Abstract:
As axis direction dimensions become smaller in HDD spindle motors as a result of thinner and more compact designs, there is a demand for hydrodynamic bearings with a long lifespan. As a means of solving this problem, a lubricant reservoir section is formed between a sleeve side surface and a cover side surface with a depth varying in a circumferential direction, lubricant is circulated in a bearing gap section, a sleeve end face gap section larger than a bearing gap between a sleeve end face and the cover, and a connecting channel, and the lubricant reservoir section and the sleeve end face gap section are connected via an introducing gap section having a bubble separation function.

Description:
BACKGROUND OF THE INVENTION 
     1. Field of the Invention 
     The present invention relates to spindle motors for driving the rotation of magnetic disks, optical disks, and the like; information recording and reproducing apparatuses; and hydrodynamic bearings used in the spindle motors and the like. 
     2. Description of the Related Art 
     Hydrodynamic bearings, having better rotation accuracy and also quietness than ball bearings, are being put to use in place of the ball bearing devices conventionally used as bearings for the spindle motors of hard disk devices and the like. 
     In recent years, furthermore, as hard disk devices have become standard equipment in laptop personal computers, and in addition, are seeing increasing levels of use in portable music players and cellular phones, factors such as thinner and more compact designs, lower power consumption, increased shock resistance, and increased lifespan are in demand. 
     Constraints are readily placed on axis direction dimensions in line with efforts to achieve thinner and more compact designs. As a result, how best to guarantee radial bearing dimensions in order to ensure the required levels of bearing angular stiffness has been a problematic issue. With regard to increasing lifespan, furthermore, how best to ensure a large oil reservoir of the bearing oil within limited bearing dimensions has been a problematic issue. And with regard to shock resistance, it is necessary to prevent the occurrence of oil leakage upon being exposed to shock. Accordingly, the reliability of the bearing device cannot be allowed to decrease with efforts to achieve thinner and more compact designs or increased lifespan. 
     A range of proposals have been put forth as a means of addressing these market requirements. For example, in some inventions, as shown in  FIG. 10  (see U.S. Pat. No. 7,059,773), an equalizing volume  102  is formed on an outer peripheral surface of a cylindrical bearing sleeve  101 , a covering cap  104  having a spacer  103  is disposed on an upper end face of the cylindrical bearing sleeve  101 , and thereby a connecting channel  106  is formed between the covering cap  103  and a bearing gap  105 . Furthermore, a re-circulation channel  107  is provided. In addition, the covering cap  104  is provided with a hole  108  on a side surface. The hole  108  is used when injecting a lubricant  109  following bearing assembly and is formed with a sufficiently small size that the lubricant  109  will not be thrown off as a result of shock or the like. 
     In the aforementioned bearing construction, the lubricant  109  moves inside a circulation channel including the bearing gap  105  and the re-circulation channel  107 , eliminating imbalance in the internal pressure inside the bearing. In addition, the equalizing volume  102 , also constituting an oil reservoir, is connected to the bearing gap  105  via the connecting channel  106 , and is capable of supplying a vaporized portion of the lubricant  109  and of absorbing a thermal expansion portion of the lubricant  109  as a result of temperature. 
     In the construction of the aforementioned U.S. Pat. No. 7,059,773, as the equalizing volume  102 , constituting the oil reservoir, can be arranged in parallel with the bearing gap  105 , the necessary length of the radial bearing section formed by the bearing gap  105  can be secured, and therefore, the required bearing angular stiffness can be realized while also achieving a thinner and more compact design. In addition, as the equalizing volume  102 , constituting the oil reservoir, is formed at an outer peripheral portion of the bearing sleeve  101 , sufficient capacity can be secured within a range not affecting bearing performance. 
     In addition, the configurations disclosed in JP 2006-161988A, JP 2006-170230A, and JP 2006-161967 have been proposed as designs having a large oil reservoir and increased lifespan. 
     SUMMARY OF THE INVENTION 
     Nevertheless, in the hydrodynamic bearing disclosed by the aforementioned U.S. Pat. No. 7,059,773, the area of an interface boundary surface (a detailed view thereof not provided in U.S. Pat. No. 7,059,773) of the lubricant  109  formed by an outer periphery of a shaft  110  and an inner periphery of the covering cap  104  is extremely small when compared with the area of an interface boundary surface of the equalizing volume  102  formed on the outer periphery of the bearing sleeve  101 . Accordingly, the surface tensions thereof cannot easily be equalized. In specific terms, as the surface tension of the interface boundary surface of the equalizing volume  102  is far larger, the interface boundary surface formed between the shaft  110  and the inner periphery of the covering cap  104  can easily rise. As a result, it is believed that the lubricant  109  can easily leak from an opening section. 
     The hydrodynamic bearing according to the present invention includes a shaft, a sleeve, a cover, a connecting channel, a lubricant, a sleeve end face gap section, a vent hole, and a first lubricant reservoir section. The sleeve is provided with a bearing hole having a closed end at one end and an open end at the other end, and the shaft is inserted into the bearing hole so as to be capable of relative rotation. The cover covers an end face and an outer peripheral surface of the sleeve at the open-end side thereof and at a distance forming a gap. The connecting channel connects a space region at the closed-end side of the sleeve and a gap region between the cover and the open-end side of the sleeve. The lubricant is retained within a sleeve-internal space including the space between the cover and the sleeve. In order that the lubricant moves from the connecting channel to the bearing hole, the sleeve end face gap section is formed between the cover and an end face at the open-end side of the sleeve and includes an introducing gap section formed in close proximity to an opening section of the connecting channel. The vent hole is formed in a space between an inner peripheral surface of the cover and an outer peripheral surface of the sleeve so as to connect with outside air and is connected to the introducing gap section. The first lubricant reservoir section is formed between the inner peripheral surface of the cover and the opposing outer peripheral surface of the sleeve by forming a depression in one of the sleeve and the cover, or both thereof so as to provide a space larger than the sleeve end face gap section. The first lubricant reservoir section is capable of storing lubricant therein and is shaped such that the gap between the inner peripheral surface of the cover and the outer peripheral surface of the sleeve grows larger as a distance from the vent hole in a circumferential direction decreases. 
     Here, the hydrodynamic bearing, circulating lubricant between the connecting channel and the bearing hole, is provided with the first lubricant reservoir section for storing lubricant between the outer peripheral surface of the sleeve and the inner peripheral surface of the cover and at a position of connection to the vent hole. The size of each gap is controlled such that the lubricant is pulled into a sleeve end face gap section between opposing surfaces of the cover and the sleeve. Furthermore, the sleeve end face gap section is formed so as to guide the lubricant from the connecting channel to the bearing-hole side. 
     As a result, even in situations where air bubbles having adhered to, for example, hydrodynamic grooves of a radial flow bearing are detached from the hydrodynamic grooves by a circulatory flow occurring upon relative rotation of the shaft and the sleeve and the air bubbles circulate, the air bubbles can be separated from the lubricant upon flow thereof into the introducing gap section from the connecting channel. The air bubbles then move to the first lubricant reservoir section, constituting a larger space than the introducing gap section, and are discharged from the vent hole. As a result of this, problems caused by air bubbles such as drops in bearing stiffness and drops in bearing performance due to, for example, instability in rotation during rotating operation can be prevented. 
     Furthermore, as the first lubricant reservoir section is formed on an outer peripheral surface side of the sleeve in the above-explained configuration, a gap in the axis direction usable for a bearing can be put to maximum effective use for radial bearings. Adverse effects on bearing characteristics can, therefore, be avoided, even in the case of hydrodynamic bearings of a thinner and more compact design. 
     In addition, the size of the storage space for lubricant in the first lubricant reservoir section can, for example, be modified easily by changing the size of the depression on the sleeve side. Accordingly, lifespan reduction caused by vaporization of the lubricant can be avoided, and deterioration of bearing characteristics due to, for example, changes in bearing length pursuant to the design of thinner, more compact hydrodynamic bearings can be prevented. 
     Furthermore, the introducing gap section, stimulating capillary action at the open-end side of the bearing hole, is provided in a region containing a section of the sleeve end face gap section, which is disposed between a back surface of the cover and the open-end side end face of the sleeve, directly above the connecting channel. In this configuration, as the gap expands towards the outer peripheral side from the open-end side, a lubricant delivered from the connecting channel flows into the bearing hole via the introducing gap section and the sleeve end face gap section as a result of a capillary force. 
     As a result of this configuration, a region of large capillary force is provided in the form of the sleeve end face gap section between the back surface of the cover and the open-end side end face of the sleeve. Accordingly, lubricant introduced from the introducing gap section is favorably supplied from a complete periphery to the open end of the bearing hole of the sleeve via the sleeve end face gap section. As a result, the bearing-hole open end of the sleeve can also be stably filled with lubricant. 
     Furthermore, the hydrodynamic bearing according to the present invention also includes a second lubricant reservoir section, connecting with the outside air and storing lubricant, on an inner peripheral surface of the cover opposing the shaft. This second lubricant reservoir section is configured so as to include an inclined surface inclined such that an internal diameter increases in line with separation from the open-end side end face of the sleeve in the axis direction. The second lubricant reservoir section is configured such that the surface tension of the lubricant stored in the second lubricant reservoir section and the surface tension of the lubricant in the first lubricant reservoir section of the outer peripheral surface side of the sleeve are substantially equalized. 
     As a result of this configuration, the surface tension of the interface boundary surface in the second lubricant reservoir section, formed on the inner peripheral surface of the cover opposing the shaft, and the surface tension of the interface boundary surface in the first lubricant reservoir section, formed between the inner peripheral surface of the cover and the outer peripheral surface of the sleeve, can be stably equalized. Accordingly, sudden changes in the position of the interface boundary surface and leakage of the lubricant as a result of movement of the interface boundary surface, for example, can be prevented. 
     Furthermore, if a gap of the sleeve end face gap section formed between the cover and the sleeve end face is defined as g 1 , a gap of the side surface gap section formed between the cover and the sleeve outer peripheral surface is defined as g 2 , and the minimum gap of the first lubricant reservoir section is defined as g 3 , then the relationship g 1 &lt;g 2 &lt;g 3  is satisfied in the hydrodynamic bearing according to the present invention. 
     As a result of this configuration, the lubricant stored in the first lubricant reservoir section is supplied to the bearing hole after being smoothly moved to the sleeve end face gap section via the side surface gap section by capillary action. As a result, lubricant can be smoothly supplied from the first lubricant reservoir section, and the lubricant in the bearing hole can be prevented from running out. 
     In addition, the hydrodynamic bearing according to the invention includes a ventilation hole in an outer peripheral surface of the cover. The ventilation hole is formed having a semicircular shape or the shape of a section of a circle on a cover end face. 
     As a result of this configuration, it is possible to form covers including ventilation holes cheaply, with few man-hours, and without the use of die configurations having, for example, side pins. 
     In addition, the hydrodynamic bearing according to the present invention includes a thrust flange fixed to a tip of the shaft in a space region at the closed-end face side of the sleeve. An opening section of the connecting channel provided at the closed-end face side of the sleeve connects to the space wherein this thrust flange is provided. 
     As a result, the lubricant supplied from the open end of the bearing hole of the sleeve can be passed through to the sleeve end face section via a radial bearing provided between the inner peripheral surface of the sleeve and the outer peripheral surface of the shaft. Consequently, the lubricant can be smoothly supplied to the bearing section. Furthermore, as circulation pressure (pump pressure) from the radial bearing can be released via this connecting channel, the vicinity of the opening section of the connecting channel of the thrust flange section can maintain a pressure substantially equivalent to that of a bearing exterior portion. Accordingly, it is possible to prevent contact between the thrust flange and the sleeve resulting from a pressure imbalance caused by a difference in areas of upper and lower thrust-bearing surfaces formed on each of the upper and lower surface sides of the thrust flange. 
     In the hydrodynamic bearing according to the present invention, furthermore, the space region at the closed-end face side of the sleeve is formed by the tip of the shaft and a closed-end-face-side region closing plate. The opening section of the connecting channel provided on the closed-end face side of the sleeve connects to a space faced by the tip of this shaft. 
     As a result, the lubricant supplied from the open end of the bearing hole of the sleeve can be passed through to the sleeve end face section via a radial bearing provided between the inner peripheral surface of the sleeve and the outer peripheral surface of the shaft. Consequently, the lubricant can be smoothly supplied to the bearing section. Furthermore, as circulation pressure (pump pressure) from the radial bearing can be released via this connecting channel, the vicinity of the opening section of the connecting channel of the thrust flange section can maintain a pressure substantially equivalent to that of a bearing exterior portion. Accordingly, it is possible to prevent contact between the thrust flange and the sleeve resulting from a pressure imbalance caused by a difference in areas of upper and lower thrust-bearing surfaces formed on each of the upper and lower surface sides of the thrust flange. 
     In the hydrodynamic bearing according to the present invention, furthermore, hydrodynamic grooves provided on at least one of the outer peripheral surface of the shaft and the inner peripheral surface of the sleeve are shaped so as to impart circulating force to the lubricant. 
     As a result of this, lubricant can be stably supplied to the radial bearing and the thrust bearing. Furthermore, even in situations wherein air bubbles have been formed inside the bearing, the air bubbles can be smoothly discharged to the exterior via the connecting channel. 
     The hydrodynamic bearing according to the present invention is provided with a shaft, a sleeve having a closed end at one end and an open end of an opening which serves a bearing hole, and a cover covering an end face on the open-end side of the sleeve and an outer peripheral side surface section of the sleeve at a distance forming a gap or a space and with the shaft inserted into the bearing hole of the sleeve so as to be capable of rotating freely. A connecting channel is formed so as to connect the space region at the closed-end face side of the sleeve and a gap region between the cover and the open-end side of the sleeve, lubricant is retained in a sleeve internal space including a space between the cover and the sleeve, and a sleeve end face gap section is formed between the cover and the open-end side end face of the sleeve such that the lubricant moves from the connecting channel to the bearing hole. An introducing gap section connecting with the sleeve end face gap section is formed in a region in close proximity to an opening section of the connecting channel. A vent hole connects a space between a cover inner peripheral section and a sleeve outer peripheral side surface with the outside air. The introducing gap section and the vent hole are connected and a first lubricant reservoir section capable of storing lubricant is formed between the cover inner peripheral section and the opposing outer peripheral side surface of the sleeve by forming a depression in one of the sleeve and the cover, or both thereof so as to provide a space larger than the gap of the sleeve end face gap section. The first lubricant reservoir section is formed such that the separation distance between the inner peripheral side surface of the cover and the outer peripheral side surface of the sleeve grows larger as a distance from the vent hole side in a circumferential direction decreases. 
     In the above-explained configuration, when either the shaft or the sleeve is rotated relatively, the lubricant flows and circulates in the sleeve inner portion and the space between the sleeve and the cover. As this time, even in situations where air bubbles having adhered to, for example, hydrodynamic grooves of the radial flow bearing are detached from the grooves by the above-explained circulatory flow and circulate, the air bubbles can be separated from the lubricant upon flow thereof into a lubricant reservoir section from the connecting channel via the introducing gap section and can be discharged from the vent hole. As a result of this, problems caused by air bubbles such as drops in bearing stiffness and drops in bearing performance due to, for example, instability in rotation during rotating operation can be prevented. 
     Furthermore, as the first lubricant reservoir section is formed in the outer peripheral side surface section of the sleeve in the above-explained configuration, a gap in the axis direction usable for a bearing can be put to maximum effective radial-bearing usage. Accordingly, it is possible to reduce the effect even of efforts to achieve thinner and more compact hydrodynamic-bearing designs on bearing characteristics. Furthermore, as the size of the storage space can be easily changed by changing the size of the sleeve-side depression in order to avoid reduction of lifespan caused by the vaporization of lubricant, bearing characteristics are not adversely affected by, for example, changes in bearing length. 
     EFFECT OF THE INVENTION 
     As the first lubricant reservoir section is formed on the outer peripheral surface side of the sleeve, so as to pull the lubricant by capillary force into an introducing gap section formed on a sleeve end face, the hydrodynamic bearing according to the present invention makes it possible for bearing length (principally of radial bearings, but also of conical bearings) to be maximized, even in the case of thinner and more compact hydrodynamic bearings with insufficient space at the sleeve end side. Accordingly, by maintaining a sufficient charge of lubricant while also making best use of the characteristic benefits of a bearing containing a connecting channel, the lifespan of the hydrodynamic bearing can be increased and the reliability thereof can be improved. 
     Furthermore, a sleeve end face gap section stimulating capillary action in the same way as the gap at the open end of the bearing hole is formed between the back surface of the cover and an open-end side end face of the sleeve. The introducing gap section is connected to the sleeve end face gap section, and as a result of this configuration, the lubricant delivered from the connecting channel flows into the bearing hole via the introducing gap section and the sleeve end face gap section due to capillary action. Accordingly, lubricant introduced from the introducing gap section is favorably supplied from a complete periphery to the open end of the bearing hole of the sleeve via the sleeve end face gap section. Consequently, the open end of the bearing hole of the sleeve can be stably filled with lubricant. As a result, the inclusion of air bubbles in the lubricant does not readily occur, even in situations wherein the hydrodynamic bearing is exposed to shock from the exterior, and therefore, the reliability of the hydrodynamic bearing can be further improved. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a cross-sectional view of a spindle motor provided with a hydrodynamic bearing according to an embodiment of the present invention. 
         FIG. 2A  is a cross-sectional view of the hydrodynamic bearing, and  FIG. 2B  is a view of a hydrodynamic groove thereof. 
         FIG. 3  is an enlarged cross-sectional view of an upper portion of the hydrodynamic bearing. 
         FIG. 4  is a cross-sectional view of the hydrodynamic bearing taken along line III-III of  FIG. 3 . 
         FIG. 5  is a see-through view from a top surface of the hydrodynamic bearing. 
         FIG. 6  is a side view of the hydrodynamic bearing seen from ventilation hole-side. 
         FIG. 7  is an enlarged cross-sectional view of Section J of  FIG. 3  showing a second lubricant reservoir section of the hydrodynamic bearing. 
         FIG. 8  is a conceptual view showing equalization of pressures between the second lubricant reservoir section and a first lubricant reservoir section of the hydrodynamic bearing. 
         FIG. 9  is a view of an information recording and reproducing apparatus  53  using a spindle motor provided with the hydrodynamic bearing according to the present invention. 
         FIG. 10  is a cross-sectional view of a conventional hydrodynamic bearing. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
     The following is a description of a hydrodynamic bearing according to a preferred embodiment of the present invention, with reference to the accompanying drawings. 
     It should be noted that, in this embodiment, a case of usage of this hydrodynamic bearing in a spindle motor of a hard disk device is explained. 
       FIG. 1  is a cross-sectional view of a spindle motor provided with a hydrodynamic bearing according to an embodiment of the present invention.  FIG. 2A  and  FIG. 2B  is a cross-sectional view of the hydrodynamic bearing and enlarged view of a hydrodynamic groove.  FIG. 3  is a detail view thereof.  FIG. 4  is a cross-sectional view taken along line III-III of  FIG. 3 . It should be noted that, although a configuration wherein an open end of a bearing hole of a sleeve is disposed above and a closed end is disposed below for ease of understanding in the following explanation as shown in  FIG. 1 ,  FIG. 2A , and  FIG. 3 , cases of practical usage are, of course, not limited to this configuration. 
     A hydrodynamic bearing included in a spindle motor of this embodiment includes a shaft  1 , a sleeve  2 , a large-diameter thrust flange  3 , and a thrust plate  4  as shown in  FIG.1  through  FIG. 3 . As regards the materials for each member, for example, stainless steel or chrome-manganese steel can be used for the shaft, and stainless steel can be used for the thrust flange. In addition, the sleeve can be manufactured from copper alloy such as brass subjected to electroless nickel plating, or stainless steel. A stainless steel plate subjected to DLC coating or the like can be used for the thrust plate. 
     The sleeve  2  is secured to a base  15  of the spindle motor and has a bearing hole  2   a  including an open, upper-side open end  2   aa  and a closed, lower-side closed end  2   ab , and the shaft  1  is inserted via an interval or space so as to be capable of rotating freely. 
     The large-diameter thrust flange  3  is secured to a lower end portion of the shaft  1  by fitting and bonding or using a screw, and in addition, is disposed at a large-diameter hole section  2   ac  constituting a closed-end side in the bearing hole  2   a  at a distance forming a gap with the top surface of the large-diameter hole section  2   ac.    
     The thrust plate  4  is secured to a bottom portion of the sleeve  2  so as to oppose a lower surface of the thrust flange  3  at a distance forming a gap. 
     In addition to these configuration elements, this embodiment provides a cover  5  including a material having a translucent or transparent property (polyetherimide resin or polyethersulfone resin, for example) and covering an upper end face (or open-end side end face) and an outer-peripheral side surface section of the sleeve  2  at a distance forming a space. Furthermore, the cover  5  is provided with a vent hole  13  connecting to the outside air at an outer peripheral side surface section. 
     A connecting channel  6  (for example, between approximately 0.2 and 0.6 mm in diameter) extending in a direction substantially parallel to an axis O passes through this hydrodynamic bearing at a position within the sleeve  2  near an outer peripheral surface thereof. This connecting channel  6  connects the large-diameter hole section  2   ac  provided at the closed end  2   ab  side of the bearing hole  2   a  (that is, a space region at the closed-end face side) to the space region between the cover  5  and the upper-end face of the sleeve  2 , constituting an open end  2   aa  side end face thereof. 
     Furthermore, internal spaces of the sleeve  2  including the space between the cover  5  and the sleeve  2  (that is, a space between an outer peripheral surface of the shaft  1  and an inner peripheral surface of the sleeve  2 , a space inside the large-diameter hole section  2   ac  of the bearing hole  2   a , a space at a connecting location between the large-diameter hole section  2   ac  of the bearing hole  2   a  and the connecting channel  6 , a space inside the connecting channel  6 , a space between the upper end face of the sleeve  2  and the cover  5 , and a space between the outer-peripheral side surface section of the sleeve  2  and an internal periphery of the cover  5  (not including the vent hole  13 )) are filled with a lubricant  20 , such as lubricating oil. Superfluid grease or ionic liquid can also be used as the lubricant. It should be noted that, as shown enlarged in  FIG. 7 , the internal peripheral surface of the cover  5  opposing the shaft  1  is provided with an inclined surface widening in line with separation from the open end in the axis direction, forming a second lubricant reservoir section  23  connecting with the outside air and storing the lubricant  20 . In addition, a step section end face  2   f  of the sleeve  2  and an end face  5   f  of the cover  5  are secured using adhesive  21  and configured such that the lubricant  20  cannot leak out to the exterior from the bonding surface of the sleeve  2  and the cover  5 . 
     A pair of hydrodynamic grooves  7 ,  8  are formed arranged vertically having, for example, a fish-bone pattern on the internal peripheral surface of the sleeve  2 . It should be noted that the hydrodynamic grooves  7 ,  8  can be provided either on the outer peripheral surface of the shaft  1  or on both the inner peripheral surface of the sleeve  2  and the outer peripheral surface of the shaft  1 . When the shaft  1  and the sleeve  2  are rotated relatively by a rotation drive force as explained hereinafter, a radial bearing wherein the shaft  1  and the sleeve  2  are supported by a force of the lubricant  20  collected and drawn out by these hydrodynamic grooves  7 ,  8  so as to be capable of rotating relatively and freely at a fixed interval in a radial direction is configured. In addition, hydrodynamic grooves  9 ,  10  are formed having, for example, a helical shape on an upper surface and lower surface of the thrust flange  3 . It should be noted that the hydrodynamic grooves  9 ,  10  can be provided on an opposing lower surface of the sleeve  2  and upper surface of the thrust plate  4 , or alternatively, on upper and lower surfaces of the thrust flange  3 , a lower surface of the sleeve  2 , and an upper surface of the thrust plate  4 . When the thrust flange  3  mounted on the shaft  1  and the sleeve  2  are rotated relatively by, for example, a rotation drive force, a thrust bearing wherein the shaft  1  and the sleeve  2  are supported by a force of the lubricant  20  collected and drawn out by these hydrodynamic grooves  9 ,  10  so as to be capable of rotating freely at a fixed interval in a thrust (or axial) direction is configured. Here, the hydrodynamic grooves  7 ,  8  of the radial bearing are of a widely-known herringbone shape and are formed in two locations. Specifically, the hydrodynamic grooves  7 ,  8  are formed at an upper side and a lower side of an outer peripheral surface of the shaft  1 . The lower hydrodynamic groove  8  is formed such that an inclined groove rising from a peak section thereof and an inclined groove descending from the peak section thereof are of same length. Meanwhile, as shown in  FIG. 2A  and  FIG. 2B , the upper hydrodynamic groove  7  is formed such that an inclined groove  7 a rising from a peak section thereof is longer than an inclined groove  7 b descending from the peak section thereof. The configuration is such that, upon driving of rotation, the lubricant  20  in this gap is actively delivered downward by this upper hydrodynamic groove  7 . 
     As shown in  FIG. 1 , a hub  16  is press fitted onto an outer periphery of a protruding shaft section  1   a  of the shaft  1  protruding from the bearing hole  2   a  of the sleeve  2 , the hub  16  constituting a rotation member with, for example, a magnetic recording disk being secured on an outer periphery thereof. In this embodiment, a rotor magnet  17  is mounted on an outer periphery of a section of the hub  16  close to a base  15 . Furthermore, a stator core  19 , whereupon a stator coil  18  is wound, is mounted on the base  15  so as to oppose the rotor magnet  17 . This rotor magnet  17  and stator core  19  constitute a rotation drive section of a spindle motor delivering rotation drive force to the shaft  1  and the sleeve  2 . 
     In addition, as shown in  FIG. 2A  and  FIG. 2B , the upper end face of the sleeve  2  opposing the cover  5  is formed having a substantially planar shape. In contrast, as shown in  FIG. 3 , an introducing gap section  11  stimulating capillary action at an inner peripheral side in a radial direction is provided on the cover  5  in a region in close proximity to the opening section of the connecting channel  6  on the upper end face of the sleeve  2 . This introducing gap section  11  is formed such that a gap grows larger towards an outer periphery. Furthermore, the back surface of the cover  5  other than in a region in close proximity to the opening section is disposed approximately parallel to the upper end face of the sleeve  2  at a distance forming a gap equivalent to the smallest gap of the introducing gap section  11 . The separation distance between the inner peripheral surface of the cover  5  and the upper portion of the outer peripheral surface of the sleeve  2  is, a dimension g 1  (as shown in  FIG. 3 ), stimulating capillary action from a first lubricant reservoir section  14 , as shown in  FIG. 4 , towards an upper surface portion of the sleeve  2 . A gap (the introducing gap section  11  and a sleeve end face gap section  12 ) wherethrough lubricant flows with respect to the bearing hole  2   a  of the inner peripheral surface of the sleeve  2  as a result of capillary action, is thus formed. It should be noted that, for ease of understanding, the separation space between the inner peripheral surface section of the cover  5  and the opposing outer peripheral surface side section of the sleeve  2  is shown conceptually in  FIG. 4 . In addition, this introducing gap section  11  is, as shown in  FIG. 3  and  FIG. 5 , formed so as to connect a position in close proximity to the opening section of the connecting channel  6  to the open end of the bearing hole  2   a  of the sleeve  2  via the sleeve end face gap section  12 . 
     It should be noted that in this embodiment, the introducing gap section  11  is, when viewed from above in an axis direction, an approximately fan-shaped section with an opening angle θs of approximately 30 degrees, and is formed so as to have a wider range than the opening section of the connecting channel  6 . Here, a separating boundary between a region of the introducing gap section  11  and a region of the sleeve end face gap section  12  is a fan-shaped annular boundary widening towards an outer periphery. However, when a taper shape of an angle θt as explained hereinafter is provided, the opposing sides of this boundary can be parallel. The inner-peripheral side boundary of the region of the introducing gap section  11  is either outside the bearing hole  2   a  or in an equivalent region to the bearing hole  2   a.    
     Furthermore, the introducing gap section  11  is, when viewed laterally as a cross-section as shown in  FIG. 3 , formed having a tapered shape of angle θt larger than 0 degrees and increasing in size towards an outer peripheral side. The lubricant  20  circulated from the connecting channel  6  is moved towards an inner peripheral side as a result of capillary action due to this fan-shaped annular shape and tapered shape. As a result, air bubbles contained therein are moved towards an outer peripheral side, subjected to gas-liquid separation in the introducing gap section  11 , passed through a side-surface gap section  30  formed between the cover  5  and the sleeve  2 , and discharged to the vent hole  13  provided in the first lubricant reservoir section  14 . In addition, the diameter of the open end of the bearing hole  2   a  on the upper end face of the sleeve  2  is, for example, between 2.8 and 3.2 mm. The gap of the introducing gap section  11  is, for example, between 0.03 and 0.15 mm. In this embodiment, furthermore, the introducing gap section  11  is formed such that a gap widens towards an outer side in a radial direction, and the separation gap of the sleeve end face gap section  12  is constant in a radial direction. 
     In particular, the first lubricant reservoir section  14  capable of storing lubricant  20  is formed as a depression in the inner peripheral surface of the cover  5  and the outer peripheral surface of the sleeve  2  so as to provide a space larger than the gap of the introducing gap section  11  and of the sleeve end face gap section  12 . In addition, the first lubricant reservoir section  14  connects the introducing gap section  11  and the vent hole  13  in an axis direction. It should be noted that this first lubricant reservoir section  14  has, for example, a width in the axis direction of between approximately 0.5 and 1.5 mm, a minimum gap in a radial direction of between approximately 0.03 and 0.15 mm, and a maximum gap in the radial direction of between approximately 0.15 and 0.3 mm. The vent hole  13  has a radius of, for example, between approximately 0.15 and 0.5 mm. A recess section  22  (for example, a radius of between approximately 0.3 and 0.8 mm, and a depth of between approximately 0.1 and 0.3 mm) is provided as a buffer space and in the form of a countersunk hole at the location wherein this vent hole  13  is provided. The separation distance is greatest from the outer peripheral surface of the sleeve  2  at the portion of the first lubricant reservoir section  14  connecting with this vent hole  13  and the recess section  22  (referred to as a maximum space section  14   a ) and that portion is inclined in a radial direction such that the separation distance from the outer-peripheral side surface section of the sleeve  2  becomes larger upon drawing closer to the maximum space section  14   a  from an opposing direction about the axis O as center. It should be noted that, in this embodiment, the separation gap of the first lubricant reservoir section  14  is constant in the axis direction. In addition, in this embodiment, the vent hole  13  connecting with the outside air is provided at a position on the cover  5  wherein, in a plan view, the vent hole  13  and the opening section of the connecting channel  6  are arranged in the same direction with respect to the axis center O. Furthermore, as shown in  FIG. 4  and  FIG. 6 , formation of the recess section  22  on the vent hole  13  ensures that, even in cases wherein the lubricant  20  has reached full volume and, for example, the temperature of the disposition environment rises, the interface boundary surface K of the lubricant  20  remains inside the recess section  22  and the lubricant  20  does not leak out via the vent hole  13 . 
     Furthermore, as shown in  FIG. 6 , the vent hole  13  is formed with an approximately semicircular shape or the shape of a section of a circle on an end face of the cover  5 . Accordingly, when the cover  5  is formed by, for example, resin molding, there is no need for the die to have a complicated configuration including side pins and the like, and therefore, the die can be cheaply produced and man-hours can be reduced. 
     Furthermore, as shown enlarged in  FIG. 7 , the second lubricant reservoir section  23  is formed so as to widen towards an opening side on an inner peripheral surface of the cover  5  opposing the shaft  1 . In specific terms, the second lubricant reservoir section  23  is provided with an inclined surface  23   a  inclined such that the second lubricant reservoir section  23  becomes narrower in a downward axis direction. Accordingly, a diameter Dt at an upper end of the inclined surface  23   a  and a diameter dt at a lower end of the inclined surface  23   a  are set such that, even in situations wherein, as explained hereinafter, the position of the interface boundary surface within the first lubricant reservoir section  14  changes as a result of reduction of the lubricant  20  due to, for example, vaporization, the interface boundary surface is equalized within the range of motion on the inclined surface  23   a  within this second lubricant reservoir section  23 . 
     As shown in  FIG. 3 , furthermore, a lube-repellant coating recess  24  is also formed at an upper-surface outer peripheral section of the cover  5  so as to prevent lubricant  20  from falling to the exterior upon the charging thereof following assembly of this hydrodynamic bearing. The lube-repellant coating recess  24  is, for example, a groove having an inner diameter of between approximately 3.5 and 6.0 mm, a width of between approximately 0.2 and 1.0 mm, and a depth of between approximately 0.03 and 0.1 mm. 
     When, in the above-explained configuration, the shaft  1  and the sleeve  2  are rotated relatively by a rotation drive force of a spindle motor, the shaft  1  is supported in a condition wherein a fixed gap is maintained with respect to the sleeve  2  by the force of the lubricant  20  drawn out by the hydrodynamic grooves  7 ,  8  of the radial flow bearing and the force of the lubricant  20  collected and drawn out by the hydrodynamic grooves  9 ,  10  of the thrust flow bearing. Furthermore, the lubricant  20  between the shaft  1  and the sleeve  2  is delivered downward in an axis direction by the force of the lubricant  20  collected and drawn out by the upper hydrodynamic groove  7  of the radial flow bearing in the axis direction. Accordingly, the lubricant  20  passes in sequence through the space between the thrust flange  3  and the sleeve  2 , the space between the sleeve  2  and the thrust plate  4 , the space inside the connecting channel  6 , the introducing gap section  11 , and the sleeve end face gap section  12 , and flows once again into the space between the shaft  1  and the sleeve  2 . In this way, the lubricant  20  circulates actively within these spaces. Furthermore, a portion of the lubricant  20  introduced to the introducing gap section  11  from the connecting channel  6 , while also flowing through the sleeve end face gap section  12 , again flows into the space between the shaft  1  and the sleeve  2  via the smallest gap at the outer periphery of the bearing hole  2   a.    
     Therefore, even in situations wherein air bubbles adhere to, for example, the hydrodynamic grooves  7 ,  8  of the radial flow bearing or the hydrodynamic grooves  9 ,  10  of the thrust flow bearing, the air bubbles are detached from the hydrodynamic grooves  7 ,  8  and the hydrodynamic grooves  9 ,  10  by the circulatory flow of the lubricant  20 . Upon passage through the introducing gap section  11  from the connecting channel  6 , the air bubbles flow into the lower-pressure first lubricant reservoir section  14 . As the air bubbles grow larger upon flow thereof into the lower-pressure first lubricant reservoir section  14 , it becomes difficult for the air bubbles to again enter the higher-pressure introducing gap section  11  and the sleeve end face gap section  12 . For this reason, air bubbles are separated from the lubricant  20  in the first lubricant reservoir section  14  and are discharged from the vent hole  13 . 
     In this embodiment, as explained above, it is possible to actively discharge air bubbles from inside the lubricant  20  even during normal rotation drive. As a result of this, problems caused by air bubbles such as drops in bearing stiffness and drops in bearing performance due to, for example, instability in rotation during rotating operation can be prevented, and the reliability of the hydrodynamic bearing can be improved. 
     In addition, this hydrodynamic bearing not only provides a second lubricant reservoir section  23  on the inner peripheral surface of the cover  5  facing the shaft  1 , but also provides a large capacity space section for holding a lubricant  20  (the first lubricant reservoir section  14 ) between the outer peripheral surface of the sleeve  2  and the cover  5 . Therefore, even in situations where the volume of lubricant in the first lubricant reservoir section  14  has reduced, the introducing gap section  11  and the sleeve end face gap section  12  are filled with the lubricant  20  through an action of a capillary force, and circulating functionality can be maintained. 
     In particular, the present invention makes possible formation of the first lubricant reservoir section  14  such that separation distance from the outer peripheral side surface of the sleeve  2  increases upon drawing closer to the maximum space section  14   a  provided with the vent hole  13  from a direction of a section symmetric to the introducing gap section  11  about the axis O, or in other words, formation of the first lubricant reservoir section  14  so as to be inclined in a circumferential direction. For this reason, even in situations wherein the hydrodynamic bearing is exposed to shock from the exterior or undergoes sudden changes in attitude, the interface boundary surface between the air and the lubricant  20  in the first lubricant reservoir section  14  remains in close proximity to the vent hole  13  and motion thereof in a circumferential direction is prevented. As a result, leakage of lubricant  20  to the exterior pursuant to motion of air bubbles can be prevented. Furthermore, the size of the storage space cross-sectional area of the first lubricant reservoir section  14  is inversely proportional to distance from the vent hole  13 . As shown in  FIG. 4  by positions P, Q of the interface boundary surface upon reduction of the charge of lubricant  20 , the interface boundary surface ordinarily extends in an axis direction. Compared with a hydrodynamic bearing configured with a ring-shaped interface boundary surface as shown in  FIG. 10 , therefore, variation in the area of the interface boundary surface and associated variation in surface tension in the first lubricant reservoir section  14  can be reduced. 
     Furthermore, the sleeve end face gap section  12  stimulating capillary action is formed between the back surface of the cover  5  and an upper surface of the sleeve  2 . As a result, the lubricant  20  introduced from the introducing gap section  11  is favorably supplied from a complete periphery to the bearing hole  2   a  of the sleeve  2  via this sleeve end face gap section  12 , maintaining a stable, full condition thereof in the bearing hole  2   a  of the sleeve  2 . 
     Furthermore, inside diameters of the second lubricant reservoir section  23  (the diameter Dt at an upper end of the inclined surface  23   a  and the diameter dt at a lower end of the inclined surface dt) are formed such that the surface tension of the lubricant  20  stored in the second lubricant reservoir section  23  and the surface tension of the lubricant  20  stored in the first lubricant reservoir section  14 , facing the vent hole  13 , are substantially equalized. Accordingly, sudden changes in the position of the interface boundary surface of the lubricant  20  in the second lubricant reservoir section  23  and leakage of lubricant  20  as a result of movement of the interface boundary surface can be prevented. 
     Hereinafter, this point is explained in detail. 
       FIG. 8  is a conceptual view showing the balancing of pressure between the second lubricant reservoir section  23  and the first lubricant reservoir section  14  of the hydrodynamic bearing of this embodiment. Here, A is a pressure due to surface tension of the interface boundary surface in the second lubricant reservoir section  23 , B is volumetric pressure due to a difference in the position of the interface boundary surfaces, and C is a pressure due to surface tension of the interface boundary surface in the first lubricant reservoir section  14 . Furthermore, γ is a surface tension [N/m] of oil (lubricant); ρ is the density [kg/m 3 ] of the oil; Li is the length of contact between the interface boundary surface of the oil and a member at the interface boundary surface I; Ai is an area of the interface boundary surface of the oil at the interface boundary surface I; Lo is the length of contact between the interface boundary surface of the oil and a member at the interface boundary surface O; Ao is an area of the interface boundary surface of the oil at the interface boundary surface O; hi is a height from an upper surface of the sleeve to the interface boundary surface I; ho is an average height (t/2) from the upper surface of the sleeve to the interface boundary surface O; and θ is a contact angle between a member and the interface boundary surface of the oil. 
     In terms of the model shown in  FIG. 8 , the formula for balancing of pressures is;
 
 A=B+C[Pa]   Formula 1:
 
     A, B, and C of Formula 1 are calculated as follows.
 
 A =(γ·cos θ× Li )/ Ai   Formula 2:
 
 B =ρ·( hi−ho )  Formula 3:
 
 C =(γ·cos θ× Lo )/ Ao   Formula 4:
 
     Substituting Formula 2, Formula 3, and Formula 4 into Formula 1 gives the following.
 
 Li/Ai={ 1/(γ·cos θ)}×[ρ·( hi−ho )+{(γ·cos θ)+ Lo}/Ao]   Formula 5:
 
Substituting the following Formula 6 and Formula 7 into Formula 5 and defining the right-hand side of the equation as Z gives Formula 6.
 
 Li =π( ds+Dts )  Formula 6:
 
 Ai =π{( Dts/ 2) 2 −( ds/ 2) 2 }  Formula 7:
 
( ds+Dts )/{( Dts/ 2) 2 −( ds/ 2) 2   }=Z   Formula 8:
 
The diameter Dts of the second lubricant reservoir section  23  is found by expanding Formula 8 and resolving the equation as follows.
 
 Dts={ 1+ SQRT (1+ Z ( ds+Z×ds   2 /4))}/( Z/ 2)  Formula 9:
 
By finding the diameter Dts for the largest and smallest interface boundary surfaces of the oil using Formula 9 and setting the inner diameters of the top seal (dt, Dt) so as to fully accommodate the range of motion of that interface boundary surface, the surface tension of the lubricant  20  stored in the second lubricant reservoir section  23  and the surface tension of the lubricant  20  stored in the first lubricant reservoir section  14 , facing the vent hole  13 , are substantially equalized. Accordingly, sudden changes in the position of the interface boundary surface of the lubricant  20  in the second lubricant reservoir section  23  and leakage of lubricant  20  as a result of due to movement of the interface boundary surface can be prevented.
 
     In the above-explained embodiment, furthermore, a lube-repellant coating recess  24  for coating of lube repellant is formed as a depression in an upper-surface outer peripheral section of the cover  5 . Accordingly, the lube-repellant coating recess  24  prevents the lubricant  20  from flowing and falling from an upper surface of the cover  5  upon the charging thereof following assembly of the hydrodynamic bearing, and therefore, operation efficiency can be improved and reduction of the volume of lubricant  20  charged to the sleeve  2  can also be prevented. As a result, the reliability of the hydrodynamic bearing can be improved. 
       FIG. 9  is a view of an information recording and reproducing apparatus  53  using a spindle motor provided with the hydrodynamic bearing according to the present invention. Although the hydrodynamic bearing according to the prevent invention is particularly suitable for the spindle motors of disk drive devices, reel drive devices, capstan drive devices, drum drive devices, and other information recording and reproducing apparatuses, the usage thereof is not limited to these applications, and the hydrodynamic bearing according to the prevent invention can also be used in other devices such as, for example, MPU fans used to cool the MPUs used in personal computers.