JP2010239836A - Motor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a motor which suppresses noises during motor driving without increasing an urging force to a slide bearing. <P>SOLUTION: The motor has a rotor 10 rotating by magnetic connection to a stator 20, the slide bearing 40 supporting the shaft end of the rotor 10, an urging member 60 urging the slide bearing 40, and a cap 50 having a cylindrical portion 52 and a flange 54 by which the slide bearing 40 are held movably in an axial direction. A recess 16, in which the cylindrical part 52 of the cap 50 is housed, is formed in the rotor 10. A taper 161 expanding toward an opening side is formed in the recess 16. A taper-shaped thick section 56 is formed so as to face the taper 161 in the cap 50. The line C of intersection of a virtual surface P1 formed by extending one edge 141 of the rotor 10 in the plane direction and a virtual surface P2 formed by extending an outer periphery E of an inner bottom surface 162 in the recess 16 in the axial direction lies inside the outer peripheral surface of the heavy-thick section 56. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a motor, and more particularly to a motor that includes a slide bearing that supports a shaft end of a rotor and is movable in the axial direction of the rotor, and a cap that holds the slide bearing.

  A small motor is used for driving a lens of a digital camera, a digital video camera or the like. In recent years, as the demand for miniaturization of a product in which a motor is mounted, such as a digital camera and a digital video camera, the demand for miniaturization of the motor itself is further increased.

  As an example of such a motor, one described in Patent Document 1 below is known. In the motor described in Patent Document 1, the shaft end on the counter-output side of the rotor that is rotated by a magnetic field generated from the stator is supported by a resin-made slide bearing that is slidable in the axial direction of the rotor. . The slide bearing is held by a cylindrical portion of a resin-made bearing holder (cap) while being urged toward the rotor by an urging member fixed to the non-output side end surface of the motor.

JP 2007-252121 A

  However, when a motor provided with a slide bearing as described in Patent Document 1 is made more compact, there is a problem that noise such as rattling occurs during motor driving.

  Such noise could be reduced by increasing the biasing force of the slide bearing by the biasing means. However, as the biasing force is increased, the contact force between the slide bearing and the rotor shaft end, and the contact point between the slide bearing and the biasing member increases. There was a problem that the amount of wear at the contact portion increased and the durability decreased. Further, there is a problem that the output torque decreases as the contact force increases. Furthermore, since the biasing means has to be enlarged, there is a problem in that the effect of downsizing the motor is reduced and the manufacturing cost is increased.

  In view of the above problems, the problem to be solved by the present invention is that when a motor using a slide bearing that supports the shaft end of the rotor is downsized, the motor drive is performed without increasing the biasing force against the slide bearing. An object of the present invention is to provide a motor that suppresses noise inside.

  In order to solve the above problems, the present inventor has made various studies. As a result, when the thickness of the cylindrical portion that holds the slide bearing is reduced in accordance with the miniaturization of the motor, the cylindricity of the cylindrical portion is reduced (particularly on the rotor side) The decrease in the degree is remarkable.) The knowledge that the noise is generated is obtained. In other words, when the cap, which is a resin molded product, becomes smaller, it melts in the cavity of the mold that forms the tip side (inner bottom surface side of the recess) of the cylindrical part away from the gate during injection molding. Since the flow of the resin is deteriorated, the molding accuracy is lowered, and in particular, the cylindricity on the tip side of the cylindrical portion is lowered. Further, when the molten resin flow is deteriorated, the resin is solidified without being partially filled, and the molding accuracy is lowered and the cylindricity is lowered. As a result, when the clearance between the outer peripheral surface of the slide bearing and the inner peripheral surface of the cylindrical portion becomes large, noise is generated due to rattling of the slide bearing inside the cylindrical portion. When the clearance with the inner circumferential surface of the slide bearing becomes small, the movement of the slide bearing held in the cylindrical portion in the axial direction deteriorates, and a gap is created between the slide bearing and the shaft end of the rotor, causing the rotor to rattle. As a result, we obtained the knowledge that noise was generated.

  The present invention has been made based on such knowledge. A rotor that is rotated magnetically connected to a stator, a slide bearing that supports a shaft end of a rotating shaft of the rotor, and the slide bearing are described above. A biasing member that biases in the axial direction of the rotor, a cylindrical portion in which the slide bearing is held movably in the axial direction, and a flange fixed to the stator that extends outward from one end surface of the cylindrical portion A concave portion that accommodates the cylindrical portion of the cap is formed at one end of the rotor, and the diameter of the inner peripheral side surface of the concave portion increases from the inner bottom surface toward the opening side. The cap is provided with a tapered thick portion straddling the cylindrical portion and the flange so as to face the tapered portion, and from the outer peripheral surface of the thick portion. Inside, said Set so that a line of intersection between an imaginary surface extending from the one end of the sensor in a direction perpendicular to the axial direction and a imaginary surface extending from the outer peripheral edge of the inner bottom surface of the recess in the axial direction is positioned. It is the gist of what is being done.

  According to the present invention having such a configuration, the taper is enlarged so that the intersecting line of the two virtual surfaces is located on the inner side so as to straddle the cylindrical portion and the collar portion of the cap (at the base portion of the cylindrical portion). By providing a thick walled portion, the flow of the molten resin becomes smooth and the resin can be easily filled up to the end portion of the cavity of the mold. For this reason, the cylindricity (dimensional accuracy) of the thin-walled cylindrical portion, especially Conventionally, the cylindricity on the tip end side (the inner bottom surface side of the concave portion) of the cylindrical portion, where the decrease in cylindricity has been remarkable, is improved. Therefore, even when the motor is downsized, noise due to slide bearing rattling and rotor rattling can be reduced without increasing the biasing force against the slide bearing.

  In this case, the slide bearing only needs to be disposed so that the end surface on the inner bottom surface side of the concave portion is positioned in the vicinity of the front end surface of the cylindrical portion.

  As described above, due to the thick portion provided in the cylindrical portion of the cap, the cylindricity of the cylindrical portion is increased over the whole, including the tip portion where the decrease in cylindricity has been significant in the past. Therefore, the slide bearing is disposed so that the end surface on the inner bottom surface side of the concave portion of the slide bearing is located in the vicinity of the tip surface of the cylindrical portion, that is, by making full use of the length of the cylindrical portion in the axial direction of the rotor. By doing so, it is possible to reduce the length of the motor in the axial direction while securing a state in which the slide bearing held by the cylindrical portion slides smoothly.

  The concave portion is formed along a cylindrical inner wall formed along the imaginary surface formed by extending an outer peripheral edge of the inner bottom surface in the axial direction, and the opening edge of the cylindrical inner wall. What is necessary is just to be comprised from the taper part.

  In this way, if the tapered portion is formed along the opening edge of the concave portion, the strength reduction of the thinned portion can be suppressed by forming the concave portion of the rotor (magnet). It is possible to prevent the occurrence of problems such as breakage of the rotor during work.

  Moreover, the slide bearing should just be arrange | positioned so that the virtual surface formed by extending the opening end surface of the said recessed part may cross | intersect the said thick part.

  Since the slide bearing held by the cylindrical portion is urged by the urging member from the end surface on the opening side of the recess, the slide bearing may be inclined in the cylindrical portion with the end surface on the opening side of the recess as a base point. In such a case, a large force is applied to the portion serving as the base point of the tilt of the bearing. On the other hand, according to the said structure, since the big force can be received in the thickness part vicinity which has high rigidity, malfunctions, such as a cap deform | transforming, are prevented.

  The slide bearing may be disposed so that the end surface on the opening side of the recess does not protrude outward from a virtual surface formed by extending from the one end of the rotor in a direction orthogonal to the axial direction. .

  Thus, if the slide bearing is disposed so as not to protrude from the end face of the rotor, the length of the motor in the axial direction can be reduced.

  The urging member has a urging portion that abuts on the slide bearing and urges in the axial direction of the rotor, and the urging portion is disposed inside the flange portion in a direction perpendicular to the axial direction. It only has to be installed.

  Thus, if the urging portion (for example, a leaf spring) that urges the slide bearing is provided so as to enter the inside of the flange portion, the length in the axial direction of the motor can be reduced. Further, when the urging portion is disposed so as to enter the inside of the collar portion, the slide bearing is positioned on the tip side of the cap accordingly. Therefore, it is significant to improve the cylindricity of the cylindrical portion by providing the thick portion on the cap.

  According to the present invention, by providing the tapered thick portion that is enlarged so that the intersection line of the two virtual surfaces is located on the inner side so as to straddle the cylindrical portion and the collar portion of the cap, The molding accuracy is improved, and in particular, the cylindricity of the cylindrical portion on the rotor side, in which the decrease in cylindricity has been remarkable in the past, is improved. Therefore, even when the motor is downsized, noise due to slide bearing rattling and rotor rattling can be reduced without increasing the biasing force against the slide bearing.

1 is an external perspective view of a motor according to an embodiment of the present invention. It is a top view of the motor shown in FIG. It is sectional drawing of the motor cut | disconnected by the AA line in FIG. It is a cross-sectional perspective view of the motor (stator) cut | disconnected by the AA line in FIG. FIG. 4 is an enlarged view of a portion B in FIG. 3, illustrating a relationship between a tapered portion formed in a concave portion and a thick portion formed in a cap. It is the figure which showed for reference the structure in which the taper part is formed from the bottom face of the recessed part. It is a figure for demonstrating the modification (modified example of the shape of a taper part and a thick part) of embodiment shown in FIGS.

  Hereinafter, an embodiment of a motor according to the present invention will be described in detail with reference to the drawings. 1 is an external perspective view of a motor 1 according to the present embodiment, FIG. 2 is a top view of the motor 1, FIG. 3 is a cross-sectional view of the motor 1 cut along line AA in FIG. 2, and FIG. It is a cross-sectional perspective view of the motor 1 (stator 20) cut | disconnected by the -A line | wire. The motor 1 according to this embodiment includes a rotor 10, a slide bearing 40 that supports the non-output-side shaft end 122 of the rotor 10, a cap 50 having a cylindrical portion 52 that holds the slide bearing 40, and a slide bearing 40. And a biasing member 60 that biases the power toward the output side (the rotor 10 side).

  The rotor 10 includes a rotating shaft 12 and a magnet (permanent magnet) 14. Specifically, the magnet 14 is fixed to the outer peripheral surface of the rotating shaft 12 on the opposite output side. A lead screw portion 12 a is formed at a portion of the rotating shaft 12 protruding from the stator 20. The magnet 14 is formed by alternately magnetizing N and S poles in the circumferential direction. Further, the magnet 14 is formed with a concave portion 16 that is recessed to a predetermined size in order to dispose a cylindrical portion 52 of the cap 50 described later.

  Such a rotor 10 is rotated by a magnetic field generated from a stator 20 disposed outside the magnet 14. As shown in the figure, the stator 20 is composed of two stator sets 22a and 22b that are arranged so as to overlap in the axial direction. The two stator sets 22a and 22b are respectively sandwiched between the outer stator cores 24a and 24b, the drive coils 26a and 26b wound around the coil bobbins 28a and 28b, and the coil bobbins 28a and 28b between the outer stator cores 24a and 24b. It has stator cores 25a and 25b.

  Each of the outer stator cores 24a, 24b and the inner stator cores 25a, 25b is formed with a rotor insertion hole 29 for inserting the rotor 10 (magnet 14) formed to be larger than the outer diameter of the magnet 14 at the center portion thereof. . A plurality of pole teeth 251 are formed so as to face the outer periphery of the magnet 14. The pole teeth 251 are erected in the axial direction from the peripheral edge of the rotor insertion hole 29 formed in each of the outer stator cores 24a and 24b and the inner stator cores 25a and 25b, and are formed in an annular shape at substantially equal intervals. ing. The outer stator cores 24a and 24b and the inner stator cores 25a and 25b having such a shape are arranged so that the drive coils 26a and 26b wound around the coil bobbins 28a and 28b are sandwiched between the pole teeth 251 alternately. In combination, the pole teeth 251 are arranged so as to face the outer periphery of the magnet 14 and the inner periphery of the drive coils 26a and 26b.

  Further, the outer peripheral edges of the outer stator cores 24a and 24b are bent in the axial direction so as to cover the outer periphery of the drive coils 26a and 26b, and the portion covering the outer periphery of the drive coils 26a and 26b functions as the motor case 90. is doing. The motor case 90 includes a first case portion 90a formed on the outer stator core 24a and covering the outer periphery of the drive coil 26a, and a second case portion 90b formed on the outer stator core 24b and covering the outer periphery of the drive coil 26b. It is composed of

  In the rotor 20 rotated by the magnetic field generated from the stator 20, the output-side shaft end 121 of the rotating shaft 12 rotates to the fixed bearing 30 and the non-output-side shaft end 122 rotates to the slide bearing 40 as shown in the figure. Supported as possible.

  The fixed bearing 30 is fixed to the frame 70. The frame 70 is a metal member formed in a substantially U-shape, and includes an output-side support portion 74 erected at a right angle from a main body portion 72 positioned parallel to the rotation shaft 12, and a stator fixing portion 76. Have. In the frame 70, the stator fixing portion 76 is fixed to the output side end surface of the stator 20 by welding or the like. The fixed bearing 30 includes a main body portion 32 and a hook-like engagement portion 34. The main body portion 32 is press-fitted into a bearing holding hole 741 formed in the output side support portion 74, and the engagement portion 34 is in the bearing holding hole 741. It is attached to the output side support part 74 by engaging with the peripheral edge.

  On the other hand, the slide bearing 40 that supports the non-output side shaft end 122 of the rotary shaft is a substantially cylindrical resin member, and is held in the cylindrical portion 52 of the cap 50 so as to be movable in the axial direction of the rotor 10. Yes. The slide bearing 40 is formed with a support recess 42 that is recessed from the output side end face. The support recess 42 is a recess whose bottom surface is formed in a conical shape, and the rotary shaft 12 is rotatably supported with the counter-output side shaft end 122 in contact with the bottom surface of the support recess 42. Although not particularly illustrated, a protrusion for preventing rotation in the circumferential direction may be formed on the outer periphery of the slide bearing 40.

  The cap 50 that holds the slide bearing 40 has a cylindrical cylindrical portion 52 that holds the slide bearing 40 and a flange portion 54 that extends outward from the end face on the non-output side of the cylindrical portion 52 by injection molding. It is a molded resin member. The cap 50 is attached so that the flange portion 54 is sandwiched between the stator 20 and the urging member 60 fixed to the opposite output side end surface of the stator 20. The cylindrical portion 52 of the cap 50 attached in this way is accommodated in the recess 16 formed in the magnet 14 as shown in the figure.

  The urging member 60 is fixed to the non-output side end surface of the stator 20 by welding or the like. A leaf spring 62 (biasing portion) is formed at the center of the urging member 60. As shown in FIG. 3, the leaf spring 62 is disposed on the inner side (radially inner side) of the flange portion 54 in the direction orthogonal to the axial direction of the rotor 10. By doing so, the length of the motor 1 in the axial direction can be reduced.

  Further, the leaf spring 62 has a hole formed at the center of the tip portion that contacts the bottom surface 44 of the slide bearing 40. On the other hand, a projection 441 which is a gate mark at the time of injection molding is formed at the center of the bottom surface 44 of the slide bearing 40, and the leaf spring 62 is inserted into the hole formed at the center thereof. Thus, the slide bearing 40 is urged to the output side. Thus, by making the contact surface of the slide bearing 40 and the leaf spring 62 into a substantially annular shape, the pressurizing direction with respect to the slide bearing 40 is prevented from being greatly inclined from the axial direction.

  Hereinafter, the configuration of the recess 16 formed in the magnet 14 of the motor 1 and the cap 50 will be described in detail with reference to the drawings. FIG. 5 is an enlarged view of a portion B in FIG.

  As described above, the cylindrical portion 52 of the cap 50 is disposed in the recess 16 formed in the magnet 14. Specifically, the magnet 14 and the cylindrical portion 52 are disposed so that the central axes thereof are coaxially positioned, and a predetermined gap is provided between the inner peripheral side surface 163 of the concave portion 16 and the outer peripheral surface 521 of the cylindrical portion 52. A clearance of the size of is provided.

  A tapered portion 161 is formed at the opening edge of the recess 16 such that the diameter increases in the direction of opening from the inner bottom surface 162 side. That is, the concave portion 16 includes a cylindrical inner peripheral side surface 163 (cylindrical inner wall) formed by extending the outer peripheral edge (the portion indicated by E in FIG. 5) of the inner bottom surface 162 in the axial direction (opposite output side direction), And a tapered portion 161. On the other hand, the cap 50 is formed with a tapered thick portion 56 straddling the cylindrical portion 52 and the flange portion 54 (on the root portion of the cylindrical portion 52) so as to face the tapered portion 161.

  As shown in FIG. 5, the thick portion 56 includes a virtual surface Q1 obtained by extending the output side end surface 541 of the flange portion 54, and a virtual surface Q2 obtained by extending the outer peripheral surface 521 of the cylindrical portion 52 to the non-output side. The region surrounded by the tapered outer peripheral surface 561 is pointed out.

  The thick portion 56 has the following size. As shown in FIG. 5, the surface obtained by extending the opposite end surface 141 of the magnet 14 to the virtual surface P <b> 1 and the outer peripheral edge (the portion indicated by E in FIG. 5) of the inner bottom surface 162 of the recess 16 are axially directed (reverse output). A surface extending in the lateral direction (in this embodiment, also a surface extending the inner peripheral side surface 163 (cylindrical inner wall) of the recess 16) is defined as a virtual surface P2. Since the virtual surface P1 is a plane and the virtual surface P2 is a cylindrical surface, the intersection line C where the virtual surface P1 and the virtual surface P2 intersect is a circle. The thick portion 56 is formed in such a size that the intersecting line C is located inside the outer peripheral surface 561.

  The “size of the thick portion 56 such that the intersection line C is located on the inner side” means not only the shape in which the intersection line C is actually located on the inner side of the thick portion 56 but also within a dimensional tolerance range. It is assumed that the intersection line C includes a shape that is located inside the thick portion 56. For example, when the dimension of the magnet 14 in the axial direction swings to the plus side within the dimensional tolerance range, the position of the intersection line C is closer to the thick portion 56 side and includes a shape that enters the thick portion 56.

  Thus, after forming the taper part 161 along the opening edge of the recessed part 16, the taper-shaped thick part 56 is formed so that it may straddle the cylindrical part 52 and the collar part 54 of the cap 50, and the magnitude | size The dimensional accuracy (cylindricity) of the cylindrical portion 52 can be increased by increasing the length so that the intersection line C between the virtual surface P1 and the virtual surface P2 is located inside. That is, conventionally, as the size of the motor 1 is reduced, the size of the cap 50 is reduced, so that it is difficult to obtain dimensional accuracy. By providing such a thick portion 56, the flow of the molten resin is smoothed and melted. The cylindricity of the cylindrical portion 52 is greatly improved because the resin is easily filled up to the end portion of the cavity of the mold.

  In the present embodiment, the gate position of the mold for molding the cap 50 is provided on the flange portion 54 side. This is due to the following reason. 1) Since the inner peripheral surface of the cylindrical portion 52 is a surface on which the slide bearing 40 slides, it cannot be provided. 2) On the outer peripheral surface of the cylindrical portion 52, if the protrusion of the gate trace remains, the concave portion 16 of the opposing magnet 14 must be enlarged, which becomes a factor that hinders the miniaturization of the motor 1. 3) When the gate position is set in the cylindrical portion 52, a force generated at the time of gate cutting is applied to the cylindrical portion 52, which may affect the dimensional accuracy of the cylindrical portion 52.

  For these reasons, the gate position must be provided on the flange 54 side. With such a configuration, the dimensional accuracy on the distal end side of the cylindrical portion 52 farthest from the collar portion 54 is inevitably difficult to ensure, so the effect of providing the thick portion 56 is great.

  Thus, by providing the thick portion 56 in the cap 50, it is possible to suppress a decrease in the cylindricity of the cylindrical portion 52 when the motor is downsized. Therefore, the outer peripheral surface of the slide bearing 40 and the cylindrical portion 52 Variations in clearance between the inner peripheral surface and the inner peripheral surface can be reduced. Therefore, the clearance between the outer peripheral surface of the slide bearing 40 and the inner peripheral surface of the cylindrical portion 52 is increased, and noise generated when the slide bearing 40 rattles inside the cylindrical portion 52, or the outer peripheral surface of the slide bearing 40 and the cylindrical portion. 52, the clearance between the inner peripheral surface of the rotor 52 is reduced, the movement of the slide bearing 40 held by the cylindrical portion 52 in the axial direction is deteriorated, and a gap is formed between the slide bearing 40 and the non-output side shaft end 122 of the rotor 10. Is generated, and the noise generated by the rattling of the rotor 10 due to the gap can be prevented.

  Further, in the present embodiment, the slide bearing 40 has an end surface 401 on the output side (the inner bottom surface 162 side of the recess 16) positioned so as to be substantially in the vicinity of the end surface 522 (tip surface) on the output side of the cylindrical portion 52. It is arranged. With this configuration, the slide bearing 40 can be efficiently disposed in the space in the cylindrical portion 52, so that the length of the motor 1 in the axial direction can be reduced.

  This point will be described in detail. Conventionally, the cylindrical portion 52 on the side of the flange portion 54 side is used because the cylindricity of the tip portion side (the inner bottom surface 162 side of the concave portion 16) of the cylindrical portion 52 has been lowered. When the slide bearing 40 is only provided and a certain length of the slide bearing 40 is secured, the space on the tip side in the cylindrical portion 52 is wasted.

  In the present embodiment, since the thick portion 56 provided in the cap 50 can ensure high cylindricity over the entire cylindrical portion 52, the length of the cylindrical portion 52 in the axial direction is fully utilized. Thus, the slide bearing 40 can be disposed. Accordingly, since the length of the cylindrical portion 52 in the axial direction can be made substantially the same as the length of the slide bearing 40, the space in the cylindrical portion 52 can be used efficiently, and the length of the motor 1 in the axial direction can be increased. The thickness can be reduced.

  In the present embodiment, a tapered portion 161 is formed along the opening edge of the recess 16 formed in the magnet 14. The reason why the tapered portion 161 is formed along the opening edge of the concave portion 16 is to prevent the strength of the magnet 14 from being greatly reduced by the tapered portion 161. For example, as shown in FIG. 6, when the tapered portion 161 is formed from the inner bottom surface 162 of the concave portion 16, compared to the case where the tapered portion 161 is formed along the opening edge of the concave portion 16, The thickness of the magnet 14 (thickness of the side wall portion 142) becomes small. In such a state, the magnet 14 may be damaged during the assembly work of the motor 1 or the like. That is, if the tapered portion 161 is formed along the opening edge of the recess 16 as in the present embodiment, the thickness of the side wall portion 142 of the magnet 14 can be suppressed as much as possible, and the assembly operation can be performed. In addition, it is possible to prevent the occurrence of problems such as the magnet 14 being damaged.

  Further, as can be seen from FIG. 5, the slide bearing 40 is disposed at a position where a virtual surface P <b> 3 formed by extending the non-output side end surface 402 intersects the thick portion 56. This is because, when the pressurizing direction by the leaf spring 62 is tilted from the axial direction due to vibration or the like, the slide bearing 40 is tilted in the cylindrical portion 52, and the portion that becomes the base point of the tilt (the portion indicated by B in FIG. 5) This is because a great force is applied. In the present embodiment, by arranging the slide bearing 40 at a position where the virtual surface P3 intersects the thick portion 56, it is configured to receive this large force in the vicinity of the thick portion 56 having high rigidity, The deformation of the cap 50 is prevented.

  Further, as can be seen from FIG. 5, the slide bearing 40 is disposed such that the non-output side end surface 402 (virtual surface P3) is positioned on the output side from the counter-output side end surface 141 (virtual surface P1) of the rotor 10. Has been. Thus, if the slide bearing 40 is disposed so as not to protrude from the non-output-side end surface 141 of the rotor 10, the length of the motor 1 in the axial direction can be reduced.

  The configuration of the tapered portion 161 and the thick portion 56 has been described in detail above, but various modifications can be considered as the configuration of the tapered portion 161 and the thick portion 56. For example, as shown in FIG. 7, the taper-shaped gradient of the taper portion 161 formed in the concave portion 16 and the taper-shaped gradient of the thick portion 56 may be formed to be substantially the same. As described above, if the slopes of the tapered shapes of the opposed thick portion 56 and the tapered portion 161 are substantially the same, that is, the two are positioned in parallel, the limited arrangement space in the motor 1 is effectively utilized. Therefore, the motor 1 can be made smaller.

  Although the embodiments of the present invention have been described in detail above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the gist of the present invention.

DESCRIPTION OF SYMBOLS 1 Motor 10 Rotor 12 Rotating shaft 14 Magnet 141 (Output side end face 16 of magnet) Recessed part 161 Tapered part 162 Inner bottom face (of recessed part) 20 Stator 40 Slide bearing 50 Cap 52 Cylindrical part 54 Gutter part 56 Thick part

Claims (6)

  A rotor that is rotated in a magnetically coupled manner with a stator, a slide bearing that supports a shaft end of a rotating shaft of the rotor, a biasing member that biases the slide bearing in an axial direction of the rotor, and the slide bearing And a cap having a cylindrical portion that is movably held in the axial direction and a flange portion that is fixed to the stator and extends outward from one end surface of the cylindrical portion. A concave portion for accommodating the cylindrical portion of the cap is formed, and a tapered portion whose diameter increases from the inner bottom surface side toward the opening side is formed on the inner peripheral side surface of the concave portion, and the tapered portion is formed on the cap. A tapered thick portion extending between the cylindrical portion and the flange portion is provided so as to face the portion, and a direction perpendicular to the axial direction from the one end of the rotor is provided inside the outer peripheral surface of the thick portion. To Motor, wherein the line of intersection between the imaginary surface a peripheral edge of the inner bottom surface of a virtual plane the recess being extended in the axial direction and can be is configured to be positioned.   2. The motor according to claim 1, wherein the slide bearing is disposed such that an end surface on an inner bottom surface side of the concave portion is positioned substantially in the vicinity of a front end surface of the cylindrical portion.   The concave portion includes a cylindrical inner wall formed along the virtual surface formed by extending an outer peripheral edge of the inner bottom surface in the axial direction, and the tapered portion formed along an opening edge of the cylindrical inner wall. The motor according to claim 1, wherein the motor is configured as follows.   The said slide bearing is arrange | positioned so that the virtual surface formed by extending the end surface of the opening side of the said recessed part may cross | intersect the said thick part. motor.   The slide bearing is arranged such that an end surface on the opening side of the concave portion does not protrude outward from a virtual surface formed by extending from the one end of the rotor in a direction orthogonal to the axial direction. The motor according to any one of claims 1 to 4.   The urging member has a urging portion that abuts on the slide bearing and urges in the axial direction of the rotor, and the urging portion is disposed inside the flange portion in a direction perpendicular to the axial direction. The motor according to claim 1, wherein the motor is provided.

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