arranged in the projection 1b each have an opening end through which the plating bath can directly flow into the groove 1c.

In addition, as shown in FIG. 4 (b), the connection recess is a concave that is connected at the inner end (one end) of each of the groove-shaped first groove and the second groove and that communicates with both grooves. It is an element. Specifically, as shown by hatching in FIG. 5 (a) which is an enlarged view of the groove 1c-1 of FIG. 4 (a) which is a plan view, the first groove 1m and the first groove 1m in the rotational direction E of the shaft Straight lines h5 and h6 drawn perpendicularly to the sides h1 and h2 so as to pass through the inner ends of the sides h1 and h2 present behind each of the second grooves 1n, and a region surrounded by the side surface of the groove portion 1c It is.

Then, in the case of the groove 1c of the present embodiment in which the sliding member constitutes the bearing portion 1a, as shown in FIG. 5A, in the rotation direction of the shaft portion indicated by the arrow E, the first groove 1m The

openings

1u and 1v of each of the second groove 1n and the second groove 1n are both disposed rearward of the connecting recess 1L. According to the groove portion 1c arranged in this manner, the

openings

1u and 1v of the first groove 1m and the second groove 1n are disposed rearward of the connecting recess 1L in the rotational direction of the shaft portion. Therefore, the flow of the plating bath (lubricating medium) flowing in the same direction so as to be dragged along with the rotation of the shaft in the rotation direction E is the opening of each of the

openings

1u and 1v as indicated by the arrows in the groove. It smoothly flows into the first groove 1m and the second groove 1n through the ends, and then merges at the connection recess 1L and flows out from the narrow gap of the sliding interface. Then, the flow speed of the plating bath changes rapidly in the connection recess 1L, a dynamic pressure is generated on the connection recess 1L, and the contact pressure with the bearing 1a is reduced by supporting the shaft by the dynamic pressure. The shaft will rotate.

As described above, the plating bath that has flowed into the groove 1c with the rotation of the shaft can easily flow into the first groove 1m and the second groove 1n through the

openings

1u and 1v, and a sufficient amount of plating bath is connected Join in the recess 1L. As a result, higher dynamic pressure is generated in the connection recess 1L as compared with the case where the outer ends of the first groove 1m and the second groove 1n are closed ends, which is the configuration of the prior art disclosed in Patent Document 1 above. Do.

On the other hand, by setting the outer end of each of the first groove 1m and the second groove 1n as the

openings

1u and 1v as described above, a plating bath having a sufficient flow rate flows into the groove 1c. The flow of the plating bath flowing in the first groove 1m and the second groove 1n may be disturbed, and the dynamic pressure generated in the connection recess 1L may become unstable. Therefore, on the surface of the groove portion 1c of this embodiment, as shown in FIG. 4 (b), the minute unevenness 1o is formed. According to the groove portion 1c in which the minute unevenness 1o is formed, the disturbance of the flow of the plating bath (lubricant medium) flowing in the groove portion 1c is small as shown in the following experimental example, and the dynamic pressure generated in the connection concave portion 1L is stabilized. It is possible to suppress the frictional wear due to the contact of the shaft portion and the bearing portion.

Furthermore, in order to effectively suppress the disturbance of the plating bath that has flowed into the groove portion 1c, the first flow of the liquid having a dynamic viscosity of 4890 St measured according to JIS Z8803 in the groove portion 1c. The friction loss coefficient of at least one of the groove 1m and the second groove 1n is desirably 0.01 to 0.05. This kinematic viscosity corresponds to the kinematic viscosity of a plating bath formed by melting metallic zinc or metallic aluminum which functions as a lubricating medium in the slide bearing of this embodiment. A plating bath heated to a high temperature may be used directly as a liquid to be subjected to the test, but oil, water, an organic solvent, etc. adjusted to have the above-mentioned dynamic viscosity at room temperature are used instead of the plating bath. It is also good.

The method of measuring the friction loss coefficient will be described with reference to FIG. 11 (a) which is a plan view showing a schematic configuration of the measuring apparatus and FIG. 11 (b) which is a HH cross-sectional view of FIG. 11 (a). . 11 (a) is a partially enlarged view of a developed view of a sliding surface 1k originally formed in an arc shape, as in FIG. 4 (a). Further, FIG. 11 shows the case of measuring the friction loss coefficient of the first groove 1m of the groove portion 1c, but the friction loss coefficient of the second groove 1n can be basically measured in the same manner.

As shown in FIG. 11A, the friction loss coefficient measuring device 70 is a stainless steel sealing member 70a disposed so as to include one groove portion 1c formed in the sliding surface 1k in plan view. A supply means 70d connected to the sealing member 70a via a conduit 70e connected to

connection ports

70g and 70h formed on both sides of the sealing member 70a so as to respectively communicate with the

openings

1u and 1v of the groove portion 1c ing. Here, specifically, the supply means 70d is stored in a tank that contains a liquid whose temperature and the like are controlled so that the liquid to be tested maintains a predetermined viscosity, and the pressure and flow rate are controlled. It is comprised from the pump etc. which supply a liquid at a predetermined flow rate.

As shown in FIG. 11B, the sealing member 70a has a top plate 70k arranged in the centerline direction, and

side plates

70L and 70m extending downward from both sides of the top plate 70k. The bottom surface 70f of the top plate 70k is disposed in intimate contact with the sliding surface 1k, and the inner surface of the

side plates

70L and 70m is disposed in intimate contact with the side surfaces 1x and 1y of the sliding surface 1k. Sealed by As described above, since the sliding surface 1k is originally in the shape of a circular arc, the bottom surface 70f of the top plate 70k is in the shape of a circular arc corresponding to the shape of the sliding surface 1k. Alternatively, a seal member such as an O-ring may be disposed at an appropriate position on the bottom surface 70f of the top plate 70k and the inner surface of the

side plates

70L and 70m to ensure sealing of the groove portion 1c.

As shown in FIG. 11, in the top plate 70k of the sealing member 70a, substantially

cylindrical connection ports

70i and 70j capable of communicating with the first groove 1m in a state where the sealing member 70a is disposed with respect to the groove portion 1c, The pressure gauges 70b and 70c are connected to the

connection ports

70i and 70j, respectively, at the ends of the first groove 1m. The two

pressure gauges

70b and 70c measure the pressure on the inlet side and the outlet side of the fluid flowing in the first groove 1m when the liquid is supplied from the supply means 70d and flows in the first groove 1m. It is a thing. Therefore, the pressure gauge 70b for measuring the pressure on the inlet side is a connection port 70i in which the distance M2 in the longitudinal direction from the outer end of the first groove 1m to the center is 5 mm, which is the center of the opening 1u. In the pressure gauge 70c for measuring the pressure on the outlet side, the longitudinal distance M2 from the inner end of the first groove 1m to the center is located at the center of the inner end (one end) It is connected and disposed at the 5 mm connection port 70j. The pressure gauges 70b and 70c used in the present measuring device 70 are not particularly limited, and may be appropriately selected from commercially available pressure gauges according to the liquid and other measurement conditions to be provided for measurement.

Furthermore, in the top plate 70k of the sealing member 70a, in a state where the sealing member 70a is disposed with respect to the groove portion 1c, a flow velocity meter 70n that measures the flow velocity of the liquid (fluid) flowing in the longitudinal center of the first groove 1m. Is arranged. The flow velocity meter 70 n used in the present measuring device 70 is not particularly limited and may be appropriately selected from commercially available flow velocity meters according to the liquid and other measurement conditions to be used for measurement, for example, using an ultrasonic wave velocity meter Can.

The measuring method by the measuring device 70 and the method of calculating the friction loss coefficient of the first groove 1m will be described. First, as described above, the sealing member 70a into which the pressure gauges 70b and 70c are incorporated is disposed with respect to the predetermined groove portion 1c having the first groove 1m to be measured. Then, the supply means 70d is activated at a predetermined flow rate and pressure to supply the liquid to be tested to the groove 1c. In order to obtain the friction loss coefficient with high accuracy, it is desirable to adjust the supply means 70d so that the flow velocity of the liquid flowing through the first groove 1m is in the range of 0.3 to 1.0 m / s. . Then, after the liquid flows in the groove 1c in the direction indicated by the symbol G in FIG. 11 (a), the pressure on the inlet side of the liquid flowing in the first groove 1m by the pressure gauges 70b and 70c ( P1) The pressure (P2) on the outlet side is determined, and the flow velocity (v) is determined by the flow meter 70n, and then the friction loss coefficient is calculated by the following equation.

(Formula 1)
Friction loss coefficient (λ) = (((P1-P2) × 2 g) / v ² ) × d
here,
P1: Inlet pressure (unit: MPa)
P2: Outlet pressure (unit: MPa)
g: Gravity acceleration (unit: m / s ² )
v: Flow velocity (unit: m / s)
d: Equivalent pipe diameter of first groove 1m (unit: m)
It is.

The equivalent pipe diameter d is calculated by the following equation. As in the first groove 1m of this embodiment, the groove depth gradually increases from the opening 1u toward the connection recess 1L, or the second modification described with reference to FIG. When the groove width is changing as in the case of the groove 2c of 1, if the cross-sectional dimension or the cross-sectional shape of the first groove 1m changes in the longitudinal direction, calculate the average value in the longitudinal direction for both S1 and S2 below. You can substitute that value.

(Formula 2)
d = (4 × S1) / S2
here,
S1: Cross-sectional area (unit: mm ² ) of the cross section divided by the bottom surface 70 f of the top plate 70 a and the first groove 1 m
S2: Length (unit: mm) around the cross section partitioned by the bottom surface 70f of the top plate 70a and the first groove 1m
It is.

Further, the arithmetic average roughness Ra according to JIS-B0601 of the surface of the groove portion 1c in which the minute unevenness 1o is disposed is desirably 0.3 to 15.0 μm. When the surface roughness Ra is less than 0.3 μm or more than 15.0 μm, the effect of the above-described micro unevenness 1 o may not be sufficiently exhibited in any case, and the effect of suppressing the wear may be low. In the case of a sliding member immersed in a molten metal plating bath heated to a high temperature as in the slide bearing 1 of the present embodiment, the surface roughness Ra of more than 15.0 μm results in unevenness. Because of the notch effect, cracks are likely to occur due to the action of thermal stress, which may lead to the breakage of the bearing portion 1a.

Furthermore, although it is sufficient if the minute asperity 1o is formed on the surface of at least one of the first groove and the second groove, it is desirable that the minute unevenness 1o be disposed on the entire groove 1c including the connecting recess 1L. In this case, it is preferable that the surface roughness of the groove 1c is gradually roughened from the

openings

1u and 1v toward the connecting recess 1L within the range of the surface roughness Ra, and the first groove 1m is formed. The arithmetic average roughness Ra according to JIS-B0601 of the surface of the opening 1u · 1v of the second groove 1n is 0.3 to 5.0 μm, and the inner end of the first groove 1m and the second groove 1n More preferably, the roughness Ra at one end portion) is 5.0 to 15.0 μm. If the surface roughness at the

openings

1u and 1v is rough, foreign matter such as dross contained in the plating bath in which the flow is disturbed immediately after flowing into the groove 1c is easily captured by the minute unevenness 1o, and the

openings

1u and 1v It is desirable to reduce the surface roughness Ra to 0.3 to 5.0 μm because there is a possibility of clogging. On the other hand, in order to stabilize the flow of the plating bath in the connecting recess 1L, the surface roughness Ra at the inner end (one end) of the first groove 1m and the second groove 1n is 5.0 to 15.0 μm. It is desirable to do. Furthermore, the surface roughness Ra of the connection recess 1L is also preferably 5.0 to 15.0 μm.

The micro-concavities and convexities 1o may be formed on either the bottom surface or the side surface of the groove portion 1c on the surface having a large contact area with the plating bath, but it is preferable to form them on both surfaces.

Next, the shape of the groove part 1c in the bearing part 1a which is a preferable aspect is demonstrated in detail. As shown to Fig.5 (a), the groove part 1c of this aspect has comprised substantially U-shape in planar view at the time of developing and seeing the sliding face 1k. Specifically, the linear first groove 1m, which is extended so that the cross-sectional shape in the short direction is substantially rectangular, and the groove width is the same, has a sliding surface 1k that is inclined downward to the right. A second groove 1n disposed on the left side and having the same groove width and groove depth as the first groove 1m is disposed on the right side of the sliding surface 1k so as to be inclined downward to the left. The two are in line symmetry with respect to a straight line F which divides. The connecting recess 1L having a substantially rectangular cross section connecting the inner end portions of the first groove 1m and the second groove 1n has an arc shape disposed rearward in the rotational direction E of the shaft portion. It has a side r1 and a side r2 having a circular arc shape disposed forward. In addition, the cross-sectional shape of the groove part 1c is not limited to a substantially rectangular shape, For example, it can be set as various shapes, such as a substantially semicircular shape, a substantially V shape, or a substantially U shape.

And in the rotational direction E of the shaft, the sides h1 and h2 present behind each of the first groove 1m and the second groove 1n are both ends of the side r1 of the connecting recess 1L at each inner end (one end) And the sides h3 and h4 present in front of each of the first groove 1m and the second groove 1n are joined to both ends of the side r2 of the connecting recess 1L at each inner end (one end), thereby There is no step on the side, that is, the side surface, and a groove portion 1c having a substantially U shape is formed in a plan view in which the plating bath flows smoothly, whereby disturbance of the flow of the plating bath flowing in the groove 1c can be reduced. From the same point of view, as shown in FIG. 4B, it is preferable that there is no step between the bottom surface of each of the first groove 1m and the second groove 1n, and the connection recess 1L and the bottom surface.

Here, the “sides” of the first groove and the second groove described above are the inner end (one end) and the outer end (the other end) of the side surfaces of the first groove and the second groove in plan view. And the straight line connecting the same (the same applies to the sides of the first groove and the second groove of the other form described below). Therefore, when the side surfaces are linear as in the first groove 1m and the second groove 1n shown in FIG. 5A, the upper edges of the side surfaces of the first groove 1m and the second groove 1n And the sides will match.

The groove width and groove depth of the first groove 1m and the second groove 1n are appropriately set, but, for example, when the curvature radius of the sliding surface 1k is 40 to 80 mm, the groove width is approximately 0.5 to The depth is about 2.0 mm, and the groove depth is about 0.1 to 0.5 mm. In addition, the groove width and the groove depth of the first groove and the second groove, and the width and the depth and the shape of the connection recess of the first groove and the second groove, including the following modified example and the second and third embodiments, are plated It refers to the size and shape in the direction perpendicular to the flow direction of the bath.

Here, in general, the groove width t1 and the groove depth of each of the first groove 1m and the second groove 1n are almost the same, but may be different. Furthermore, the lengths of the first groove 1m and the second groove 1n do not have to be the same, and may be different. Further, if each of the

openings

1u and 1v of the first groove 1m and the second groove 1n is disposed rearward of the connection recess 1L, the

openings

1u and 1v of the first groove 1m and the second groove 1n can be used. The inclination angles j1 and j2 based on the straight line F are not limited, but the crossing angles j1 and j2 are about 5 to 85 °, preferably about 30 to 60 °. Furthermore, the first groove 1m and the second groove 1n do not have to be disposed in line symmetry, and the inclination angles j1 and j2 may be different from each other.

The shape of the groove portion 1c in plan view is not limited to the substantially U shape shown in FIG. 5 (a), but may be the shape shown in FIGS. 5 (b) to 5 (e) which is the first to fourth modifications. Can. In FIGS. 5B to 5E, the same components as those of the groove portion 1c of FIG. 5A are denoted by the same reference numerals, and the detailed description thereof is omitted.

As shown in FIG. 5B, the groove portion 5c according to the first modification in which the above-mentioned micro unevenness is formed on the surface has a substantially V shape. That is, the linear first groove 5m extended so as to have the same groove width is disposed on the left side of the sliding surface 1k so as to incline downward to the right, and the groove width and the groove depth The second grooves 5n, which are identical to each other, are disposed on the right side of the sliding surface 1k so as to incline downward to the left. Then, in the groove portion 5c of this aspect, the connection concave portion 5L is formed by directly connecting the first groove portion 5m and the second groove portion 5n. Also in the substantially V-shaped groove portion 5c, as shown by hatching in FIG. 5B, the connection concave portion 5L is formed of each of the first groove 5m and the second groove 5n in the rotational direction E of the shaft portion. It becomes an area surrounded by straight lines h5 and h6 drawn perpendicularly to the side faces h1 and h2 and the sides of the groove 5c so as to pass through the inner ends of the sides h1 and h2 present behind.

In the groove portion 5c of the present embodiment, the inclination angles of the first groove 5m and the second groove 5n are different based on a straight line F dividing the sliding surface 1k into two in the central line direction. Therefore, in the rotational direction E of the shaft portion, the

openings

1u and 1v of each of the first groove 5m and the second groove 5n are both disposed rearward of the connecting recess 5L, but their positions are It is different. The

openings

1u and 1v of the first groove 5m and the second groove 5n are disposed rearward of the connecting recess 5L in the rotational direction E of the shaft also by the groove 5c. Since minute asperities are formed on the surface, the same function and effect as the groove portion 1c can be obtained.

As shown in FIG. 5C, the groove portion 6c according to the second modification in which the above-mentioned micro unevenness is formed on the surface has a substantially W shape. That is, the groove 6c has a pair of substantially V-shaped V-

grooves

6m and 6n arranged in line symmetry via a straight line F dividing the sliding surface 1k into two in the center line direction. The left V groove 6m has a left groove 6m-1 that slopes downward to the right and a groove 6m-2 that slopes to the left, of which the outer end is the opening 1u. Functions as a first groove. The right V groove 6n also has a left groove 6n-1 that slopes to the lower right and a groove 6n-2 that slopes to the lower left, of which the outer end is the opening 1v. -1 functions as a second groove. And, in the groove portion 6c of the present embodiment configured by a combination of substantially V-shaped

V groove portions

6m and 6n, the inner end portion (one end portion) of each of the first groove 6m-1 and the second groove 6n-1 Is an aspect of being indirectly coupled by the coupling recess 6L-1 or 6L-2.

This will be specifically described with the V groove 6m on the left side. As shown by the solid arrows in the groove, the plating bath flowing from the opening 1v of the second groove 6n-1 is the second groove 6n-. 1, the groove 6n-2 and the groove 6m-2 sequentially flow in the groove 6c, reach the left connection recess 6L-1, and flow from the opening 1u of the first groove 6m-1 and the connection It joins in the recessed part 6L, and generates a dynamic pressure. The same applies to the V groove 6n on the right side as indicated by the broken line arrow in the groove, and one groove 6c in this embodiment has two connection recesses 6L-1 and 6L-2 in the center line direction. It is possible to more effectively suppress the friction and wear of the shaft portion and the bearing portion.

As shown in FIG. 5D, the groove 8c according to the third modification in which the minute unevenness is formed on the surface is a first groove 1m and a second groove having the same shape and arrangement as the groove 1c. And a connecting recess 8L extending in the direction of the center line connecting the inner end of each of the first groove 1m and the second groove 1n. The

openings

1u and 1v of the first groove 1m and the second groove 1n are disposed rearward of the connecting recess 8L in the rotational direction E of the shaft also by the groove 8c. Since micro-concavities and convexities are formed on the surface, the same function and effect as those of the groove 1c can be obtained. Further, with respect to the groove shown in FIGS. Since the length is long, it is possible to more effectively suppress the friction and wear of the shaft portion and the bearing portion.

As shown in FIG. 5 (e), the groove portion 9c according to the fourth modification in which the above-mentioned micro unevenness is formed on the surface, is a first groove 9m and a second groove 9m in which both side surfaces are curved in plan view. There is a groove 9m, and the first groove 9m is disposed on the right side of the sliding surface 1k so as to incline downward to the left, and the second groove 9n is disposed on the left side of the sliding surface 1k so as to incline downward to the right It is done. Then, in the groove 9c of this embodiment, the first groove 9m and the second groove 9n are directly connected to each other as in the substantially V-shaped groove 5c shown in FIG. Is formed.

When the side surface is curved like the groove 9c, the range of the connection recess 9L is determined as follows. That is, in the rotational direction E of the shaft portion, the inner end (one end) and the outer end (the other end) of the rear side are connected by a straight line, and a side h1 is set, and the inner end and the outer end of the front side are straight Set the tie side h3. Further, the sides h2 and h4 which are straight lines are set similarly for the second groove 9n. Then, like the groove 5c of FIG. 5 (b), the connecting recess 9L of the groove 9c is formed by the first groove 9m and the first groove 9m in the rotational direction E of the shaft as shown by hatching in FIG. A straight line h5 · h6 drawn perpendicularly to the side faces h1 · h2 and an area surrounded by the side faces of the groove 9c so as to pass through the inner ends of the sides h1 · h2 present behind the respective grooves 9n . In addition, the same applies to the case where the side surface of the groove in a plan view is not linear but is curved or bent.

Next, an arrangement aspect of the groove part 1c in the bearing part 1a which is a preferable aspect will be described with reference to FIG. Even if one groove portion 1c of the above-mentioned shape is arranged on the sliding surface 1k, the effect of the present invention can be exhibited. However, it is preferable to arrange a plurality of groove portions 1c along the circumferential direction as follows. That is, as shown in FIG. 4 (a), in the bearing portion 1a of the present embodiment, two

ridges

1b and 1b are formed in the center line direction via the groove 1t, and the left ridge 1b Five grooves 1c-1 to 5 are provided on the sliding surface 1k, and five grooves 1c-6 to 10 are provided in parallel along the circumferential direction on the sliding surface 1k of the right projecting portion 1b. In FIG. 4A, the grooves 1c-1 to 5 and the grooves 1c-6 to 10 are arranged at equal intervals (angles), but they may be arranged at unequal intervals, and the grooves 1c- The groove width and groove depth of each of the first groove 1m and the second groove 1n of each of 1 to 5 and the groove portion 1c-6 to 10 and the crossing angle of both do not have to be all the same, It may be set appropriately in consideration of pressure distribution, dross retention and other conditions.

Furthermore, in the bearing portion 1a of this embodiment, the groove portions 1c-1 to 5 formed on the sliding surface 1k of the left projecting portion 1b and the groove portion 1c formed on the sliding surface 1k of the right projecting portion 1b. In the case of -6 to 10, when viewed from the center line direction, they are arranged in parallel, that is, the groove portions 1c serving as a pair are at the same position in the circumferential direction, and the connection recesses overlap. Hereinafter, the operation of the groove portion 1c having such an arrangement will be described with reference to FIG. 6 which is a cross-sectional view taken along the line FF of FIG. Note that, for the sake of understanding, FIG. 6 includes a sliding portion 27 c (not shown) in FIG. 4. Here, FIG. 6 is generated in each of the groove portions 1c-1 to 5 when the sliding surface 27k of the sliding portion 27c of the shaft portion rotates while sliding with the sliding surface 1k of the bearing portion 1a. It is a conceptual schematic diagram showing pressure distribution of dynamic pressure, and a diagram shown by numerals G1 to G5 shows sliding of dynamic pressure generated in each groove 1c-1 to 5 when the pressure value is in the radial direction. It is a pressure distribution in the surface 1k.

As shown in FIG. 6, when a load acts from the direction shown by the arrow G, the sliding surface 1k of the bearing portion 1a and the sliding surface 27k of the sliding portion 27c are in close contact with each other at a position X In the close groove portion 1c-3, the gap between the sliding interfaces 1w of the two is narrow, and dynamic pressure of a pressure distribution shown by a line G3 is generated. On the other hand, in grooves 1c-2 and 4 arranged at positions farther from position X than groove 1c-5 with respect to flow direction E of plating bath 21, the sliding interface 1w of sliding

surfaces

1k and 27k is The gap is wide, and a dynamic pressure is generated at a pressure whose maximum pressure is lower than the dynamic pressure G5, which is a pressure distribution shown by the diagrams of G2 and G4. Similarly, in the grooves 1c-1 and 5, the dynamic pressures G1 and G5 generated as they go away from the top X decrease. Here, even with only the dynamic pressure G3 generated in the groove 1c-3 provided in the vicinity of the position X, the sliding portion (shaft portion) 27c can be sufficiently supported to exert a lubricating effect. However, as in the bearing portion 1a of this embodiment, the sliding portion 27c is surrounded by the dynamic pressure G1 to G5 generated by the plurality of groove portions 1c-1 to 5 (1c-6 to 10) formed in the circumferential direction. For example, since the sliding portion 27c can be supported even when a large load or a fluctuating load is applied, it is preferable.

A developed view of the inner surface of a bearing 7a which is a first modification of the bearing 1a is shown in FIG. In the bearing 1a, as described above, the groove formed on the sliding surface of the left ridge and the groove formed on the sliding surface of the right ridge are viewed from the center line direction. The pair of groove portions are at the same position in the circumferential direction, and the connection recesses are arranged so as to completely overlap, but as shown in FIG. 7, they are arranged on the sliding surface 1k of the left ridge 1b. The grooves 7c-6 to 10 arranged on the sliding surface of the right ridge 1b with respect to the grooves 1c-1 to 5c are circumferentially shifted, and the connecting recesses of the grooves 1c are paired by L3 in the circumferential direction Even if 1 L partially overlaps, the same effect as described above can be obtained.

Next, the preferable cross-sectional shape of the groove part 1c is demonstrated with reference to FIG.4 (b). As shown in FIG. 4B, the groove depth of the groove portion 1c of this embodiment is the groove depth of the outer end (other end) of the

openings

1u and 1v of the first groove 1m and the second groove 1n. The groove depth of the inner end (one end) of the inner end portion of the first groove 1m and the second groove 1n is d2, and specifically, the bottom surface of the groove 1c so that d2> d1. Is formed to be inclined from the

openings

1 u and 1 v toward the connecting recess 1 L. Thus, by making the groove depth of the

openings

1 u and 1 v shallow, it is possible to suppress the inflow of minute foreign substances such as dross into the groove 1 c, which is preferable. The difference between the groove depths of the

openings

1u and 1v of the first groove 1m and the second groove 1n and the inner end is preferably about 0.2 to 0.5 mm. Alternatively, the inner end portions of the first groove 1m and the second groove 1n may be extended as it is, and the groove depth of the connection recess 1L may be deeper than the inner end portion.

As a ceramic which is a preferable material constituting the bearing portion 1a, alumina, zirconia, silica and other oxides are selected according to the thermal shock resistance, corrosion resistance and the like at the request of the atmosphere and other operating conditions in which the bearing portion 1a is used. Ceramics, zirconium boride, titanium boride, boron boride and other boride-based ceramics, silicon carbide, boron carbide and other carbide-based ceramics, or inorganic materials such as carbon may be used. And since the bearing part of this aspect is rapidly heated and rapidly cooled at the time of immersion to a plating bath and taking out, it is necessary to be excellent in thermal shock resistance. Therefore, silicon nitride, aluminum nitride and other nitride ceramics having high thermal conductivity are preferable as ceramics constituting the bearing portion, and they have high corrosion resistance and wear resistance to the molten metal which is a plating bath. Particularly preferred is a silicon nitride-based ceramic containing sialon excellent in high temperature strength. In the case where the shaft portion of the sink roll 27 of this embodiment is made of ceramics, the same applies to the slide bearing which is the sliding member of the second embodiment described below and the ceramics which constitutes the shaft portion which is the sliding member of the third embodiment. is there.

As a method of forming the groove portion 1c in the bearing portion 1a shown in FIG. 4, when the bearing portion 1a is made of metal, cutting, electric discharge machining, and other known processing methods can be applied. On the other hand, in the case where the bearing portion 1a is made of ceramic which is a hard-to-cut material, for example, a method of forming the groove portion 1c in a compact before sintering and then sintering it; It is possible to apply a method of forming a groove 1c by removing with a grindstone. However, as in the groove portion 1c of the present embodiment, when it is necessary to form the micro unevenness 1o on the surface, a mask having an opening corresponding to the groove portion 1c in the sliding surface 1k of the bearing portion 1a after sintering. To form grooves 1c by shot blasting, forming a groove 1c by irradiating the sliding surface 1k of the bearing 1a after sintering with a laser, preferably a fiber laser having a high energy density of a laser spot It is desirable to adopt a method such as a method that can easily create the minute unevenness 1 o.

The second modified example of the bearing 1a described with reference to FIG. 4 will be described with reference to FIG. 8 which is a developed view of the sliding surface 1k of the bearing 2a according to the second modified example. In FIG. 8, the same components as those of the slide bearing 1 and the shaft portion 27b of the first embodiment are given the same reference numerals, and the detailed description will be omitted (second and third embodiments described later) The same applies to the sliding members of

The bearing 2a according to the second modification has a substantially U-shaped groove 2c and is basically configured in the same manner as the bearing 1a, but the arrangement of the groove 2c and the first groove It differs from the bearing portion 1a in terms of the shapes of 1 m and the second groove 2n. First, the arrangement of the grooves 2c will be described. In the bearing 2a of the second modification, the grooves 2c-1 to 3 formed in the sliding surface 1k of the left ridge 1b and the grooves 2c formed on the sliding surface 1k of the right ridge 1b. -4 and 5 are arranged in a zigzag when viewed from the center line direction, that is, groove portions 2c-1 to 3 and 2c-4 and 5 are at different positions in the circumferential direction, The connection recess 1L of each groove 2c formed in each of the projecting

ridges

1b and 1b is arranged so as not to overlap.

Thus, according to the slide bearing having the bearing portions 2a in which the groove portions 2c are arranged in a staggered manner, the arrangement interval of the groove portions 2c in the circumferential direction is greater than the groove width of the first groove 2m and the second groove 2n. This is particularly effective when the size is small, in which case the dynamic pressure generated by the grooves 2c-1 to 3 formed in the left ridge 1b and the groove 2c-4 and 5 formed in the right ridge 1b are also effective. By combining with the generated dynamic pressure, the generation distribution of the dynamic pressure viewed from the centerline direction can be made similar to the distribution shown in FIG.

Next, the shapes of the first groove 2m and the second groove 2n according to the second modification will be described. The groove width t4 at the inner end of the inner end is narrower than the groove width t3 at the outer end of the opening 2u, and the groove width gradually narrows from the outer end toward the inner end. The second groove 2n is disposed on the left side of the sliding surface 1k so as to be inclined and has the same groove width and groove depth as the first groove 2m is disposed on the right side of the sliding surface 1k so as to be inclined downward to the left. Both are in a symmetrical relationship with respect to a straight line F which divides the sliding surface 1k into two in the center line direction. Then, in the rotational direction E of the shaft portion, the sides h1 and h2 present behind each of the first groove 2m and the second groove 2n are joined to both ends of the side r1 of the connecting recess 1L at each inner end The sides h3 and h4 present in front of each of the first groove 2m and the second groove 2n are joined to both ends of the side r2 of the connecting recess 1L at each inner end (one end), and one groove portion 2c is It is configured. Thus, the groove 2c of the bearing 2a according to the second modification has openings 2u and 2v having a groove width t3 wider than the groove width t4 of the inner end when viewed in a plan view. There is. By thus widening the opening width t3 of the openings 2u and 2v, it is possible to achieve smooth inflow of the plating bath into the groove 2c.

Second Embodiment
About slide bearing 3 which is a sliding member of the 2nd mode which constitutes a slide bearing device, Drawing 9 (a) which is a front sectional view, and Drawing 9 (b) which are DD sectional views of Drawing 9 (a) The description will be made with reference to. The sliding bearing 3 of the second aspect is different from the sliding bearing 1 of the first aspect in that the bearing portion 3a itself made of ceramic is the sliding bearing 3 and does not have a metal holding portion. The configurations of the sliding surface 1k and the groove 1c are basically the same.

As shown in FIG. 9 (a), the slide bearing 3 (bearing portion 3a) of the second embodiment in which the sectional view along the center line I is substantially U-shaped is formed at the center in the center line direction. It has a hollow portion 3b, and has two ridges 1b juxtaposed in the center line direction so as to project inwardly toward the hollow portion 3b. A plurality of groove portions 1c are formed at equal intervals along the circumferential direction of the sliding surface 1k on the sliding surface 1k, which is the inner peripheral surface of the annular ridge 1b. The sliding portion 27c is inserted from the left side in FIG. 9A into the hollow portion 3b having the sliding surface 1k whose inner diameter is larger than the outer diameter of the sliding portion 27c of the shaft portion.

As shown in FIG. 9 (a), the slide bearing 3 of this embodiment receives the end face of the shaft portion of the sink roll that moves in the horizontal direction during operation to receive the horizontal position. Although the portion 3d is disposed, the hollow portion 3b may be extended to the right end without providing the bearing end 3d. When the bearing end 3d is provided on the slide bearing 3 as described above, the left end of the hollow portion 3b to the bearing end 3d is used to prevent foreign matter such as dross from staying in the slide bearing 3. Providing a liquid reservoir 3c having a larger inner diameter than the hollow portion 3b and an opening 3f formed along the center line I so as to penetrate the bearing end 3d, which are disposed in the entire area Is preferred. With this configuration, even when the shaft is inserted into the slide bearing 3, the plating bath can freely move in and out of the liquid reservoir 3 c and circulate in the hollow portion 3 b.

Here, as shown in FIG. 9 (b), in the sliding bearing 3 of this embodiment, a plurality of groove portions 1c are provided for each section of the sliding surface 1k indicated by reference numerals F1 to F4 divided by an angle of 90 °. It is done. In addition, the shape and the arrangement position of the groove part 1c in each section may be the same or different. By providing the groove portion 1c in the sliding surface 1k for each section divided at an angle of 90 ° in this way, four sliding surfaces 1k divided for each section F1 to F4 can be used for operation. That is, when the operating conditions in the sections F1 to F4 are the same, the shapes and the arrangement positions of the grooves 1c in the sections F1 to F4 are the same, and when the wear of the sliding surface 1k of the section F1 advances due to use, If the sliding bearing 1 is rotated clockwise by 90 ° and the sliding surface 1k of the next section F2 is used and the sliding surface 1k of the section F2 wears, the sliding of the section F3 and then the section F4 is performed similarly. The moving surface 1k can be used, and the life of the slide bearing 3 can be extended, which is desirable. Further, when there are a plurality of different operating conditions, the positions of the sections F1 to F4 of the slide bearing 3 are changed by setting the shape and the arrangement position of the groove portion 1c in the sections F1 to F4 corresponding to the operating conditions. It is possible to cope with the change of the operating condition by simply carrying out the process and to reduce the number of the slide bearings 3, which is desirable from the viewpoint of cost.

Third Embodiment
The shaft portion 47b, which constitutes the slide bearing device and to which the sliding member of the third aspect is attached, will be described with reference to FIG. 10 which is a front sectional view thereof. As described in the first embodiment, the shaft 47b of the present embodiment, in which the two projections 47e, which are sliding members, are integrally attached via the recess 4t, on the other hand, sinks It is also the axial part 47b extended in the centerline direction from the both ends of the trunk | drum of a roll, and serves as the element which comprises a sink roll. In addition, although the axial part 47b of this aspect to which the protruding part 47e was integrally attached is comprised with the same ceramics as the protruding part 47e, at least the protruding part 47e which is a sliding member is comprised with ceramics It is enough if it is done. That is, the sliding member may be separately attached to the shaft. Specifically, a cylindrical body made of ceramics provided with a projecting portion may be fitted and fixed to a shaft made of metal, for example, and two annular projecting portions made of ceramic are prepared. For example, this may be inserted into and fixed to a shaft made of metal.

The slide bearing 4 (bearing portion 4a) of this embodiment basically has the same configuration as the slide bearing 1 of the slide bearing device described above, but no groove is formed on the sliding surface 1k. On the other hand, the shaft portion 47b rotating in the direction of the arrow E and having a cylindrical appearance as described above has the two ridges 47e juxtaposed in the center line direction so as to project on the outer peripheral surface thereof. doing. A plurality of grooves 4c are formed at equal intervals along the circumferential direction of the sliding surface 47k on the sliding surface 47k which is the outer peripheral surface of the two ridges 47e.

Here, as shown in FIG. 10 (b) which is an enlarged view of the groove 4c of FIG. 10 (a), the groove 4c of this embodiment is substantially U-shaped basically like the groove 1c of the first embodiment. The sliding member of this embodiment has the shaft portion, and the first groove 1m and the second groove 1n are formed in the rotation direction E of the shaft portion. Each of the

openings

1u and 1v is disposed forward of the connecting recess 1L. By arranging the

openings

1u and 1v in this manner, the plating bath flowing from the

openings

1u and 1v with the rotation of the shaft 47b flows toward the connection recess 1L as indicated by the arrow in the groove, and the connection recess Join at 1 L to generate dynamic pressure.

Furthermore, in the case where the groove portion 4c is provided in the shaft portion 47b as in the present embodiment, the dynamic pressure is continuous continuously at the sliding interface between the sliding surface 47k of the sliding unit 47c and the sliding surface 1k of the sliding bearing 4 Preferably, the grooves 4c are offset in the adjacent rows when viewed in the direction of the center line I, that is, the grooves 4c are arranged in a zigzag. Specifically, as shown in FIG. 10 (a), when the shaft 47b is viewed from the direction of the center line I, the left side in the circumferential direction so that the grooves 4c in adjacent rows do not overlap. It is preferable that the groove 4c of the protrusion 47e on the right side is disposed between the grooves 4c formed in the protrusion 47e. With the above configuration, when the shaft 47b rotates, dynamic pressure is continuously generated, and the shaft 47b is always supported by the dynamic pressure, and the sliding surface 27k is from the sliding surface 1k of the sliding bearing 4 Since the state is always separated, the rotation of the sink roll is stabilized, and it is possible to suppress the progress of the wear of the shaft portion 47b and the slide bearing 4 due to friction.

The shape, size, and arrangement of the groove 4c are arbitrary as in the case of the groove 1c in the slide bearing 1 as long as the above effects are exhibited. Further, the whole of the shaft portion 47b does not necessarily have to be a substantially cylindrical shape, as long as the portion where the sliding surface 47k corresponding to the sliding surface 1k of the slide bearing 4 is formed has a substantially cylindrical shape. . Therefore, as long as the slide bearing 4 can be rotatably supported, the shape of the shaft 47b in a cross-sectional view perpendicular to the center line I of the portion other than the sliding surface 47k has portions that do not constitute a circular shape. May be

[Example of experiment]
As shown in Table 1, in Experimental Examples 1 to 20 and 22 to 24, sliding parts were manufactured for the bearing portion of the slide bearing and for Experimental Example 21 for the shaft portion of the rotating body. The material of the bearing portion is a known Hitachi Sialon (material symbol: HCN10). Further, the material of the shaft portion of the sink roll is silicon nitride ceramics (material symbol: HSN70) made of Hitachi Metal which is well known, and the body portion is also made of the same material. The various properties of each are shown in Table 4.

In Experimental Examples 1 to 20 and 22 to 24 in which the object is a bearing part, bearing parts having the shapes shown in FIGS. 3A and 4A were manufactured, and the dimensions of each part are as follows: is there. The shaft portion sliding with the bearing portion was manufactured using the above-mentioned Hitachi Metals silicon nitride ceramics (material symbol: HSN70), and the radius thereof was 68 mm.
Radius of curvature of outer peripheral surface of bearing: 100 mm
Curvature radius of sliding surface 1k: 70 mm
Width (L1): 30 mm of the protrusion 1b
Width (L2) of central recess 1t: 10 mm
Width (L3) of recess 1t on both sides: 15 mm
Depth of each recess 1t (d3): 5 mm
Number of grooves 1c: 5 arrangement Angle of arrangement of grooves 1c Pitch: 5 °

Table 1 shows the shape in plan view of the groove portion and the dimensions of the first groove and the second groove prepared in each experimental example by the known sand blast method. In Experimental Examples 1 to 16 and 22 to 24, each of the first U-shaped groove 1c and the second U-shaped groove 1n in the rotational direction of the shaft portion has the substantially U-shaped groove 1c shown in FIG. The

openings

1u and 1v are both formed to be disposed rearward of the connection recess 1L. The crossing angle of each of the first groove 1m and the second groove 1n with the straight line F is 45 ° in each of Experimental Examples 1 to 13 and 22 to 24, and is 85 ° in each of Experimental Example 14; In Experimental Example 15, it was 30 °. Furthermore, in the experimental example 24, the positions of the outer ends of the sides h3 and h4 of the first groove 1m and the second groove 1n are set 5 mm inward from the side surfaces 1x and 1y of the protruding portion 1b. The outer ends of the first groove 1m and the second groove 1n were closed ends. In the numerical values shown in the column indicating the crossing angle, the numerical value described before "/" indicates the intersecting angle of the first groove 1m, and the numerical value described later indicates the intersecting angle of the second groove 1n. (It is the same in the following other experimental examples).

In Experimental Examples 17 to 20, groove portions having various shapes shown in FIGS. 5 (b) to 5 (d) and 8 (a) were formed. The groove widths and groove depths of the first groove and the second groove in the cross-sectional shape of the first groove and the second groove of Experimental Examples 17 to 20 and the cross-sectional shape in the short direction are substantially rectangular. As shown in

Here, in the experimental example 18 in which the substantially W-shaped groove portion 6c shown in FIG. 5C is formed, the intersection angle of the first groove 6m-1 with the groove 6m-2 and the second groove 6n-1 The crossing angle with the groove 6n-2 was 90 °, and the groove width and the groove depth of the grooves 6m-2 and 6n-2 were the same as the groove 6m-2 of the first groove 6m-1. Moreover, in Experimental example 19 which formed the groove part 8c shown in FIG.5 (d), the groove part 8c was formed so that the width | variety of the connection recessed part 8L might be 10 mm. Furthermore, in the experimental example 20 in which the groove 2c shown in FIG. 8B is formed, the groove width (t3) of the outer end of the opening 1u · 1v so that the groove width narrows from the opening 1u · 1v to the connecting recess 1L. The groove width (t4) of the inner end of the inner end was 2.0 mm.

In each of Experimental Examples 1 to 15, 17 to 19, and 22 to 24, the groove width of the first groove 1m and the second groove 1n having a substantially rectangular cross-sectional shape in the width direction is 2.0 mm, and the groove depth is The groove length (d1) of the outer end of the

openings

1u and 1v is 0.3 mm so that the groove depth is increased from the

openings

1u and 1v toward the connection recess 1L only in the experimental example 16; The groove depth (d2) of the inner end of the inner end portion was 0.5 mm. In each experimental example, the width and the depth of the connection recess are the same as the groove width and the groove depth of the inner end of the inner end of the first groove and the second groove.

In Example 21 in which the subject is a stem, a stem having the shape shown in FIG. 10A was manufactured. The dimensions of each part are as follows. In Experimental Example 21, each of the

openings

1u and 1v of the first groove 1m and the second groove 1n is the U-shaped groove 4c shown in FIG. 10 (b) in the rotational direction of the shaft. Both were formed to be disposed forward of the connecting recess 1L. The crossing angle of the first groove 1m and the second groove 1n of Experimental Example 21, the groove width and the groove depth of the first groove 1m and the second groove 1n are as shown in Table 1. As the bearing portion sliding with the shaft portion, a bearing portion of the same material and shape as the bearing portion used in Experimental Examples 1 to 16 and 22 to 24 was used except that there was no groove portion.
Radius of sliding surface 47k: 68 mm
Width (L5): 30 mm of protrusion 47e
Width of concave 4t (L6): 15 mm
Depth of recessed part 4t: 5 mm
Arrangement angle pitch of grooves 4c: 7 °

Except for Experimental Example 22, the size, material, processing conditions, etc. of the media used in sandblasting were adjusted and, if necessary, masking etc. were applied to adjust the surface roughness of the first groove, the second groove and the connection recess. The surface roughness of the opening and the inner end of the first groove and the second groove and the surface roughness of the connecting recess in each experimental example are shown in Table 2. In Experimental Example 1, both the first groove and the second groove were formed by grinding, and thereafter, only the opening and the inner end of the first groove were adjusted to have a predetermined roughness by sandblasting. In Experimental Example 22, both the first groove and the second groove were formed only by grinding. Here, the surface roughness is an arithmetic mean roughness Ra determined in accordance with JIS-B0601. With regard to the surface roughness of the opening and the inner end, both the first groove and the second groove have surfaces in the range set in the longitudinal direction in the range of 10 mm from the inner end of the outer end and the inner end of the opening The three arbitrary points of the above were measured with a laser type roughness measuring device (model: OLS 3000 manufactured by Olympus), and the average value was determined. In addition, the same was applied to the surface roughness of the connection recess. In the first and second grooves other than Experimental Examples 7 to 9, the surface roughness of the groove between the opening and the inner end is the surface roughness measured at the opening and the inner end. Within the range of In Experimental Examples 7 to 9, in both the first groove and the second groove, the surface roughness of the groove between the opening and the inner end changes continuously from the opening to the inner end. It was

Furthermore, the friction loss coefficient of the first groove and the second groove of each experimental example was determined using the friction loss coefficient measuring device 70 described with reference to FIG. In addition, in order to obtain | require the said coefficient, the mineral oil which adjusted dynamic viscosity measured based on JISZ8803 to 4890 St was used, and it supplied to the groove part at the flow velocity of 0.5 m / s. The friction loss coefficient confirmed in each experimental example is shown in Table 3.

A sliding bearing incorporating the bearing of each experimental example and a sink roll incorporating the shaft are both immersed in a hot dip galvanizing bath melted at 460 ° C., and the pressing force per unit area against the sliding surface is 98 MPa The rotation speed of the shaft portion was used at an average of 60 rpm. The amount of wear after one month of using the sliding surfaces of the bearing portion and the shaft portion of each experimental example is shown in Table 4. The amount of wear of the bearing portion is the difference between the height of the bottom surface of the recess 1t and the sliding surface 1k shown in FIG. 3A by the depth micrometer, the sliding surface before use and the sliding surface after one month of use Measured at various points in the circumferential direction and central axis direction in the above, and deducted the measured values at various places of the sliding surface after one month from the average value of measured values at various places of the sliding surface before use, and the maximum value among them It was the amount of wear of the bearing. In addition, the amount of wear on the shaft is the radius of the sliding surface before use and the sliding surface after 1 month of use, in micrometers, the circumference of the sliding surface before use and the sliding surface after 1 month of use Measured at various points in the axial direction and central axis direction, subtract the measured values at various points on the sliding surface after one month from the average values at various points on the sliding surface before use It was the amount of wear. In addition to the measurement by the depth micrometer and micrometer as described above, the amount of wear of the bearing and the shaft may be automatically measured using, for example, a laser-type length-measuring device disposed at a reference point. You may

As shown in Table 3, in the case of Experimental Example 22 where the friction loss coefficient of the first groove and the second groove is less than 0.01 and Experimental Example 23 where the friction loss coefficient is more than 0.05, the first groove and the second groove In the case of Experimental Example 24 in which the outer end of the groove was a closed end, the wear amount of the bearing portion exceeded 3.0 mm. On the other hand, in the case of Experimental Examples 1 to 21 in which the friction loss coefficient of at least one of the first groove and the second groove is in the range of 0.01 to 0.05, the wear amount of the bearing portion and the shaft portion Each became less than 3.0 mm.

Furthermore, from the viewpoint of surface roughness, in the cases of Experimental Examples 1 to 3 and Experimental Examples 12 and 13 exceeding 15.0 μm in which the surface roughness Ra is less than 0.3 μm, the wear amount of the bearing portion was also large. . On the other hand, in the case of Experimental Examples 4 to 11 and 14 to 21 in which the surface roughness Ra of the groove portion 1c is in the range of 0.3 to 15.0 μm, the bearing portion is compared with the above Experimental Examples 1 to 3 and 12/13. And the amount of wear on the shaft was relatively small. Furthermore, as shown in Experimental Examples 8 and 9, when the surface roughness Ra of the opening is near the lower limit and the surface roughness Ra of the inner end is in the range, the wear amount of the bearing is another experiment. It became smaller than the example. On the other hand, assuming that the surface roughness Ra of the opening is near the upper limit as shown in Experimental Example 7, slag may be trapped at the opening, and the opening may be slightly closed to reduce the flow rate of the plating bath. • The amount of wear on the bearing portion was relatively large compared to 9.

Furthermore, in the experimental examples 14 and 15 in which the crossing angle of the first groove and the second groove is changed, the surface roughness of the first groove, the second groove and the connection recess is almost equal to that of the experimental example 1. According to Experimental Examples 17 to 20 in which the shapes are variously changed, and Experimental Example 21 in which the object to which the sliding member is applied is the shaft portion, the first groove and the second groove are similar to the experimental examples 1 to 13 above. By setting the friction loss coefficient of the grooves in the range of 0.01 to 0.05, it was confirmed that the wear amount of the bearing portion or the shaft portion was reduced.

1 (3, 4) Slide bearing 1a (2a, 3a, 4a) Bearing portion 1b Projection portion 1c (2c to 9c) Groove portion 1h Water storage portion 1k Sliding surface 1L (2L to 9L) Coupling recess 1m First groove 1n Second groove 1u (1v, 2u, 2v) Opening 20 Molten metal plating apparatus 21 Molten metal plating bath 22 Plating tank 23 Snout 26 Wiping nozzle 27 Sink roll 27a Body 27b (47b) Shaft 27c (47c) Slide Moving part 47k Projection part 27k (47k) Sliding surface 28 Support roll E Flow direction of lubricating medium (plating bath) I Center line W Steel plate

Claims

A sliding member for a sliding bearing device having at least one sliding surface, which constitutes a bearing portion or a shaft portion of a sliding bearing device rotatably supporting a rotating body, comprising:
A groove portion having a first groove, a second groove, and a connection recess for directly or indirectly connecting one end of each of the first groove and the second groove, formed in the sliding surface. The other end of each of the first groove and the second groove is an opening having an open end,
When the sliding member for a sliding bearing device constitutes a bearing portion, each of the openings of each of the first groove and the second groove in the rotational direction of the shaft portion is formed by the connection recess portion. It is located at the rear,
In the case where the sliding member for a sliding bearing device constitutes a shaft portion, in the rotation direction of the shaft portion, each of the openings of each of the first groove and the second groove is formed by the connection concave portion. Located in front of the
The sliding member for a sliding bearing device, wherein minute asperities are formed on the surface of the groove.
The sliding member according to claim 1, wherein the groove portion has a substantially V shape, a substantially U shape, or a substantially W shape.
The coefficient of friction loss of at least one of the first groove and the second groove is 0.01 to 0.05 when flowing a liquid having a kinematic viscosity of 4890 St measured in accordance with JIS Z8803 in the groove portion. The sliding member for a sliding bearing device according to any one of claims 1 or 2.
The sliding member for a sliding bearing device according to any one of claims 1 to 3, wherein an arithmetic mean roughness Ra according to JIS-B0601 of the surface of the groove portion in which the minute unevenness is formed is 0.3 to 15.0 m. .
The sliding member for a sliding bearing device according to any one of claims 1 to 4, wherein the minute unevenness is formed on the surface of at least one of the first groove and the second groove.
The sliding member for a sliding bearing device according to any one of claims 1 to 5, wherein the minute unevenness is formed on the entire surface of the groove.
The sliding member for a sliding bearing device according to claim 6, wherein the surface roughness of the first groove or the second groove is roughened from the opening to the connection recess.
Arithmetic mean roughness Ra according to JIS-B0601 of the surface at the opening of the first groove or the second groove is 0.3 to 5.0 μm, and at one end of the first groove or the second groove The sliding member for a sliding bearing device according to claim 7, wherein the roughness Ra is 5.0 to 15.0 μm.
The sliding member according to any one of claims 1 to 8, wherein a depth of at least one of the first groove and the second groove is deeper from the opening toward the connecting recess. .
The sliding member according to any one of claims 1 to 9, wherein a groove width of at least one of the first groove and the second groove is narrowed from the opening toward the connecting recess.
The sliding member for a sliding bearing device according to any one of claims 1 to 10, wherein the sliding member is made of a ceramic.
A sliding bearing device in which the sliding member for a sliding bearing device according to any one of claims 1 to 11 is incorporated as a bearing portion, wherein the sliding surface has a plurality of the groove portions along the rotation direction of the shaft portion. A slide bearing characterized in that it is formed.
The slide bearing according to claim 12, wherein a plurality of the groove portions are formed in the sliding surface in parallel with a direction along the center line thereof.
The slide bearing according to claim 12, wherein a plurality of the groove portions are formed in a staggered manner in a direction along the center line of the sliding surface.
The bearing portion has a segment shape in which the sliding surface forms a part of an annular ring, and the bearing portion includes a holding portion to which the bearing portion is inserted. The bearing portion is inserted to the holding portion. In the state, it has one end located on the opposite side to the rotation direction of the shaft portion, and in the state where the bearing portion is mounted to the holding portion, it has a pouring basin disposed outside the one end of the bearing portion. The sliding bearing according to any one of Items 12 to 14.
The holding portion has an exposed surface which is located outward of one end of the bearing portion in a state where the bearing portion is mounted, and is formed on the side where the bearing portion is inserted and attached. The sliding surface is inserted in a state in which the sliding surface is positioned inward of one surface of the holding portion in a cross-sectional view intersecting the center line, and a pooling portion is formed on the one surface of the holding portion. Slide bearing according to 15.
The slide bearing according to claim 16, wherein one surface of the holding portion has a surface inclined toward the sliding surface of the bearing portion.
The holding portion has an exposed surface which is located outward of one end of the bearing portion in a state where the bearing portion is mounted, and is formed on the side where the bearing portion is inserted and attached. The sliding surface is inserted in a state of being positioned inward of one surface of the holding portion in a cross sectional view intersecting the center line, and between the one surface where the holding portion is exposed and the sliding surface The slide bearing according to any one of claims 12 to 14, wherein a step is formed.
A sliding member according to any one of claims 1 to 11, wherein the sliding member is a rotary member having a shaft portion integrally or separately attached, wherein the sliding member for a sliding bearing device is the sliding member. The rotating body is characterized in that the outer surface is an outer surface of a substantially cylindrical shape, and in the sliding surface, a plurality of the groove portions are formed at equal pitches along the rotation direction of the shaft portion. .
20. The rotating body according to claim 19, wherein a plurality of the grooves are formed in the sliding surface in parallel to a direction along the center line thereof.
20. The rotating body according to claim 19, wherein a plurality of the grooves are formed in a staggered manner in a direction along the center line of the sliding surface.