JP2006077864A - Shaft member for dynamic pressure type bearing device and manufacturing method thereof - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To recover the pressure balance in a thrust bearing gap formed on both sides in the axial direction of a flange part at its early stage, and to realize the above function at a low cast. <P>SOLUTION: In a common forging process, a shaft blank material 10 integrally having a shaft part 11 and a flange part 12 is formed, and simultaneously a through hole 19 opened to both end faces 12a, 12b is formed in the flange part 12 of the shaft blank material 10. As a result, the through hole 9 is formed to open on the inner diameter side from the bearing gaps W1, W2 away from the thrust bearing gaps W1, W2 formed on both end faces of the flange part 22 of the shaft member 2 as a finished product. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a shaft member for a hydrodynamic bearing device and a manufacturing method thereof. This bearing device is a spindle motor such as an information device, for example, a magnetic disk device such as an HDD, an optical disk device such as a CD-ROM, CD-R / RW, DVD-ROM / RAM, or a magneto-optical disk device such as MD or MO, It is suitable for polygon scanner motors of laser beam printers (LBP) and other small motors.

  In addition to high rotational accuracy, the various motors are required to have high speed, low cost, low noise, and the like. One of the components that determine the required performance is a bearing that supports the spindle of the motor. In recent years, the use of a hydrodynamic bearing having characteristics excellent in the required performance has been studied or actually used. Yes.

A dynamic pressure bearing is a member that rotatably supports a shaft member with pressure generated by a dynamic pressure action of fluid generated in a bearing gap, and is used by being incorporated in a spindle motor of a disk drive device such as an HDD. The In this type of hydrodynamic bearing device, a radial bearing portion that supports the shaft member in a non-contact manner so as to be rotatable in the radial direction and a thrust bearing portion that supports the shaft member in a non-contact manner so as to be rotatable in the thrust direction are provided. As a portion, a dynamic pressure generating groove (dynamic pressure groove) is formed on the inner peripheral surface of the bearing sleeve or the outer peripheral surface of the shaft member. Also, both end surfaces of the flange portion of the shaft member that constitutes the thrust bearing portion, or surfaces facing this (the end surface of the bearing sleeve, the end surface of the bottom member fixed to the housing, the inner bottom surface of the bottom of the housing, etc.) In addition, a dynamic pressure groove is formed (see, for example, Patent Document 1).
JP 2002-61641 A

Recently, in order to cope with an increase in information recording density and high-speed rotation in information equipment, the spindle motor for the information equipment has been required to have higher rotational accuracy. Higher rotational accuracy is also required for the hydrodynamic bearing device incorporated in the motor.

  By the way, in order to stably exhibit the rotational performance of the hydrodynamic bearing device over a long period, the radial bearing gap and the thrust bearing gap in which the fluid pressure for supporting the shaft member is generated must be managed with high accuracy. Is important. For example, when the thrust bearing gap is formed on both sides in the axial direction of the flange portion as described above, in order to stably maintain the thrust support state of the shaft member, It is necessary to balance between the pressure and the pressure for supporting the thrust on the other end surface side, and to avoid sliding contact between the end surface of the flange portion and the surface facing this as much as possible. The high precision of the thrust bearing gap can be achieved by machining the end face of the flange part facing this and the dynamic pressure groove, etc. with high precision, but simply increasing the machining precision leads to high costs. Therefore, it is not appropriate.

  An object of the present invention is to recover pressure balance in a thrust bearing gap formed on both axial sides of a flange portion at an early stage and to realize such a function at a low cost.

  In order to solve the above-mentioned problems, the present invention comprises a flange portion, and is non-contact supported in the thrust direction by the pressure generated by the dynamic pressure action of the fluid generated in the thrust bearing gap on both sides in the axial direction of the flange portion. A shaft member for a hydrodynamic bearing device is provided in which through holes are formed in both end surfaces of the flange portion, and the inner periphery of the through hole is a plastic processed surface.

  As described above, in the present invention, since the through holes that are open on both end faces are formed in the flange portion, if for some reason the fluid pressure in the thrust bearing gap on the one end side in the axial direction increases extremely, the flange portion A fluid (for example, lubricating oil) flows into the thrust bearing gap on the other axial end side through the formed through hole. As a result, the pressure balance in both thrust bearing gaps can be recovered quickly, and each thrust bearing gap can be maintained at an appropriate width to prevent sliding friction between the end face of the flange portion and the face facing it. it can.

  As a method for forming the through hole in the flange portion, for example, cutting is conceivable. However, if the cutting is performed, the cycle time is long, the processing efficiency is lowered, and the cost is increased. Further, in the cutting process, generation of chips is unavoidable, and this may be mixed in the fluid as contamination. In order to prevent this, the shaft member must be cleaned separately after cutting, resulting in an increase in cost. In particular, in the hydrodynamic bearing device used for the information equipment, the diameter of the flange portion is several mm, and the through hole has an ultra-small diameter of several tens to several hundreds μm correspondingly. In this case, it is not easy to completely remove the chips after the cutting process, and therefore, a careful cleaning process or the like is required, and cost increase is inevitable.

  On the other hand, plastic working represented by forging generally has a shorter cycle time than cutting and can be processed with high efficiency. Further, unlike the cutting process, no chips are generated, so that a cleaning process is not necessary. Therefore, if the through hole is formed by plastic working, the forming cost can be greatly reduced. In this case, the inner circumference of the through-hole is a plastic-worked surface, but the surface of the plastic-worked surface has good surface roughness, so that the fluid in the through-hole can be obtained without special post-processing. Smooth distribution can be ensured.

  The through hole is desirably formed in the vicinity of the shaft portion. By forming a through hole in the vicinity of the shaft part, a fluid flow path between the two thrust bearing gaps is also secured on the inner diameter side of the flange part. In combination with the flow passage (annular clearance between the outer peripheral surface of the flange portion and the inner peripheral surface of the housing), the function of adjusting the pressure balance between the two thrust bearing gaps can be enhanced. From this point of view, it is desirable to open the through hole on the inner diameter side of the radial center of the thrust bearing gap. In this case, in order to prevent the so-called escape of the dynamic pressure, the through hole is located at a position (inner diameter side of the thrust bearing gap) avoiding the thrust bearing gap between the formation region of the dynamic pressure groove and the surface facing it. It is desirable to make it open. If it is difficult to open at this position due to space constraints or the like, it may be opened at a position over the thrust bearing gap. However, even in this case, it is desirable to avoid the escape of dynamic pressure as much as possible.

  The shaft member for the hydrodynamic bearing device includes, for example, a shaft member, a bearing sleeve in which the shaft member is inserted into the inner periphery, and a fluid generated in a radial bearing gap between the outer periphery of the shaft portion and the inner periphery of the bearing sleeve. A radial bearing that generates non-contact support in the radial direction by generating pressure by the dynamic pressure action of the shaft, and a thrust generated by the dynamic pressure action of fluid generated in the thrust bearing gap at one end of the flange. A first thrust bearing portion that is supported in a non-contact manner in a direction, and a second thrust bearing portion that generates a pressure by a dynamic pressure action of a fluid generated in a thrust bearing gap at the other end of the flange portion to support the flange portion in a non-contact manner in the thrust direction. Can be provided as a hydrodynamic bearing device.

  A dynamic pressure groove for generating a dynamic pressure action of fluid is formed asymmetrically in the axial direction on one of the outer peripheral surface of the shaft portion facing the radial bearing gap and the inner peripheral surface of the bearing sleeve facing this outer peripheral surface. Then, a fluid flow in the axial direction occurs in the radial bearing gap. If this flow is directed to the flange, it is possible to avoid the generation of negative pressure inside the bearing device, and the high pressure generated by pushing into the flange is balanced by the pressure balance adjustment function using the through holes. It becomes.

  The hydrodynamic bearing device can also be provided as a motor including a hydrodynamic bearing device, a rotor magnet, and a stator coil.

  The present invention also provides a shaft member for a hydrodynamic bearing device that includes a shaft portion and a flange portion, and is supported in a non-contact manner in the thrust direction by a dynamic pressure action of a fluid generated in a thrust bearing gap on both axial sides of the flange portion. A manufacturing method is provided, in which a shaft portion and a flange portion are integrally forged, and through holes that are open on both end surfaces of the flange portion are forged, and these forgings are performed simultaneously. And

  According to the present invention, when the shaft member rotates, the pressure balance in the thrust bearing gaps formed on both axial sides of the flange portion can be recovered quickly, and the thrust bearing gaps can always be maintained at a predetermined interval. As a result, the rotational performance of the bearing can be stably exhibited over a long period of time. Further, such a function can be obtained at a low cost, and the mass productivity can be dramatically improved.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 2 conceptually shows a configuration example of a spindle motor for information equipment incorporating the fluid dynamic bearing device 1 according to one embodiment of the present invention. This spindle motor for information equipment is used in a disk drive device such as an HDD, and includes a hydrodynamic bearing device 1 that rotatably supports a shaft member 2 in a non-contact manner, a disk hub 3 attached to the shaft member 2, For example, a stator coil 4 and a rotor magnet 5 which are opposed to each other via a gap in the radial direction, and a bracket 6 are provided. The stator coil 4 is attached to the outer periphery of the bracket 6, and the rotor magnet 5 is attached to the inner periphery of the disk hub 3. The bracket 6 has the hydrodynamic bearing device 1 mounted on the inner periphery thereof. The disk hub 3 holds one or more disk-shaped information recording media (hereinafter simply referred to as disks) D such as a magnetic disk on the outer periphery thereof. In the spindle motor for information equipment configured as described above, when the stator coil 4 is energized, the magnetic force between the stator coil 4 and the rotor magnet 5 causes the rotor magnet 5 to rotate. The disk D held by the hub 3 rotates integrally with the shaft member 2.

  FIG. 3 shows an example of the hydrodynamic bearing device 1. The hydrodynamic bearing device 1 mainly includes a housing 7 having a bottom 7b at one end, a bearing sleeve 8 fixed to the housing 7, a shaft member 2 inserted into the inner periphery of the bearing sleeve 8, and a seal member 9. Configured as a simple component. For convenience of explanation, the following description will be made with the bottom 7b side of the housing 7 as the lower side and the side opposite the bottom 7b as the upper side.

  As shown in FIG. 3, the housing 7 is positioned on one side of the side portion 7a and the side portion 7a formed in a cylindrical shape with a resin material such as LCP, PPS, or PEEK, and is formed of, for example, a metal material. And a bottom portion 7b. In this embodiment, the bottom portion 7b is formed as a separate body from the side portion 7a, and is retrofitted to the lower inner periphery of the side portion 7a. In the partial annular region of the upper end surface 7b1 of the bottom 7b, a dynamic pressure groove having a spiral shape, for example, is formed as a dynamic pressure generating portion, although illustration is omitted. In this embodiment, the bottom portion 7b is formed separately from the side portion 7a and is fixed to the lower inner periphery of the side portion 7a. However, the bottom portion 7b can be integrally molded with the side portion 7a, for example, with a resin material. . At that time, the dynamic pressure groove provided in the upper end surface 7b1 can be molded simultaneously with the injection molding of the housing 7 composed of the side portion 7a and the bottom portion 7b, thereby eliminating the trouble of separately forming the dynamic pressure groove in the bottom portion 7b. It can be omitted.

  The bearing sleeve 8 is formed in a cylindrical shape with a porous body made of sintered metal, in particular, a sintered metal porous body mainly composed of copper, and is fixed at a predetermined position on the inner peripheral surface 7 c of the housing 7. The

  A dynamic pressure groove as a dynamic pressure generating portion is formed on the entire inner surface 8a of the bearing sleeve 8 or a partial cylindrical surface region. In this embodiment, for example, as shown in FIG. 4 (a), herringbone-shaped dynamic pressure grooves 8a1 and 8a2 are formed at two positions apart from each other in the axial direction. In the formation region of the upper dynamic pressure groove 8a1, the dynamic pressure groove 8a1 is formed to be axially asymmetric with respect to the axial center m (the axial center of the upper and lower inclined groove regions). The axial dimension X1 of the upper region is larger than the axial dimension X2 of the lower region. Accordingly, when the shaft member 2 rotates, the lubricating oil in the radial bearing gap is pushed downward by the asymmetric dynamic pressure groove 8a1.

  One or a plurality of axial grooves 8b1 are formed on the outer peripheral surface 8b of the bearing sleeve 8 over the entire axial length. In this embodiment, three axial grooves 8b1 are formed at equal intervals in the circumferential direction.

  For example, a spiral-shaped dynamic pressure groove 8c1 shown in FIG. 4B is formed as a dynamic pressure generating portion on the entire lower surface 8c of the bearing sleeve 8 or a partial annular region.

  As shown in FIG. 3, the seal member 9 as a sealing means is formed of a soft metal material such as brass, other metal materials, or a resin material separately from the housing 7 and formed in an annular shape. It is fixed to the inner periphery of the upper part of 7a by means such as press fitting or adhesion. In this embodiment, the inner peripheral surface 9 a of the seal member 9 is formed in a cylindrical shape, and the lower end surface 9 b of the seal member 9 is in contact with the upper end surface 8 d of the bearing sleeve 8.

  For example, as shown in FIG. 1, the shaft member 2 is formed of a metal material such as stainless steel and has a T-shaped cross section integrally including a shaft portion 21 and a flange portion 22 provided at the lower end of the shaft portion 21. . On the outer periphery of the shaft portion 21, as shown in FIG. 3, radial bearing surfaces 23a and 23b facing the formation regions of the two dynamic pressure grooves 8a1 and 8a2 formed on the inner peripheral surface 8a of the bearing sleeve 8 are axially arranged. Two places are formed apart from each other. Above one of the radial bearing surfaces 23a, a tapered surface 24 that gradually decreases in diameter toward the tip of the shaft is formed adjacently, and a cylindrical surface 25 that serves as a mounting portion of the disk hub 3 is further formed thereabove. . Between the two radial bearing surfaces 23a, 23b, between the other radial bearing surface 23b and the flange portion 22 and between the tapered surface 24 and the cylindrical surface 25, annular nuisance portions 26, 27, 28 are respectively provided. Is formed.

  For example, as shown in FIG. 3, a thrust bearing surface 22a facing the thrust bearing gap of the first thrust bearing portion T1 is formed on the upper end surface of the flange portion 22, and the lower end surface of the flange portion 22 is shown in FIG. As shown, a thrust bearing surface 22b that faces the thrust bearing gap of the second thrust bearing portion T2 is formed. Further, in this embodiment, on the inner diameter side of the flange portion 22 (in the vicinity of the shaft portion 21), openings are formed on both end surfaces of the flange portion 22 at locations on the inner diameter side of the thrust bearing surfaces 22a and 22b on both end surfaces of the flange portion 22. A through-hole 29 is formed.

  Between the taper surface 24 of the shaft portion 21 and the inner peripheral surface 9a of the seal member 9 facing the taper surface 24, an annular seal whose radial dimension gradually increases from the bottom 7b side of the housing 7 upward. A space S is formed. In the hydrodynamic bearing device 1 (see FIG. 3) after the assembly is completed, the inner space of the housing 7 including the radial bearing gap and the thrust bearing gap is all filled with lubricating oil, and the oil level is within the range of the seal space S. Kept.

  In the dynamic pressure bearing device 1 configured as described above, when the shaft member 2 is rotated, the formation regions (upper and lower two places) of the dynamic pressure grooves 8a1 and 8a2 of the bearing sleeve inner peripheral surface 8a, and the dynamic pressure grooves 8a1, In the radial bearing gap between the radial bearing surfaces 23a and 23b of the shaft portion 21 respectively facing the formation region 8a2, pressure due to the dynamic pressure action of the lubricating oil is generated, and the shaft portion 21 of the shaft member 2 moves in the radial direction. It is rotatably supported in a non-contact manner. As a result, the first radial bearing portion R1 and the second radial bearing portion R2 that support the shaft member 2 in a non-contact manner so as to be rotatable in the radial direction are formed. Further, a first portion between the dynamic pressure groove 8c1 region formed on the lower end surface 8c of the bearing sleeve 8 and the thrust bearing surface 22a on the upper side (shaft side) of the flange portion 22 facing the dynamic pressure groove 8c1 region. Thrust bearing clearance W1 (see FIG. 3), and a dynamic pressure groove region formed on the upper end surface 7b1 of the bottom portion 7b, and a thrust bearing surface on the lower side (on the opposite shaft side) of the flange portion 22 facing this dynamic pressure groove region In the second thrust bearing gap W2 (see FIG. 3) between the shaft member 2 and the second thrust bearing gap W2 (see FIG. 3), the pressure due to the dynamic pressure action of the lubricating oil is generated, and the flange portion 22 of the shaft member 2 is supported in a non-contact manner so The Thereby, the 1st thrust bearing part T1 and the 2nd thrust bearing part T2 which support the shaft member 2 in a non-contact manner so as to be rotatable in the thrust direction are formed.

  When the shaft member 2 rotates, the lubricating oil circulates between the radial bearing gap, the thrust bearing gaps W1 and W2, or the inside of the porous bearing sleeve 8, and lubrication for supporting the shaft member in each bearing gap. Oil is supplied as appropriate, but for some reason, the oil circulation may be disturbed. Even in that case, the through-hole 29 provided in the flange portion 22 adjusts the pressure balance between the thrust bearing gaps W1 and W2, so that one thrust bearing gap (first thrust bearing gap W1) and the other The thrust bearing gap (second thrust bearing gap W2) can be maintained at appropriate intervals. Thereby, the shaft member 2 can be stably thrust-supported, and such bearing performance can be stably exhibited over a long period of time.

  Hereinafter, the manufacturing method of the shaft member 2 which comprises the said dynamic-pressure bearing apparatus 1 is demonstrated.

  The shaft member 2 is manufactured mainly through two steps of (A) forming step and (B) grinding step. Of these, the forming step (A) includes shaft material forming processing (A-1), through-hole forming processing (A-2), and shaft portion correction processing (A-3). The grinding process (B) includes a width grinding process (B-1), a whole surface grinding process (B-2), and a finish grinding process (B-3).

(A) Molding step (A-1) Shaft material molding process and (A-2) Through hole molding process First, a metal material such as stainless steel, which is a material of the shaft member 2 to be molded, is used with a mold. For example, by compression molding in cold (forging), for example, as shown in FIG. 5, a shaft portion corresponding region (hereinafter simply referred to as a shaft portion) 11 and a flange portion corresponding region (hereinafter simply referred to as a flange portion). The shaft material 10 having 12 integrally is formed (shaft material forming process (A-1)). Moreover, the metal mold | die used for the forge molding of this shaft raw material 10 serves as the metal mold | die for shape | molding the through-hole 19 in the flange part 12 in this embodiment. Therefore, by compressing the metal material with this mold, the shaft blank 10 is forged and formed at the same time as the inner diameter side of the flange portion 12 (in the vicinity of the shaft portion 11), as shown in FIG. A through-hole 19 is formed to penetrate between the shaft-side end surface 12a of the flange 12 and the non-shaft-side end surface 12b (through-hole forming process (A-2)).

  In this way, by forming the through-hole 19 in the flange portion 12 by forging, the generation of chips and the like accompanying the processing is avoided, and the cleaning step after processing is omitted or simplified. be able to. Further, the forming of the through hole 19 and the forming of the shaft material 10 integrally provided with the shaft portion 11 and the flange portion 12 are both forged and performed simultaneously, thereby simplifying the processing step and reducing the processing time. Can be greatly shortened.

  As a method of cold forging in the forming step, any of extrusion processing, upsetting processing, heading processing, or the like, or a combination thereof can be adopted. In the illustrated example, the outer peripheral surface 11a of the shaft portion 11 after forging has a different-diameter shape with a tapered surface 14 and a tapered surface 14 continuous upward and a cylindrical surface 15 having a smaller diameter than other portions. The tapered surface 14 may be omitted and the uniform diameter may be formed over the entire length. In addition, although this embodiment demonstrated the case where shaping | molding of the shaft raw material 10 and shaping | molding of the through-hole 19 were simultaneously performed by the forging process, it is not necessary to perform both processes simultaneously, and the shaft raw material 10 was forged. Later, the through hole 19 may be formed by forging.

(A-3) Shaft part straightening processing The shaft part 11 of the shaft material 10 formed by forging in the previous step is pressed with, for example, a pair of rolling dies (for example, a flat die or a round die). By sandwiching and reciprocating the pair of rolling dies in opposite directions, the outer peripheral surface 11a of the shaft portion 11 is subjected to rolling processing for cylindricity correction (shaft portion correction processing (A-3)). ). Thereby, the cylindricity of the surface 13 subjected to the correction processing in the shaft outer peripheral surface 11a of the shaft material 10 is improved within a required range (for example, 10 μm or less). As the cylindricity correction processing, various processing methods such as rolling processing, sizing processing by drawing, ironing, or split-type press (pinching) can be employed. Further, the correction processing is performed over the entire length of the outer peripheral surface 11a of the shaft portion 11, and is performed only on a part of the outer peripheral surface 11a as long as the portion corresponding to the radial bearing surfaces 23a and 23b of the shaft member 2 as a finished product is included. You can also

(B) Grinding Step (B-1) Width Grinding Surface Surfaces that have been subjected to the above-mentioned correction processing on the shaft end face 11b and the opposite end face 12b of the flange 12 that are both end faces of the shaft material 10 that has undergone the forming process. Grinding with reference to 13. For example, as shown in FIGS. 6A and 6B, the grinding device 40 used in this grinding process includes a carrier 41 that holds a plurality of shaft materials 10 as workpieces, and a shaft material 10 that is held by the carriers 41. A pair of grindstones 42 and 42 for grinding the shaft end face 11b and the opposite end face 12b of the flange 12 are provided.

  As shown in the drawing, a plurality of notches 43 are provided at equal pitches in the circumferential direction in a partial region in the circumferential direction of the outer peripheral edge of the carrier 41. The shaft material 10 is accommodated in the notch 43 in a state in which the straightened surface 13 is in angular contact with the inner surface 43 a of the notch 43. The straightened surface 13 of the shaft material 10 protrudes slightly from the outer peripheral surface of the carrier 41, and a belt 44 is stretched on the outer diameter side of the carrier so as to constrain the protruding portion of the shaft material 10 from the outer diameter side. Has been. For example, as shown in FIG. 7, a pair of grindstones 42 and 42 face each other (grinding surfaces) at predetermined intervals on both ends in the axial direction of the carrier 41 in which the shaft material 10 is accommodated in the notch 43. Coaxially arranged.

  As the carrier 41 rotates, the shaft material 10 is sequentially put into the notch 43 from a fixed position. The thrown shaft material 10 traverses from the outer diameter end to the inner diameter end on the end faces of the rotating grindstones 42 and 42 in a state where the dropping from the notch 43 is restrained by the belt 44. Along with this, both end faces of the shaft blank 10, in other words, the shaft end face 11b and the opposite end face 12b of the flange 12 are ground by the end faces of the grindstones 42, 42 (see FIG. 7). At this time, since the straightened surface 13 of the shaft material 10 is supported by the carrier 41 and the straightened surface 13 has a high degree of cylindricity, the perpendicularity between the rotation axis of the grindstone 42 and the ground surface of the grindstone 42 in advance, If the parallelism between the rotational axis of the grindstone 42 and the rotational axis of the carrier 41 is managed with high accuracy, the both end surfaces 11b and 12b of the shaft material 10 are highly accurate with reference to the straightened surface 13. The squareness value with respect to the straightened surface 13 can be kept small. Moreover, the axial direction width | variety (full length including the flange part 12) of the shaft raw material 10 is finished to a predetermined dimension.

(B-2) Whole surface grinding process Next, the outer peripheral surface 10a of the shaft blank 10 and the flange portion 12 of the shaft blank 10 are determined with reference to both end faces of the ground shaft blank 10 (shaft end face 11b, opposite end face 12b of the flange 12). The shaft side end surface 12a is ground. A grinding apparatus 50 used in this grinding process performs plunge grinding with a grindstone 53 while pressing a backing plate 54 and a pressure plate 55 against both end surfaces of the shaft material 10 as shown in FIG. The straightened surface 13 of the shaft material 10 is rotatably supported by a shoe 52.

  The grindstone 53 is a general-purpose grindstone provided with a grinding surface 56 corresponding to the outer peripheral surface shape of the shaft member 2 as a finished product. The grinding surface 56 includes a cylindrical grinding portion 56a that grinds the outer peripheral surface 11a over the entire axial length of the shaft portion 11 and the outer peripheral surface 12c of the flange portion 12, and a surface grinding portion 56b that grinds the shaft portion side end surface 12a of the flange portion 12. And. The grindstone 53 in the illustrated example includes, as a cylindrical grinding portion 56a, portions 56a1 and 56a2 for grinding regions corresponding to the radial bearing surfaces 23a and 23b of the shaft member 2, a portion 56a3 for grinding a region corresponding to the tapered surface 24, and a cylindrical surface. 25, a portion 56 a 4 for grinding the region corresponding to 25, portions 56 a 5 to 56 a 7 for grinding each of the portions 26 to 28, and a portion 56 a 8 for grinding the region corresponding to the outer peripheral surface 22 c of the flange portion 22.

  The grinding process in the grinding apparatus 50 having the above-described configuration is performed in the following procedure. First, with the shaft material 10 and the grindstone 53 being rotated, the grindstone 53 is fed in an oblique direction (in the direction of arrow 1 in the figure), and the flat grinding portion 56b of the grindstone 53 is pressed against the shaft portion side end surface 12a of the flange portion 12. The shaft part side end surface 12a of the flange part 12 is ground. As a result, the finishing process of the end surface on the flange portion 22 side of the shaft member 2 is completed, and the thrust bearing surface 22a facing the first thrust bearing portion T1 is formed. Next, the grindstone 53 is fed in a direction orthogonal to the rotational axis of the shaft blank 10 (in the direction of arrow 2 in the figure), and the grindstone 53 is placed on the outer circumferential surface 11 a of the shaft portion 11 and the outer circumferential surface 12 c of the flange portion 12. The cylindrical grinding portion 56a is pressed to grind the surfaces 11a and 12c. Thereby, among the outer peripheral surface of the shaft portion 21 of the shaft member 2, the regions corresponding to the radial bearing surfaces 23a and 23b and the cylindrical surface 25 are ground, respectively, and the tapered surface 24, the outer peripheral surface 22c of the flange portion 22, and each Nusumi portions 26 to 28 are formed. In the grinding, for example, as shown in FIG. 8, it is preferable to perform grinding while measuring the remaining grinding allowance with a measurement gauge 57.

  In this entire surface grinding process, since the perpendicularity of the both end faces 11b and 12b of the shaft blank 10 is determined in advance by width grinding, each surface to be ground can be ground with high precision.

(B-3) Finish grinding (B-2) Of the surfaces ground by the overall grinding, final finish grinding is performed on regions corresponding to the radial bearing surfaces 23a and 23b and the cylindrical surface 25 of the shaft member 2. Apply. The grinding apparatus used for this grinding is, for example, a plunge grinding with a grindstone 63 while rotating the shaft material 10 sandwiched between a backing plate 64 and a pressure plate 65 in a cylindrical grinder shown in FIG. The shaft material 10 is rotatably supported by the shoe 62. The grinding surface 63a of the grindstone 63 corresponds to the first cylindrical grinding part 63a1 that grinds the region corresponding to the radial bearing surfaces 23a and 23b of the shaft member 2 (regions indicated by 13a and 13b in the figure) and the cylindrical surface 25. And a second cylindrical grinding portion 63a2 for grinding a region to be ground (a region indicated by 15 in the figure).

  In the grinding device 60 having the above-described configuration, by supplying a radial feed to the rotating grindstone 63, the regions 13a, 13b, and 15 corresponding to the radial bearing surfaces 23a, 23b and the cylindrical surface 25 are ground, respectively. Is finished to the final surface accuracy.

  After passing through the forming step (A) and the grinding step (B), the shaft member 2 shown in FIG. 1 is completed by performing heat treatment and cleaning treatment as necessary. As a result, through holes 29 that open to both end faces of the flange portion 22 are formed in the vicinity of the shaft portion 21. Since the inner peripheral surface of the through hole 29 is formed by forging, the surface roughness is good.

  According to the said manufacturing method, the cylindrical degree of the radial bearing surfaces 23a and 23b formed in the axial part 21 outer periphery can be finished with high precision. Thereby, for example, the variation in the circumferential direction or the axial direction of the radial bearing gap formed between the inner peripheral surface 8a of the inner periphery of the bearing sleeve 8 in the dynamic pressure bearing device 1 is suppressed within a predetermined range, The adverse effect on the bearing performance due to the variation in the radial bearing gap can be avoided. Further, the shaft member 2 is formed in which the squareness values of both end surfaces (thrust bearing surfaces) 22a and 22b of the flange portion 22 are kept small with reference to the radial bearing surfaces 23a and 23b formed on the outer periphery of the shaft portion 21. You can also. Thrust bearing surfaces 22a and 22b formed on both end surfaces of the flange portion 22 form a thrust bearing gap between opposing surfaces (such as the lower end surface 8c of the bearing sleeve 8 and the upper end surface 7b1 of the bottom portion 7b of the housing 7). Therefore, the variation in the thrust bearing gap can be suppressed by keeping the squareness value small. Further, the end surface 21b of the shaft portion also serves as a reference surface for setting the thrust bearing gap. For this reason, the thrust bearing clearance can be managed with high accuracy by keeping the squareness of the shaft end face 21b small.

  Further, in this embodiment, the finish grinding process (see FIG. 9) is performed on the region corresponding to the cylindrical surface 25 of the shaft portion 21, so that the cylindricity of the cylindrical surface 25 is also finished with high accuracy, and the disk hub 3 and the like. Assembling accuracy when attaching the member to the shaft member 2 is improved. As a result, it is possible to improve the accuracy when fixing a clamper or the like for holding the disk D to the disk hub 3 to the shaft member 2, and the shaft member of the disk D clamped and fixed between the clamper and the disk hub 3. Assembling accuracy with respect to 2 is further increased, and further improvement in motor performance is achieved.

  In the above embodiment, the case where the radial bearing surfaces 23a and 23b and the thrust bearing surfaces 22a and 22b of the shaft member 2 are all smooth surfaces without dynamic pressure grooves is exemplified. Grooves can also be formed. In this case, the radial dynamic pressure groove can be formed by rolling or forging before the grinding process shown in FIGS. 6 to 9, and the thrust dynamic pressure groove can be formed by pressing or forging. .

  Moreover, in the above embodiment, in order to prevent the escape of the pressure in the thrust bearing gaps W1 and W2, the through holes 29 are avoided by avoiding the thrust bearing surfaces 22a and 22b (thrust bearing gaps W1 and W2) of the flange portion 22. The case where it is formed so as to open to the inner diameter side than the bearing surfaces 22a and 22b has been described. However, when a dynamic pressure groove and a thrust bearing gap can be set in consideration of some pressure relief, the through hole 29 is formed in the thrust hole. It is also possible to form the bearing surfaces 22a and 22b at positions.

  Moreover, in the above embodiment, as the dynamic pressure bearings constituting the radial bearing portions R1 and R2 and the thrust bearing portions T1 and T2, for example, a dynamic pressure generating portion including a herringbone shape or a spiral shape dynamic pressure groove is used. Although the bearing is illustrated, the configuration of the dynamic pressure generating unit is not limited to this. As the radial bearing portions R1 and R2, for example, multi-arc bearings, step bearings, taper bearings, taper flat bearings, etc. can be used. As the thrust bearing portions T1 and T2, step pocket bearings, taper pocket bearings, taper・ Flat bearings can also be used.

  Moreover, in the above embodiment, the inside of the hydrodynamic bearing device 1 is filled, and the radial bearing gap between the bearing sleeve 8 and the shaft member 2 and the thrust between the bearing sleeve 8 and the housing 7 and the shaft member 2 are filled. Although the lubricating oil is exemplified as the fluid that causes the dynamic pressure action in the bearing gaps W1 and W2, it is not particularly limited to this fluid. A fluid capable of generating a dynamic pressure action in each bearing gap having the dynamic pressure grooves, for example, a gas such as air, or a fluid lubricant such as a magnetic fluid may be used.

It is a side view of the shaft member for fluid dynamic bearing devices concerning one embodiment of the present invention. It is sectional drawing of the spindle motor for information devices incorporating the dynamic pressure bearing apparatus provided with the shaft member. It is a longitudinal cross-sectional view of a fluid dynamic bearing device. It is a longitudinal cross-sectional view of a bearing sleeve. It is a side view of the shaft raw material shape | molded by the forging process. (A) is the schematic which shows an example of the grinding apparatus which concerns on the width grinding process of a shaft raw material, (b) is an enlarged view of the notch periphery of the carrier holding a shaft raw material. It is a partial cross section figure showing an example of a grinding device concerning the above-mentioned width grinding process. It is the schematic which shows an example of the grinding device which concerns on the shaft material whole surface grinding process. It is the schematic which shows an example of the grinding apparatus which concerns on the grinding finishing process of a shaft raw material.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Dynamic pressure bearing apparatus 2 Shaft member 3 Disk hub 4 Stator coil 5 Rotor magnet 7 Housing 8 Bearing sleeve 8a Inner peripheral surface 8a1, 8a2 Dynamic pressure groove 8c Lower end surface 8c1 Dynamic pressure groove 9 Seal member 10 Shaft material 11 Shaft part 11b End surface 12 Flange portion 12a Shaft portion side end surface 12b Non-shaft portion side end surface 13 Straightening surface 14 Tapered surface 15 Cylindrical surface 19 Through hole (shaft material)
21 Shaft portion 21b End surface 22 Flange portion 22a, 22b Thrust bearing surface 23a, 23b Radial bearing surface 24 Tapered surface 25 Cylindrical surface 26, 27, 28 Nusumi portion 29 Through hole 40 Grinding device 41 Carrier 42 Grinding stone 43 Notch 43a Inner surface 50, 60 grinding device 52, 62 shoe 53, 63 grinding wheel 54, 64 backing plate 55, 65 pressure plate 56 grinding surface 56a cylindrical grinding unit 56b surface grinding unit 57, 67 measuring gauge 63 grinding wheel 63a grinding surface D disk S seal space R1, R2 Radial bearing part T1, T2 Thrust bearing part W1, W2 Thrust bearing clearance

Claims (7)

In a shaft member for a hydrodynamic bearing device that includes a flange portion and is supported in a non-contact manner in a thrust direction by a pressure generated by a dynamic pressure action of a fluid generated in a thrust bearing gap on both axial sides of the flange portion.
In the flange portion, through-holes that are open on both end faces are formed,
A shaft member for a hydrodynamic bearing device, wherein the inner periphery of the through hole is a plastically processed surface.   The shaft member for a hydrodynamic bearing device according to claim 1, further comprising a shaft portion forged and formed integrally with the flange portion.   The shaft member for a hydrodynamic bearing device according to claim 1, wherein the through hole is formed in the vicinity of the shaft portion.   The hydrodynamic action of the fluid which arises in the radial bearing clearance between the shaft member in any one of Claims 1-3, the bearing sleeve in which a shaft member is inserted in an inner periphery, and the outer periphery of a shaft part, and the inner periphery of a bearing sleeve A radial bearing that supports the shaft in a non-contact manner in the radial direction by generating pressure with a hydrodynamic pressure generated by the fluid generated in the thrust bearing gap at one end of the flange, and the flange is non-contact in the thrust A first thrust bearing portion for supporting, and a second thrust bearing portion for generating pressure by a dynamic pressure action of a fluid generated in a thrust bearing gap on the other end side of the flange portion and supporting the flange portion in a non-contact manner in the thrust direction. Hydrodynamic bearing device.   A dynamic pressure groove for generating a dynamic pressure action of fluid is formed asymmetrically in the axial direction on one of the outer peripheral surface of the shaft portion facing the radial bearing gap and the inner peripheral surface of the bearing sleeve facing this outer peripheral surface. The hydrodynamic bearing device according to claim 4.   A motor comprising the hydrodynamic bearing device according to claim 4, a rotor magnet, and a stator coil. A method of manufacturing a shaft member for a hydrodynamic bearing device comprising a shaft portion and a flange portion and supported in a non-contact manner in a thrust direction by a pressure generated by a dynamic pressure action of a fluid generated in a thrust bearing gap on both axial sides of the flange portion In
A shaft member for a hydrodynamic bearing device, wherein the shaft portion and the flange portion are integrally forged, and through holes that are open on both end surfaces of the flange portion are forged and these forgings are performed simultaneously. Manufacturing method.

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