JPH11191944A - Spindle motor and rotary shaft supporting device of laser beam printer - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a spindle motor capable of noise suppression and cost reduction and, furthermore improvement in printing precision. SOLUTION: A polygon mirror 11 is attached to a rotary shaft 3. The rotary shaft 3 is driven to rotation by an excitation force induced between a rotor 14 and a stator 13, while it is freely rotatably supported by a bearing 1. The bearing 1 has a porous bearing main part, which has a bearing surface facing opposite to the outer circumference of the rotary shaft 3 with a bearing gap therebetween, lubrication oil or lubrication grease, with which the bearing main part is impregnated and a dynamic pressure channel formed on the bearing surface of the bearing main part. The bearing 1 supports the rotary shaft 3 in a noncontact manner with a dynamic pressure oil film made of the lubrication oil in the bearing gap and the oil is circulated between the inside of the bearing main part and the bearing gap via open holes in the surface of the bearing main part.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] 1. Field of the Invention [0002] The present invention relates to a spindle motor of a laser beam printer (LBP) and a rotating shaft supporting device provided on the motor.

[0002]

2. Description of the Related Art LBP spindle motors are required to have high rotational accuracy, high speed, low cost, low noise, and the like. One of the components that determine these required performances is a support device that supports the spindle of the motor. Conventionally, a support device using a ball bearing or a sintered oil-impregnated bearing is used as the support device.

[0003]

However, the use of ball bearings has the following disadvantages.

The spindle motor of LBP is 10,000 to 30,000 r
It is often used at a high speed of about pm. Race sound peculiar to ball bearings (the sound of a ball rolling on a raceway)
Also, noise is generated due to self-excited vibration of the cage, and when used at high speed, the noise level is large, and noise reduction has reached its limit. In addition, ball bearings, outer ring, inner ring, ball,
Since it is made up of many components such as a cage, a seal, and grease, there is a limit to cost reduction and high accuracy.

On the other hand, a sintered oil-impregnated bearing is superior to a ball bearing in terms of performance such as low noise, small number of parts and easy control of accuracy. However, since the rigidity of the oil film is low, and unstable vibration called “whirl” peculiar to a perfect circular bearing is generated, the jitter required to accompany the recent high speed and high performance of the LBP is 0.02% or less. It means that it is difficult to achieve an irregular variation of a pulse amplitude or a parameter on a time axis in a pulse train of a reflected light from a polygon mirror or a value of the variation, and further improvement is desired. In the case of a sintered oil-impregnated bearing, air is also entrained with the rotation. However, under high-speed rotation, the entrained amount of air is increased, and the formation of an oil film is hindered. If the oil film formation is insufficient, metal contact occurs between the shaft and the bearing, and wear proceeds, which causes a problem in durability.

Accordingly, an object of the present invention is to provide an LBP spindle motor and a rotating shaft supporting device thereof, which solve the above-mentioned problems of ball bearings and sintered oil-impregnated bearings.

[0007]

In order to achieve the above object, a spindle motor according to the present invention comprises a rotating shaft on which a polygon mirror is mounted, a bearing for rotatably supporting the rotating shaft, A rotor having a rotor provided on a rotating member that rotates together with the rotating shaft, and a stator provided on a stationary member, wherein the rotating shaft has a diameter of 5 mm or less, and the bearing comprises an outer peripheral surface of the rotating shaft and a bearing. A bearing body made of a porous sintered metal having a bearing surface opposed via a gap, lubricating oil or lubricating grease impregnated in the bearing body, and provided on the bearing surface of the bearing body so as to be inclined with respect to the axial direction. The rotating shaft is provided in a non-contact manner by a dynamic pressure oil film of lubricating oil formed in the bearing gap, and the oil is supplied to the inside of the bearing body and the bearing gap through an opening in the surface of the bearing body. When It is intended to circulate between (claim 1).

[0008] In addition, a rotation shaft supporting device for an LBP spindle motor according to the present invention is provided with a rotation shaft on which a polygon mirror is mounted and which is rotated by an exciting force generated between the rotor and the stator to rotate the polygon mirror. And a bearing that rotatably supports the rotating shaft,
A bearing body made of a porous sintered metal having a diameter of the rotating shaft of 5 mm or less, the bearing having a bearing surface opposed to an outer peripheral surface of the rotating shaft via a bearing gap, and a bearing body impregnated with the bearing body. Equipped with lubricating oil or lubricating grease, and a dynamic pressure groove provided on the bearing surface of the bearing body at an angle to the axial direction. The rotating shaft is supported in a non-contact manner by a lubricating oil film formed in the bearing gap. At the same time, the oil is circulated between the inside of the bearing body and the bearing gap through an opening in the surface of the bearing body (claim 8).

In the bearing (porous oil-impregnated bearing), the lubricant (lubricating oil or lubricating grease base oil) inside the bearing body is rotated by the rotation of the rotating shaft, and the inner peripheral surface of the bearing body (including the inner diameter chamfer portion). ) And is drawn into the bearing gap. The oil drawn into the bearing gap forms a lubricating oil film and supports the rotating shaft in a non-contact manner. At this time, if a plurality of dynamic pressure grooves (for example, a herringbone type or a spiral type) are provided on the bearing surface inclined with respect to the axial direction, the lubricant inside the bearing main body can be further increased by the dynamic pressure action. Since the lubricant is continuously pushed into the bearing surface while being drawn into the gap, the oil film strength is increased, and the rigidity of the bearing can be improved. In addition, unstable vibration called whirl such as a perfect circular bearing does not occur.

When a positive pressure is generated in the bearing gap, there is a hole in the surface of the bearing surface (opening portion: a portion in which pores of the porous body structure are opened on the outer surface). Although the oil returns to the inside, new lubricant continues to be pushed into the bearing gap one after another, so that the oil film force and the rigidity are maintained in a high state. Accordingly, high rotational accuracy can be obtained, and a jitter of 0.02% or less required for recent LBP can be achieved. Further, since the shaft and the bearing main body rotate in a non-contact manner, low noise and low cost are obtained. Furthermore, unlike ordinary hydrodynamic plain bearings that are not porous, even when bubbles are generated or entrained in the oil film, the oil is circulated, so the bubbles are absorbed inside the bearing body and the bearing function is improved. There is no instability.

The ratio between the groove depth h of the dynamic pressure groove and the bearing clearance c is expressed by
If c / h is set to 0.5 to 2.0 (claim 2,
9) The printing accuracy can be improved by further suppressing jitter and the like.

The kinematic viscosity of the lubricating oil or lubricating grease base oil impregnated in the bearing body is at least 5 cSt at 40 ° C.
St or less is preferable (claims 3 and 10).

[0013] When the surface porosity of the bearing surface is set to 2% or more and 12% or less (claims 4 and 11), the amount of oil recirculation into the inside of the bearing body and the amount of oil seeping out are balanced, and practically A favorable oil film strength (bearing rigidity) can be secured.

The bearing surface has a first groove region in which a plurality of dynamic pressure grooves inclined to one side with respect to the axial direction are arranged in the circumferential direction, and is axially separated from the first groove region, and is axially separated from the first groove region. On the other hand, it has a second groove region in which a plurality of dynamic pressure grooves inclined in the other direction are arranged in the circumferential direction, and a smooth portion located between the first and second groove regions. , 12). According to this configuration, the dynamic pressure grooves formed in the two regions in opposite directions collect the oil around the smooth portion, so that the oil film pressure in this portion increases. Further, since there is no dynamic pressure groove in the smooth portion, the bearing rigidity can be increased as compared with a continuous bearing in which the dynamic pressure groove is continuous in the axial direction, and the shaft runout can be further reduced.

By forming a plurality of bearing surfaces spaced apart from each other in the axial direction on the inner diameter surface of the bearing body (claim 6), it is possible to avoid adverse effects such as poor accuracy which may be a problem when a plurality of bearings are arranged separately. be able to.

The bearing body is fixed to the inner diameter of the housing,
By providing a ventilation path open at both axial ends of the bearing body between the outer diameter surface of the bearing body and the inner diameter surface of the housing (claim 7), the incorporation of the shaft into the bearing is improved.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS.

FIG. 1 is a sectional view of a spindle motor (generally called a polygon mirror motor or a scanner motor) provided in a laser beam printer. The spindle motor includes a rotating shaft 3 and a rotating shaft supporting device 10 having a bearing 1 for rotatably supporting the rotating shaft 3, a polygon mirror 11 mounted on an upper end of the rotating shaft 3, and an axial gap. The motor unit 15 mainly includes a stator 13 and a rotor 14 which are opposed to each other. Bearing 1
Is fixed to the inner diameter of the housing 2 (stationary member) fixed to the base 16. 17 is the polygon mirror 11 rotor hub
It is a preload spring for elastically pressing against the 18 (rotating member). When the stator 13 is energized, the rotor 14 is rotated by the exciting force between the stator 13 fixedly arranged on the outer peripheral portion of the housing 2 and the rotor 14 provided on the rotor hub 18, and the polygon mirror 11 is rotated with this rotation. Rotate. Laser light that has entered the polygon mirror 11 from a laser light source via a predetermined optical system is reflected by the polygon mirror 11 and scans the photosensitive drum surface.

The rotating shaft 3 constituting the supporting device 10 has a diameter of 5 mm or less. The lower limit value of the diameter of the rotating shaft 3 is arbitrary, but is preferably 2 mm or more in consideration of various factors such as shaft rigidity and manufacturing cost.

The bearing 1 is fixed to the inner diameter of the housing 2 by press-fitting or bonding. As shown in FIGS. 2 and 3, this bearing 1 has a cylindrical bearing body 1a made of a porous sintered metal having a bearing surface 1b opposed to an outer diameter surface of a rotating shaft 3 via a bearing gap 4. Is impregnated with lubricating oil or lubricating grease. Bearing body 1a made of sintered metal
Is formed of a sintered metal containing copper or iron, or both as a main component, and desirably uses copper in an amount of 20 to 95% by weight and has a density of 6.4 to 7.2 g / cm ^3. Molded. In addition to the sintered metal, a thick cylindrical porous body having a large number of pores obtained by sintering, foaming, or the like of cast iron, synthetic resin, ceramic, or the like may be used.

As the lubricating oil or the base oil of the lubricating grease, one having a kinematic viscosity at 40 ° C. of 5 to 20 cSt is used. If the kinematic viscosity at 40 ° C. is larger than 20 cSt, an increase in torque will hinder high-speed driving, resulting in a decrease in printing accuracy or the like, or it will be difficult to stabilize the starting torque early. Conversely, if it is smaller than 5 cSt, the kinematic viscosity is too small, and the oil is liable to be scattered, causing a problem in durability. When lubricating grease is used as the lubricant, the apparent viscosity of the lubricant other than the bearing gap 4 that receives shearing force is significantly larger than that of oil, and it is difficult to flow out to the surroundings. However, if the amount of the thickener mixed and dispersed in the oil is more than 5% by weight, the apparent viscosity is too high to impregnate the bearing body, and the work of removing excess grease adhering to the surface after the impregnation is complicated. Becomes On the other hand, 0.5 wt
If it is less than%, the effect of grease is small, and the degree of outflow is not different from that in the case of using oil. Therefore, the thickener concentration of the lubricating grease is 0.5 to 5.0 wt%.
Use the one set in. The type of the lubricating oil or the lubricating grease base oil is not particularly limited, but a poly-α-olefin type, an ester type synthetic oil (a diester, a polyol ester type synthetic oil), or a mixed oil of both is suitable. In addition, as a thickener for lubricating grease,
A lithium thickener which is easy to handle and has excellent productivity is suitable.

On the inner periphery of the bearing body 1a, two bearing surfaces 1b which are separated in the axial direction are formed, and both of the two bearing surfaces 1b
A plurality of dynamic pressure grooves 1c (herringbone type) each inclined with respect to the axial direction are arranged and formed in the circumferential direction. Dynamic pressure groove
It is sufficient that 1c is formed to be inclined with respect to the axial direction, as long as this condition is satisfied, other shapes other than the herringbone type,
For example, it may be a spiral type. The inclination angle of the dynamic pressure groove 1c is basically set to an arbitrary angle, but is preferably set such that the angle in a direction orthogonal to the axial direction is 15 to 40 ° (more preferably 15 to 25 °). Is done. The width ratio of the dynamic pressure groove 1c and the width of the back portion 1e between the dynamic pressure grooves 1c is 0.8 to
It is good to set it between 1.5 and desirably between 1.0 and 1.2.

In the present invention, a single bearing body is provided, and a plurality of (two in this embodiment) hydrodynamic bearing surfaces are provided on the inner surface of the bearing body.
1b is provided in order to avoid adverse effects such as poor accuracy, which would be a problem when a plurality of bearings 1 are arranged separately. That is, if a plurality of bearings 1 are temporarily
, The accuracy of each bearing, such as the coaxiality and cylindricity, becomes a problem. If the accuracy is poor, the rotating shaft 3 and the bearing 1 come into line contact. In the worst case, the rotating shaft 3 has two bearings. It may also happen that it does not penetrate. On the other hand, if a plurality of bearing surfaces 1b are formed on the bearing main body 1a as in the present invention, this kind of problem can be avoided.

The two bearing surfaces 1b are provided with a first groove region m1 in which the inclined hydrodynamic grooves 1c are arranged on one side, and a hydrodynamic groove 1c axially separated from the first groove region m1 and inclined on the other side. The second array of
Groove region m2 and an annular smooth portion n located between the two groove regions m1 and m2. The dynamic pressure groove 1c of the two groove regions m1 and m2 is partitioned by the smooth portion n and is It is continuous. The back portion 1e between the smooth portion n and the dynamic pressure groove 1c is at the same level. This type of non-continuous type dynamic pressure groove 1c is a continuous type, that is, compared with a case where the smooth portion n is omitted and the dynamic pressure groove 1c is formed in a V-shape that is continuous with each other between both groove regions m1 and m2. There is an advantage that the oil film pressure is high because oil is collected around the smooth portion n, and the bearing rigidity is high because the smooth portion n has no groove.

In general, it is said that the herringbone type dynamic pressure groove has no negative pressure inside the bearing in the continuous type, so that no bubbles are generated and the oil sealing property is excellent. When the bearing body 1a is a porous body as in the invention, since oil circulates between the bearing gap 4 and the inside of the bearing,
Even if bubbles are generated, they are not absorbed into the inside of the bearing. Therefore, it is considered that there is no problem that the oil is pushed out of the bearing gap 4 by the bubbles and the sealing property is impaired.

It should be noted that the continuous type dynamic pressure groove is not particularly essential (a continuous type dynamic pressure groove may be used) since a continuous type dynamic pressure groove may be rather preferable depending on the use conditions and the like.

Assuming that the axial width of each bearing surface 1b is 1, the ratio R of the smooth portion n in the bearing width direction is R = 0.1-0.
6 is preferable, and R is preferably set in the range of 0.2 to 0.4. If the bearing surface width 1 is less than 0.1,
The effects (increase in dynamic pressure and increase in bearing rigidity) due to the provision of the smooth portion n do not appear remarkably, and are the same as in the case of continuous grooves. Further, when R is larger than 0.6 with respect to the bearing width 1, the dynamic pressure groove is reduced, and the force for pushing the oil into the axial center becomes weak, so that the dynamic pressure effect is not effectively exhibited.

The ratio between the groove depth of the dynamic pressure groove 1c (h: see FIG. 3) and the bearing radial gap c (difference between the radius of the inner diameter surface of the bearing body and the radius of the outer diameter surface of the rotating shaft) is given by There is an optimum range, and it is considered that a sufficient dynamic pressure effect cannot be obtained outside this range. In order to clarify this optimum range, the jitter was measured using an actual LBP motor. As a result, if the c / h was in the range of 0.5 to 2.0, the jitter could be suppressed to a practically sufficient level. found. For example, if the groove depth h is 2 to 4 μm, the bearing radial gap c may be set in the range of 2 to 4 μm.

The dynamic pressure groove 1c described above can be formed, for example, by compression molding. That is, a concave / convex groove shape corresponding to the shape of the dynamic pressure groove 1c is formed on the outer peripheral surface of a core rod (for example, a sizing pin), and the sintered metal that is the material of the bearing body 1a is supplied to the outer peripheral surface of the core rod. A pressing force is applied to the metal to press the inner diameter portion thereof into the groove of the core rod, and the dynamic pressure groove 1c corresponding to the shape of the groove is transferred to the inner diameter portion. At this time, the back portion 1e and the dynamic pressure groove 1c can be formed simultaneously. After the formation of the dynamic pressure grooves, the core rod can be released from the inner diameter of the sintered metal without breaking the dynamic pressure grooves 1c by utilizing the springback of the sintered metal by removing the pressing force.

In this case, if the sizing pin for transferring the dynamic pressure groove 1c is finished with high accuracy, the accuracy of the bearing is also improved. It is not so difficult to finish the sizing pin with required precision, for example, within a circularity of 1 μm or less and a cylindricity of 2 μm or less, and it can be easily achieved.

Before performing the above-described dynamic pressure groove sizing, it is preferable to perform rotational sizing on the inner diameter portion of the sintered metal so that the distribution of apertures on the inner diameter surface is made uniform in advance. At this time, the surface porosity of the bearing surface 1b is 2% or more and 12% or less,
Desirably, it is set to about 5%, which is smaller than the surface porosity of a general sintered oil-impregnated bearing without dynamic pressure grooves (usually about 20 to 30%). This is because, if the surface porosity is too large, the oil in the bearing gap 4 tends to escape into the bearing and the dynamic pressure decreases. The setting of the surface porosity is
In addition to performing the surface treatment such as rotational sizing as described above, it can be performed by setting the density of the bearing main body 1a in advance, or by using both the surface treatment and the setting of the density.

Normally, the rotating shaft 3 is provided on the housing 2 with a thrust plate 7 for supporting the lower end of the rotating shaft 3.
Is inserted into the inner diameter of the bearing 1. At the time of this insertion, air escapes from the bearing gap 4 between the bearing 1 and the rotating shaft 3, but since the bearing gap 4 is only about several μm, air is trapped in the space below the housing 2 and the rotating shaft 3 Insertion becomes difficult. In addition, when the motor is driven, heat is generated. However, the heat may cause the trapped air to expand and push up the rotating shaft 3 to destabilize the bearing performance.

In this case, as shown in FIGS. 1 and 2, between the outer diameter surface of the bearing main body 1a and the inner diameter surface 2a of the housing 2, a ventilation path 8 opening at both axial ends of the bearing main body 1a is formed. It is sufficient if air is released through the ventilation path 8. The air passage 8 can be formed by providing an axial groove on the outer diameter surface of the bearing main body 1a, but may be provided on the inner diameter surface of the housing. The grooves may be provided not only at one place on the outer diameter surface of the bearing body 1a but also at a plurality of places in the circumferential direction.

[0034]

As described above, according to the rotating shaft supporting apparatus of the present invention, the rotating shaft is supported in a non-contact manner by the hydrodynamic oil film of the lubricating oil formed in the bearing gap, and the opening in the surface of the bearing main body. Since oil is circulated between the inside of the bearing main body and the bearing gap through the portion, noise and cost can be reduced as compared with a rotating shaft supporting device using a ball bearing. In addition, compared to the case of using a sintered oil-impregnated bearing without a dynamic pressure groove, the dynamic pressure action of the dynamic pressure groove can increase the bearing rigidity and improve the rotational accuracy, and the LBP spindle motor is evaluated. Jitter, which is one of the typical characteristics, can be reduced. Further, since a good oil film is always formed on the bearing surface, the durable life can be greatly improved.

According to the spindle motor of the present invention, noise and cost can be reduced, and the LBP printing accuracy can be improved.

[Brief description of the drawings]

FIG. 1 is a sectional view of a spindle motor provided in a laser beam printer.

FIG. 2 is a cross-sectional view of the spindle motor support device.

FIG. 3 is a radial cross-sectional view of the support device.

[Description of Signs] 1 Bearing 1a Bearing body 1b Bearing surface 1c Dynamic pressure groove 2 Housing 3 Rotary shaft 4 Bearing gap 8 Ventilation path 10 Rotary shaft support device 11 Polygon mirror 13 Stator 14 Rotor m1 First groove area m2 Second Groove area n Smooth part

Claims (14)

[Claims] A rotating shaft on which a polygon mirror is mounted;
A bearing that rotatably supports the rotating shaft, a rotor provided on the rotating shaft or a rotating member that rotates with the rotating shaft, and a stator provided on a stationary member, wherein the diameter of the rotating shaft is 5 mm or less, wherein the bearing is made of a porous sintered metal having a bearing surface opposed to an outer peripheral surface of a rotating shaft via a bearing gap, and a lubricating oil or lubricating grease impregnated in the bearing body. A dynamic pressure groove provided on the bearing surface of the bearing body so as to be inclined with respect to the axial direction. The dynamic pressure oil film of the lubricating oil formed in the bearing gap supports the rotating shaft in a non-contact manner, and the surface of the bearing body. A spindle motor for a laser beam printer, wherein oil is circulated between the inside of a bearing body and a bearing gap through an opening of the laser beam printer. 2. The laser beam printer according to claim 1, wherein a ratio of a groove depth h of the dynamic pressure groove to a bearing radial gap c is c / h = 0.5 to 2.0. Spindle motor. 3. The kinematic viscosity at 40 ° C. of a lubricating oil or a lubricating grease base oil impregnated in a bearing body is 5 cSt or more.
3. The spindle motor for a laser beam printer according to claim 1, wherein the spindle motor is 20 cSt or less. 4. The spindle motor for a laser beam printer according to claim 1, wherein the surface porosity of the bearing surface is 2% or more and 12% or less. 5. A first groove region in which a plurality of dynamic pressure grooves whose bearing surfaces are inclined in one direction with respect to the axial direction are arranged in a circumferential direction,
A second groove region in which a plurality of hydrodynamic grooves which are axially separated from the first groove region and inclined to the other with respect to the axial direction are arranged in a circumferential direction, and between the first and second groove regions. 5. The spindle motor for a laser beam printer according to claim 1, further comprising: 6. A spindle motor for a laser beam printer according to claim 1, wherein a plurality of bearing surfaces are formed on an inner diameter surface of the bearing body so as to be spaced apart in an axial direction. 7. A bearing body is fixed to an inner diameter portion of a housing, and between an outer diameter surface of the bearing body and an inner diameter surface of the housing.
7. The spindle motor for a laser beam printer according to claim 1, wherein ventilation passages are provided at both ends in the axial direction of the bearing body. 8. A motor having a polygon mirror mounted thereon and having a rotating shaft that is driven to rotate by an exciting force generated between a rotor and a stator to rotate the polygon mirror, and a bearing that rotatably supports the rotating shaft. Wherein the diameter of the rotating shaft is 5 mm or less, the bearing is made of a porous sintered metal having a bearing surface opposed to an outer peripheral surface of the rotating shaft via a bearing gap, and the bearing body is impregnated with the bearing body. Lubricating oil or lubricating grease, and a dynamic pressure groove provided on the bearing surface of the bearing body so as to be inclined with respect to the axial direction, and the rotating shaft is not in contact with the dynamic pressure oil film of the lubricating oil formed in the bearing gap A rotary shaft support device for a spindle motor of a laser beam printer, which supports and circulates oil between the inside of the bearing body and the bearing gap through an opening in the surface of the bearing body. 9. The laser beam printer according to claim 8, wherein the ratio of the groove depth h of the dynamic pressure groove to the bearing radial gap c is c / h = 0.5 to 2.0. Spindle motor rotation shaft support device. 10. The rotation of a spindle motor of a laser beam printer according to claim 8, wherein the kinematic viscosity at 40 ° C. of the lubricating oil or lubricating grease base oil impregnated in the bearing body is 5 cSt or more and 20 cSt or less. Shaft support device. 11. The surface porosity of the bearing surface is 2% or more and 12% or more.
The rotating shaft support device for a spindle motor of a laser beam printer according to any one of claims 8 to 10, wherein: 12. A first groove region in which a plurality of dynamic pressure grooves inclined in one direction with respect to the axial direction are arranged in a circumferential direction, a bearing surface is axially separated from the first groove region, and the bearing surface is axially separated from the first groove region. A plurality of dynamic pressure grooves inclined in the other direction with respect to the direction are arranged in the circumferential direction.
The rotary shaft support device for a spindle motor of a laser beam printer according to any one of claims 8 to 11, further comprising: a groove region; and a smooth portion located between the first and second groove regions. 13. A rotary shaft supporting device for a spindle motor of a laser beam printer according to claim 8, wherein a plurality of bearing surfaces are formed on an inner diameter surface of the bearing body so as to be spaced apart in an axial direction. 14. A bearing body is fixed to an inner diameter portion of a housing, and between an outer diameter surface of the bearing body and an inner diameter surface of the housing.
14. The rotating shaft support device for a spindle motor of a laser beam printer according to claim 8, wherein ventilation passages are provided at both ends in the axial direction of the bearing body.