JP2002258202A - Light deflecting scanner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a light deflecting scanner where undesired sound caused by electro-magnetic noise during motor driving rotation can be greatly reduced. SOLUTION: In the light deflecting scanner provided with a light source, a motor for deflector where luminous flux generated by the light source is deflected and scanned and scanning optical lens 20 to have the luminous flux from the motor for deflector scanned over a photosensitive body at approximately equal speed, outer diameter of rotor Dr of the motor for deflector and outer diameter of cylindrical part dk2 and inner diameter dk1 of a stator core 15 are set so that Dr<=40 mm dk1<=0.60×dk2 are satisfied.

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an optical deflection scanning device for deflecting and scanning a light beam at a high speed using a scanning optical lens, such as a laser printer. 2. Description of the Related Art In a scanning optical apparatus used for an image forming apparatus such as a laser beam printer and a laser facsimile,
A light beam such as a laser beam is deflected and scanned by a rotating polygon mirror rotating at a high speed, and the obtained scanning light is imaged on a rotating drum-shaped photosensitive member to form an electrostatic latent image. The electrostatic latent image on the photoreceptor is developed by a developing device to be visualized as a toner image, and the toner image is transferred to a recording medium such as recording paper and sent to a fixing device. Is heated and fixed to perform printing. In recent years, non-contact rotating hydrodynamic bearings have been used in optical deflection scanning devices as increasingly high-speed and high-precision rotating devices. In particular, so-called pneumatic bearings are mainly used for high-speed rotation, but oil-type hydrodynamic fluid bearings are now being used instead of pneumatic bearings, which are required to be small and thin and cost-effective. . FIG. 19 shows a main section of a conventional light deflection scanning apparatus. In FIG. 19, reference numeral 101 denotes a deflector motor, 10
2 is a rotating polygon mirror having a plurality of mirror surfaces 102a, 103 is a rotating shaft, 104 is a sleeve, 105 is a thrust disk receiver, 106 is a lubricating fluid filled between the rotating shaft 103, the sleeve 104 and the thrust disk receiver 105, 104
Reference numerals a and 104b denote wedge-shaped shallow grooves formed in the sleeve 104. When the rotating shaft 103 rotates clockwise as viewed from the direction A, the lubricating fluid 106
The pressure is increased by being taken into the central portions of the wedge-shaped shallow grooves 104a and 104b formed in the groove 104, and the rotating shaft 103 is held away from the sleeve 104. Thrust disk holder 10
5, the end 103c of the rotating shaft 103 is in contact with the rotating shaft 103.
03 is held in the thrust direction. Reference numeral 107 denotes a rotating polygon mirror receiving seat fixedly fitted to the rotating shaft 103, reference numeral 108 denotes a rotor yoke fixed to the polygon mirror receiving seat 107 by caulking, and reference numeral 109 denotes a rotor magnet adhered and fixed to the rotor yoke 108. The rotary polygon mirror 102 is mounted on a rotary polygon mirror receiving seat 107, which is fixed by a wave washer 110, a holding ring 111, and a retaining ring 112 for holding and fixing these to a rotating shaft 103. On the other hand, a plurality of stator coils 113 are provided on a stator core 115 on a motor circuit board 114,
By applying a current to the stator coil 113 to generate a rotating magnetic force, a rotating torque is generated between the rotor magnet 109 and the rotor magnet 109 and the rotating shaft 10.
The rotor unit including the polygon mirror 3 and the rotating polygon mirror 102 is driven to rotate. However, in the above prior art, the stator coil 11 is driven by a drive current supplied from a drive circuit formed on the motor circuit board 114.
3, when the stator coil 113 is excited by the current flowing through the rotor 3 and the rotor magnet 109 facing the stator coil 113 is rotated by the rotating magnetic force, the stator core 11 is rotated.
5 itself vibrates, and vibrates at a frequency near a frequency unique to the stator core 115 itself (a so-called natural frequency). The natural vibration of the stator core 115 is transmitted to the motor circuit board 114 from a terminal pin or the like that fixes the stator core 115 using air as a medium, and further propagated to the optical box. In the ear. Generally, the electromagnetic sound generated from the stator core 115 is caused by the natural frequency of the stator core 115, and is unpleasant to humans when a peak occurs in an audible band (a frequency band of 20 Hz to 18 kHz) that can be felt by humans. It feels like a good sound. Also, unlike the fundamental frequency component of the number of revolutions, it is impossible to easily lower the frequency peak value by adjusting the unbalance of the rotor. From the design stage, it was necessary to pay attention to the shape of the stator core. This is because in a general rotary drive motor, the inner peripheral portion of the stator core inevitably escapes the rotating shaft and the bearing portion, so that the central portion has a hollow structure in which a cylindrical portion is formed. A notch is provided in the outer peripheral portion of the stator core so as to obtain an optimal rotating magnetic force for satisfying the basic characteristics of the motor such as the number of rotations used, the starting time, and the current consumption, and a slot for winding the stator coil. The (groove) portion and the teeth portion are formed, and an electric wire such as a polyester wire is wound to form a stator coil. However, with the recent increase in the rotational speed, a reduction in the start-up time is required, and in order to satisfy this, it is necessary to keep the inertia low, so that the outer diameter of the rotor of the deflector motor must be reduced. I had to. Further, when an optical lens or the like approaches due to the reduction in the size of the scanning optical system, the diameter of the rotor must be reduced. This results in a structure that is very weak against vibration from the viewpoint of the mechanical characteristics (rigidity) of the stator core itself. In this case, if the natural frequency of the stator core has a peak in the audible band (frequency band of 20 Hz to 18 kHz). However, this causes electromagnetic noise to be generated in the vicinity of the natural frequency of the stator core. [0012] Generally, the natural frequency of the stator core is from 2000 Hz to 18000 due to the high speed rotation (10000 rpm or more) specification and the small diameter of the rotor (φ40 mm or less).
It is known from simulation that the noise is generated in the vicinity of Hz. For this reason, the electromagnetic noise has significantly reduced the noise in an office environment or the like. SUMMARY OF THE INVENTION The present invention has been made in consideration of the above problems, and has as its object to provide an optical deflection scanning device capable of greatly reducing noise due to electromagnetic noise during motor drive rotation. . In order to achieve the above object, the invention according to claim 1 comprises a light source, a motor for a deflector for deflecting and scanning a light beam generated from the light source, and a motor for the deflector. of the optical deflection scanning apparatus provided with a substantially constant speed to the scanning optical lens for scanning on a photosensitive member a light beam, a rotor outer diameter Dr and the stator core cylindrical outer diameter dk ₂ and an inner diameter dk ₁ of the deflector motor, Dr ≦ 40 mm dk ₁ ≦ 0.60 × dk ₂ . According to a second aspect of the present invention, in the first aspect of the present invention, the cross-sectional shape of the stator core is a polyhedral shape in which the outer diameter dk ₂ and the inner diameter dk of the stator core cylindrical portion are circumscribed circles or inscribed circles. Features. According to a third aspect of the present invention, in the first aspect of the present invention, a ring-shaped bush is provided inside the inner diameter portion of the stator core cylindrical portion. According to a fourth aspect of the present invention, in the third aspect of the present invention, the bush is brought into contact with another component other than the stator core. Therefore, according to the present invention, the rotor outer diameter Dr
Is reduced to 40 mm or less, so that it is possible to realize a low inertia and satisfy the demand for shortening the start-up time due to the high speed, and to obtain a ratio dk ₁ / dk of a stator core cylindrical portion inner diameter dk ₁ to a stator core cylindrical portion outer diameter dk ₂ . _{When 2} is set to 0.6 or less, the peak value of the natural frequency of the stator core can be reduced, and it has been experimentally confirmed that the vibration of the stator core itself is kept low. Also, the natural frequency of the stator core can be moved out of the audible band (frequency band of 20 Hz to 18 kHz), and the electromagnetic sound can be made lower than the resolution of the human ear to make it substantially difficult to hear. In addition, the noise of the light deflection scanning device can be greatly reduced. Embodiments of the present invention will be described below with reference to the accompanying drawings. <Embodiment 1> FIG. 1 is a sectional view of an optical deflection scanning apparatus according to Embodiment 1 of the present invention. In FIG. 1, reference numeral 1 denotes a motor for a deflector, and 2 denotes a rotary having a plurality of mirror surfaces 2a. Polyhedral mirror, 3 is a rotating shaft, 4 is a sleeve, 5 is a thrust disk receiver, 6 is a lubricating fluid filled between the rotating shaft 3 and the sleeve 4 and the thrust disk 5, 4a and 4b are sleeves 4
Is a wedge-shaped shallow groove engraved in the groove. When the rotating shaft 3 rotates clockwise as viewed from the direction A in FIG. 1, the lubricating fluid 6 is taken into the central portions of the wedge-shaped shallow grooves 4a and 4b of the sleeve 4, and the pressure increases. , The rotating shaft 3 is held apart from the sleeve 4. The end 3c of the rotating shaft 3 abuts on the thrust disk receiver 5, and holds the rotating shaft 3 in the thrust direction. Numeral 7 denotes a rotary polygon mirror receiving seat fixedly pressed into the rotary shaft 3, reference numeral 8 denotes a rotor yoke fixed to the polygon mirror receiving seat 7 by caulking, and reference numeral 9 denotes a rotor magnet bonded and fixed to the rotor yoke 8. The rotary polygon mirror 2 is mounted on a rotary polygon mirror receiving seat 7, which is fixed by a wave washer 10, a holding ring 11, and a retaining ring 12 for holding and fixing these to the rotating shaft 3. Reference numeral 20 denotes a scanning optical lens, and reference numeral 21 denotes a mirror pedestal provided in an optical box (not shown). FIG. 2 is a cross-sectional view of the rotor section shown in FIG. 1. As shown in FIG. 2, a stator coil 15a is soldered and fixed on a motor circuit board 14 via terminal pins 15b. A plurality of coil windings are provided on the teeth portion 17 of the stator coil 15a, and a current is applied to the stator coil 15a to generate a rotating magnetic force in the slot portion 16, thereby generating a rotating torque with the rotor magnet 9. The rotor unit including the rotor magnet 9, the rotating shaft 3 and the rotating polygon mirror 2 is driven to rotate. However, in recent years, there has been a demand for a reduction in the start-up time associated with an increase in the number of rotations. For laser beam printers and the like, a start-up time of 5 seconds or less is an essential condition. In order to satisfy this, the rotational torque, the moment of inertia and the number of revolutions have a great influence, and the size of the motor, that is, the rotor outer diameter Dr is substantially determined by these parameters. This relationship is represented by the following equation and is illustrated in FIG. T = I × ω / Md (1) t: activation time, I: moment of inertia, ω: rotation speed, M
d: Rotational torque FIG. 3 is a diagram showing the relationship between the starting time t and the rotor outer diameter Dr. Here, the starting torque is determined by the rotor magnet 9.
The ferrite magnet is generally used as the rotor magnet 9, and the rotation speed is 200
In order to satisfy the starting time of 5 sec or less when the starting torque is 300 gf · cm or less at 00 rpm, the rotor outer diameter Dr must be 40 mm or less.
In particular, when the rotation speed exceeds 20,000 rpm, the rotor outer diameter Dr of the deflector motor 1 must be further reduced. In the present embodiment, a ferrite magnet is used for the rotor magnet 9, but the same applies when a high rare earth magnet such as neodymium is used. Here, the rotor outer diameter Dr is, as shown in FIG. 4B, a double distance from the center of rotation of the rotating shaft 3 to the side surface 8a on which the rotor magnet 9 is back-yoke.
Further, the stator core cylindrical outer diameter dk ₂ in outer rotor slotted motor is smaller than the rotor outside diameter Dr, the finding of this _{relation, dk 2 = Dr-2 ×} (try + tmg + Agap) ... (2) try: rotor yoke 8 Thickness, tmg: Thickness of rotor magnet 9 Agap: Air gap (gap between rotor magnet 9 and stator core 15) In the present embodiment, rotor outer diameter Dr = 22 mm,
The outer diameter dk _{2 of the} stator core cylindrical portion is 20 mm. However, when the rotor outer diameter Dr is φ4
When it is within 0 mm, the torsional stress τ acting on the stator core 15 is amplified. The relationship between the rotor outer diameter Dr and the torsional stress τ is shown in FIGS. 5 and 6, respectively. As described above, when the rotor outer diameter Dr is reduced, the outer diameter dk ₂ of the stator core cylindrical portion is reduced, and the torsional stress τ is increased. Although there are differences in specifications in terms of magnet magnetic flux density, winding wire diameter, number of turns, etc., the deflector motor 1
In a small, low-torque motor such as used in the following, the length TL of the teeth portion 17 = (Ds−d2) / 2
Is considered to be substantially constant, and the length TL of about 5 mm is sufficient. This is shown in FIG. Here, the rotational magnetic force Mt is 100 gf · cm.
Consider a degree deflector motor. Looking at the relationship between the torsional stress τ acting on the stator core cylindrical outer diameter dk ₂ In such a configuration, obtained by _{τmax = 16Mt / π × dk 2} 3 ... (3). FIG. 6 illustrates this relationship from equations (2) and (3). [0034] There Figures 6 to rise with the torsional stress τ acting on the stator core cylindrical outer diameter dk ₂ to diameter of the rotor outer diameter Dr, rapidly increased in the following particular Dr = [phi] 40 mm. For this reason, the stator core cylindrical portion outer diameter dk ₂
Has a large torsional stress τ, and is very weak in torsional rigidity. In this embodiment, since the oil dynamic pressure bearing is used, rotation is performed to satisfy the motor specifications specific to the optical deflection scanning device such as oil viscosity, bearing stiffness, shaft stiffness, startup time, and current consumption. Although the shaft diameter Ds is set to Ds = φ3 mm, the same can be said when the rotation shaft diameter Ds is set to less than φ3 mm in order to further increase the number of rotations. Therefore, it is necessary to pay sufficient attention to rigidity. Needless to say. In consideration of the case where the rotating load of the rotary polygon mirror or the like is large, the same can be said for an optical deflection scanning apparatus using a ball bearing as a bearing with a rotating shaft having a rotating shaft diameter Ds of Ds = φ3 mm or more. Therefore, it goes without saying that it is necessary to pay sufficient attention to rigidity. Next, the outer diameter dk ₂ of the stator core cylindrical portion and the inner diameter dk _{1 of the} stator core cylindrical portion constituting the central portion of the stator core 15 will be noted. FIG. 7 shows the shape of the stator core 15 and FIG.
(A)-(c) show only the cylindrical section of the stator core 15. Here, as shown in FIG. 7, the cylindrical shape of the stator core 15 is considered to be a hollow round bar having a uniform cross section. At this time, the shape of the teeth 17 and the slot 16
I will not talk about the shape of. Starter core 1 at this time
The deformation of the cross section of the cylindrical portion of No. 5 is considered as follows. That is, the torsional moment Mt is generated in the outer diameter dk ₂ of the cylindrical portion of the stator core 15 by the external force transmitted to the teeth portion 17 due to the high speed rotation of the rotor magnet 9 by the rotating magnetic force. The torsional moment Mt is a force acting on the cross section of the cylindrical portion of the stator core 15, and causes the stator core 15 to vibrate when the rotor magnet 9 is rotating. Secondary section polar moment Ip of the cylindrical portion section in this case is determined as ^{_{Ip = π × (dk 2 4}} -dk 1 4) / 32 ... (4). The magnitude of the deformation resistance against torsion can be represented by torsional rigidity B, which is obtained by the following equation. [0042] B = GIp = G × π × (dk 2 4 -dk 1 4) / 32 ... (5) G: modulus of rigidity, where the cylindrical outer diameter dk ₂ of the stator core 15 as a hollow round bar The inner diameter dk ₁ of the cylindrical portion of the stator core 15
FIG. 9 illustrates this relationship from equations (4) and (5) in order to see the relationship between the torsional stiffnesses GIp when is continuously changed. That is, the torsional rigidity GIp in the cross section of the cylindrical portion of the stator core 15 is equal to the outer diameter dk of the cylindrical portion of the stator core.
_{If the} inner diameter dk _{1 of the} stator core cylindrical portion is smaller than ₂ , the diameter can be increased to the same as a solid round bar, and the ratio dk ₁ /
It can be seen that setting dk ₂ to 0.6 or less can maximize torsional rigidity GIp. In this embodiment, when the outer diameter dk ₂ of the stator core cylindrical portion is set to φ12 mm (that is, the inner diameter dk _{1 of the} stator core cylindrical portion is φ7 mm or less), the torsional rigidity GIp almost equal to that of a solid round bar is obtained. As a result, it is possible to maximize torsional rigidity in a limited space. [0045] Incidentally, the cylindrical portion the cross section of the stator core 15 shown in FIG. 8 (a), FIG. 8 (b), and inscribed circle of the stator core cylindrical outer diameter dk ₂ and an inner diameter dk ₁ as shown in (c) Even if it is a polyhedral shape, it is desirable because the torsional rigidity GIp can be further increased. As shown in FIGS. 10 (a) and (b), d
also k ₂ and dk ₁ a polyhedral shape and the circumscribed circle, desirable in order to be further enhanced torsional stiffness GIP. Next, the natural frequency of the stator core 15 in the present embodiment is obtained by simulation analysis. FIGS. 11 (a), 12 (a), 13
(A) shows the cross-sectional shape of the stator core 15 that was actually subjected to the simulation analysis. The result is shown in FIG.
(B), FIG. 12 (b), and FIG. 13 (b).
From this, when the inner diameter dk _{1 of the} stator core shown in FIG.
_{1 for the} inner diameter dk _{1 of} φ7 mm
It can be seen that at 8000 Hz, the stator core inner diameter dk ₁ = φ6 mm shown in FIG. 13A has a natural frequency at 19000 Hz. This is shown in a graph in FIG. From this, at least the ratio dk of the outer diameter dk ₂ of the stator core cylindrical portion to the inner diameter dk ₁ of the stator core cylindrical portion is obtained.
It is understood that if ₁ / dk ₂ is set to 0.6 or less, the natural frequency of the stator core can be set to 18000 Hz or more. In the present embodiment, the shapes of the slot portion 16 and the teeth portion 17 on the outer peripheral portion of the stator core 15 are not particularly defined, but there are constraints to satisfy the motor starting characteristics, and any motor specifications The shape can be regarded as equivalent, and it is not effective enough to greatly change the natural frequency of the stator core. In the present embodiment,
Although the number of the slot portions 16 is nine, the number of slots can be set arbitrarily. Further, in this simulation analysis, since the fastening portion between the stator core and the motor circuit board has a high frequency (10000 Hz or more) component, it is considered that vibration is generated in a minute area, and no constraint condition is set. As described above, if the ratio dk ₁ / dk ₂ of the inner diameter dk _{1 of the} stator core to the outer diameter dk ₂ of the stator core is set to 0.6 or less, the rotor magnet 9 is driven to rotate by the rotating magnetic force. In this case, the vibration of the stator core 15 itself can be suppressed, and the peak value of the natural frequency can be reduced. Further, the natural frequency of the stator core 15 can be moved out of the audible band (frequency band of 20 Hz to 18 kHz), and the electromagnetic noise can be made lower than the resolution of the human ear to make it substantially difficult to hear. Therefore, it is possible to obtain an optical deflection scanning device capable of greatly reducing noise. Second Embodiment Next, a second embodiment of the present invention will be described. FIG. 15 shows the details of the optical deflection scanning device according to the second embodiment of the present invention. This embodiment is characterized in that a ring-shaped bush is provided inside the inner diameter of the cylindrical portion of the stator core of the first embodiment. Therefore, since the other configuration of the light deflection scanning device according to the present embodiment is the same as that of the light deflection scanning device according to the first embodiment, in FIG. 15, the same elements as those shown in FIG. , And a description thereof will be omitted below. As shown in FIGS. 15 and 16, the light deflection scanning device according to the present embodiment has a stator core cylindrical portion inner diameter d.
The k ₁ a ring-shaped bush 22 is internally provided. [0056] According to this configuration, since the stator core cylindrical inner diameter dk ₁ disposed therein a ring-shaped bush 22, even if vibration at the natural frequency of the stator core 15 is generated by the rotating magnetic force, the stator core cylindrical portion the material of the inner diameter dk annular bush 22 that is provided inside _one can be variously selected, it is possible to change the weight of the stator core 15, since the natural frequency of the stator core 15 can be varied to an optimum frequency Accordingly, the degree of freedom in designing the stator core 15 is increased. In addition, since the material of the stator core 15 is generally iron, if the material of the internal bush 22 is made of a metal material such as, for example, brass, aluminum, or lead, the rigidity can be increased. It is further preferable that the natural frequency of the stator core 15 can be changed because the weight of the stator core 15 can be changed. Needless to say, the effect can be further enhanced by selecting a material having better mechanical properties (particularly, a lateral elasticity coefficient) than the material of the stator core 15. FIG. 18 shows the analysis result of this simulation. Accordingly, not only the vibration of the stator core 15 can be suppressed, but also the peak value of the natural frequency can be varied, so that the degree of freedom in design is increased.
The natural frequency of the stator core 15 is set in the audible band (20 Hz to
(Frequency band of 18 kHz). If the ring-shaped bush 21 is in contact with the motor circuit board 14 other than the stator core 15, it can be considered that there is a constraint condition (the inner diameter is fixed). This can be easily explained by considering the vibration as a wave. That is,
It has been found that when a certain wave is generated in the stator core 15, when a certain point of the stator core 15 is constrained, the speed of the wave increases and the frequency increases with the constrained point as a node. This is effective when it is desired to greatly change the vibration mode at the natural frequency of the stator core 15. Accordingly, the ring-shaped bush 22 provided inside the inner diameter dk ₁ of the stator core cylindrical portion can greatly change the vibration mode by being in contact with the motor circuit board 14 other than the stator core 15. The natural frequency of the audible band (20Hz to 18kHz
Frequency band), and the noise can be greatly reduced. In the present embodiment, the ring-shaped bush 22 is in contact with the motor circuit board 14, but may be a bearing and a housing. Thus, also in the present embodiment, it is possible to realize an optical deflection scanning device capable of surely reducing the vibration, as in the first embodiment. As apparent from the above description, according to the present invention, the light source, the deflector motor for deflecting and scanning the light beam generated from the light source, and the light beam from the deflector motor are substantially In an optical deflection scanning device including a scanning optical lens for scanning a photosensitive member at a constant speed, a rotor outer diameter Dr, a stator core cylindrical portion outer diameter dk _2, and an inner diameter d of the deflector motor are provided.
Since k ₁ is set so as to satisfy Dr ≦ 40 mm dk ₁ ≦ 0.60 × dk ₂ , it is possible to obtain an effect that noise due to electromagnetic noise during motor rotation can be significantly reduced.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a sectional view of a light deflection scanning device according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view of a rotor section of the optical deflection scanning device according to the first embodiment of the present invention. FIG. 3 is a diagram showing a relationship between a rotor outer diameter and a starting time. FIG. 4 is a partially enlarged cross-sectional view of the light deflection scanning device according to the first embodiment of the present invention. FIG. 5 is a cross-sectional view of a stator core illustrating a relationship between a rotor outer diameter and a torsional stress. FIG. 6 is a diagram illustrating a relationship between a rotor outer diameter and a torsional stress. FIG. 7 is a sectional view of a stator core. FIG. 8 is a sectional view of a cylindrical portion of a stator core. FIG. 9 is a diagram showing a relationship between a stator core inner / outer diameter ratio and torsional rigidity. FIG. 10 is a sectional view of a stator core cylindrical portion. FIG. 11 is a diagram showing a cross-sectional view of a stator core used for a simulation analysis and a simulation analysis result. FIG. 12 is a diagram showing a cross-sectional view of a stator core used for a simulation analysis and a simulation analysis result. FIG. 13 is a diagram showing a cross-sectional view of a stator core used for a simulation analysis and a simulation analysis result. FIG. 14 is a diagram showing a relationship between a stator core inner / outer diameter ratio and a stator core natural frequency. FIG. 15 is a sectional view of an optical deflection scanning device according to Embodiment 2 of the present invention. FIG. 16 is a sectional view of a stator core of the optical deflection scanning device according to the second embodiment of the present invention. FIG. 17 is a sectional view of a cylindrical portion of a stator core of the optical deflection scanning device according to the second embodiment of the present invention. FIG. 18 is a diagram showing a simulation result. FIG. 19 is a cross-sectional view of a conventional light deflection scanning device. [Description of Signs] 1 Deflector motor 2 Rotating polygon mirror 3 Rotating shaft 4 Sleeve 6 Lubricating fluid 8 Rotor yoke 9 Rotor magnet 15 Stator core 15a Coil 15b Terminal pin 16 Slot 17 Teeth 20 Scanning optical lens 22 Bush

Claims (1)

[The claims] A light source and a light beam generated by the light source are deflected.
Scanning deflector motor and light from the deflector motor
A scanning optical lens that scans a bundle almost uniformly on a photoconductor.
In an optical deflection scanning device comprising: Rotor outer diameter Dr and stator core circle of the deflector motor
Tube outer diameter dk_Two And inner diameter dk₁ To Dr ≦ 40mm dk₁≦ 0.60 × dk_Two Optical deflection scanning device characterized in that it is set to satisfy
Place. 2. The stator core according to claim 1, wherein
Core cylindrical part outer diameter dk _Two Circumscribed circle or inscribed circle with inner diameter dk
2. The light according to claim 1, wherein the light is a polygon.
Deflection scanning device. 3. A ring is formed on the inner diameter of the cylindrical portion of the stator core.
The bush according to claim 1, wherein the bush is internally provided.
Light deflection scanning device. 4. A bush other than a stator core
4. An optical polarization device according to claim 3, wherein said optical polarization device is brought into contact with a product.
Directional scanning device.