WO2013046526A1 - 電動機 - Google Patents
電動機 Download PDFInfo
- Publication number
- WO2013046526A1 WO2013046526A1 PCT/JP2012/005216 JP2012005216W WO2013046526A1 WO 2013046526 A1 WO2013046526 A1 WO 2013046526A1 JP 2012005216 W JP2012005216 W JP 2012005216W WO 2013046526 A1 WO2013046526 A1 WO 2013046526A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bearing
- washer
- electric motor
- claw
- ball bearing
- Prior art date
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Classifications
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
- F16C25/06—Ball or roller bearings
- F16C25/08—Ball or roller bearings self-adjusting
- F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K5/00—Casings; Enclosures; Supports
- H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
- H02K5/16—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields
- H02K5/173—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings
- H02K5/1732—Means for supporting bearings, e.g. insulating supports or means for fitting bearings in the bearing-shields using bearings with rolling contact, e.g. ball bearings radially supporting the rotary shaft at both ends of the rotor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2380/00—Electrical apparatus
- F16C2380/26—Dynamo-electric machines or combinations therewith, e.g. electro-motors and generators
-
- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K2205/00—Specific aspects not provided for in the other groups of this subclass relating to casings, enclosures, supports
- H02K2205/03—Machines characterised by thrust bearings
Definitions
- the present invention relates to an electric motor having a ball bearing mainly used for an electric blower such as a household vacuum cleaner or an industrial blower.
- the configuration in which the outer ring of the conventional ball bearing and the bearing housing are fixed by fitting or using an adhesive has the following inconvenience due to heat generation during operation of the motor. That is, the dimension between the outer rings of two ball bearings (generally called the dimension between the outer rings of the bearing) and the dimension between the inner rings of the two ball bearings (generally called the dimension between the inner rings of the bearing) ), A dimensional difference occurs due to a difference in thermal expansion coefficient.
- the outer ring of the bearing and the bearing housing are fixed with an adhesive or the like, the dimensional difference greatly affects the ball bearing, causing play inside the ball bearing, causing abnormal vibration and abnormal noise, Had the problem of destruction.
- the dimensional difference generated between the dimension between the bearing housings and the dimension between the ball bearings is remarkable when a bracket made of synthetic resin is used.
- Patent Document 1 a ring portion that is press-fitted and fixed to the outer ring of the ball bearing, a stopper that a metal stopper member that includes a flange portion, and a fitting portion that is provided on the resin frame member, It is configured to prevent idling.
- a new part called a stopper member is required, and there is a problem that the cost increases.
- a portion where the outer ring of the ball bearing can be held by the bearing mounting portion of the resin frame becomes narrow. For this reason, the subject that it became difficult to ensure the precision of bearing outer ring holding
- An electric motor of the present invention includes a rotor having a rotating shaft, a pair of ball bearings supporting the rotating shaft, and two brackets having a bearing housing for holding the ball bearing.
- One ball bearing and the bearing housing A washer is provided between the end walls of the. The washer has a plurality of claws.
- the claw of the washer acts on the ball bearing and the bearing housing so as to fit in a wedge shape. For this reason, idling of the ball bearing such as a creep phenomenon can be prevented. Furthermore, even if a dimensional difference occurs between the bearing outer ring dimension and the bearing inner ring dimension as described above, the washer claw is deformed to act to absorb this dimensional difference. Generation of internal play can be prevented. For this reason, according to the electric motor of the present invention, the idling phenomenon of the ball bearing can be prevented while securing the bearing preload, and the electric motor with low vibration / low noise and high reliability can be provided.
- FIG. 1 is a side view of a partial cross section of an electric motor according to Embodiment 1 of the present invention.
- FIG. 2A is an external view of a washer according to Embodiment 1 of the present invention.
- FIG. 2B is an external view of another configuration example of the washer according to Embodiment 1 of the present invention.
- FIG. 3 is an enlarged partial cross-sectional view of a location of the bearing housing in the first embodiment of the present invention.
- FIG. 4A is a diagram showing a bearing outer ring dimension D1 and a bearing inner ring dimension D2.
- FIG. 4B is a diagram illustrating a state in which the ball bearing according to Embodiment 1 of the present invention slides in the axial length direction with a dimensional difference.
- FIG. 1 is a side view of a partial cross section of an electric motor according to Embodiment 1 of the present invention.
- FIG. 2A is an external view of a washer according to Embodiment 1 of the present invention.
- FIG. 5 is an enlarged partial cross-sectional view of a location of the bearing housing in the second embodiment of the present invention.
- FIG. 6A is an external view of a washer according to Embodiment 2 of the present invention.
- FIG. 6B is an external view of another configuration example of the washer according to Embodiment 2 of the present invention.
- FIG. 7A is a front view of a bearing housing according to Embodiment 2 of the present invention.
- FIG. 7B is a cross-sectional view of the bearing housing according to Embodiment 2 of the present invention.
- FIG. 1 is a side view of a partial cross section of an electric motor 10 according to Embodiment 1 of the present invention.
- an electric motor that includes a commutator electric motor and a fan for blowing as the electric motor 10 and is used as an electric fan such as a vacuum cleaner will be described.
- the electric motor 10 includes two brackets, a first bracket 12 made of a steel plate having a substantially cup shape with one opening and a second bracket 13 made of synthetic resin disposed on the opening side of the bracket 12. ing. And the commutator motor 11 is provided inside these two brackets. Further, the electric motor 10 has a fan 18 attached to the tip of the rotating shaft 43 protruding from the bracket 13, and an air guide 19 attached so as to partition the fan 18 and the commutator electric motor 11.
- the commutator motor 11 includes a stator 30 that is a field, a rotor 40 that is an armature, ball bearings 14 and 15 that rotatably support the rotor 40, and a brush 35. It is comprised including.
- the stator 30 has a field winding 32 wound around a field core 31 made of iron or the like.
- the field core 31 is formed by, for example, laminating a plurality of electromagnetic steel plates having a predetermined shape. Further, the field core 31 has a magnetic pole portion serving as a magnetic pole inside thereof and a space portion for arranging the rotor 40. Such a stator 30 is fixed inside the bracket 12.
- the rotor 40 includes an armature core 41, an armature winding 42, a rotating shaft 43, and a commutator 45.
- An armature winding 42 is wound around the armature core 41.
- the lead wire of the armature winding 42 drawn from the armature core 41 is connected to the commutator 45.
- the armature core 41 and the commutator 45 have a cylindrical shape, and the rotary shaft 43 is coupled so as to pass through the centers of the armature core 41 and the commutator 45.
- One end side of the rotating shaft 43 that is the output shaft side is rotatably supported by the ball bearing 15, and the other end side of the rotating shaft 43 that is the non-output shaft side is rotatably supported by the ball bearing 14.
- the rotor 40 configured as described above is disposed on the inner peripheral side of the stator 30 with the armature core 41 and the magnetic pole portion formed on the field core 31 facing each other.
- a brush holder for holding the brush 35 is fixed to the bracket 13.
- the brush 35 is composed of a composition containing a solid lubricant in a carbon brush material such as artificial graphite.
- Such a brush 35 is held in the brush holder and pressed against the commutator 45 by a brush spring or the like.
- the commutator motor 11 has a pair of such brushes 35, and each of the pair of brushes 35 is in contact with the commutator 45.
- the commutator motor 11 is configured as described above.
- a fan case 17 is attached so as to cover the opened side of the bracket 12.
- the rotation shaft 43 of the rotor 40 has its output shaft side extending from the opening of the bracket 12 through the central portion of the bracket 13 into the fan case 17, and a fan for blowing air is provided at the tip of the rotation shaft 43. 18 is attached. Further, an air guide 19 is attached between the fan 18 and the opening of the bracket 12. As described above, the fan 18 and the air guide 19 are arranged in the fan case 17.
- the brackets 12 and 13 are formed with bearing housings for attaching and holding the ball bearings 14 and 15. That is, as shown in FIG. 1, in the bracket 12, the bearing housing 12a is formed in the center part of the circular end surface by the side of a non-output shaft. The bearing housing 12 a is formed on the inner side of the bracket 12 so as to be a cylindrical depression. The ball bearing 14 is inserted into the cylindrical recess. On the other hand, in the bracket 13, the bearing housing 13a is formed in the circular center part. The bearing housing 13 a is formed to be a cylindrical depression on the commutator motor 11 side of the bracket 13. The ball bearing 15 is inserted into the cylindrical recess.
- the ball bearings 14 and 15 are columnar bearings having a plurality of iron balls between a bearing inner ring and a bearing outer ring. And the rotating shaft 43 is being fixed to the inner peripheral side of each bearing inner ring
- FIG. 1 A block diagram illustrating an exemplary computing environment in accordance with the present disclosure.
- the electric motor 10 is held by the bracket 12 made of steel plate, the bracket 13 made of synthetic resin, and the bearing housings 12a and 13a of the bracket 12 and the bracket 13, respectively, and supports the rotor 40 rotatably.
- the washer 20 is inserted between the end wall 12b of the bearing housing 12a of the bracket 12 and the side surface of the ball bearing 14 included in the bearing housing 12a.
- FIG. 2A is an external view of the washer 20 according to Embodiment 1 of the present invention.
- FIG. 2B is an external view of another configuration example of the washer 20 according to Embodiment 1 of the present invention.
- the washer 20 includes an annular yoke 20b and a plurality of claws 20a that apply a bearing preload to the ball bearing 14. More specifically, a plurality of claws 20a having a predetermined width w and curved in a U shape are arranged at equal intervals in the circumferential direction on the inner peripheral side of the yoke 20b, which is a flat washer. 20 is constituted.
- FIG. 2A shows an example in which six claws 20a are provided. Each claw 20a is fixedly formed on the yoke 20b so that the two tip portions of the claw 20a protrude in one surface direction in a state where the central curved portion of the claw 20a is fixed to the yoke 20b.
- claw 20a is arrange
- the claw 20a is arranged so that a straight line connecting both tip portions of the claw 20a intersects a straight line extending in the radial direction from the center of the yoke 20b.
- the washer 20 shown in FIG. 2B has a configuration in which a plurality of claws 20a having a U-shape similar to FIG. 2A are arranged on an annular corrugated yoke 21b.
- a bearing preload is applied to the ball bearing 14 by the corrugated shape of the yoke 21b together with the U-shaped claw 20a. That is, in the present embodiment, the bearing preload is applied to the ball bearing 14 by utilizing the spring effect due to the U-shape of the claw 20a and the corrugated shape of the yoke 21b.
- each claw 20a has a plurality of U-shaped claws 20a having a predetermined width w arranged at equal intervals in the circumferential direction on the inner peripheral side of the yoke 21b which is a corrugated washer. This is the configuration. Further, each claw 20a is fixed to the yoke 21b so that both end portions of the claw 20a protrude in one surface direction in a state where the central curved portion of the claw 20a is fixed to the top of the wave formed on the yoke 21b. Is formed. Furthermore, each nail
- the washer 20 is provided with such claws 20a to prevent creep.
- FIG. 3 is an enlarged partial cross-sectional view of a portion of the bearing housing 12a according to the first embodiment of the present invention.
- the ball bearing 14 has a plurality of iron balls 14c between a bearing inner ring 14a and a bearing outer ring 14b. Furthermore, the ball bearing 14 has a bearing seal plate 14d whose outer surface is covered with rubber on the circular surface. The end of the rotary shaft 43 on the side opposite to the output shaft is fixed to the bearing inner ring 14a.
- the bearing housing 12a that is a cylindrical depression is formed.
- the bearing housing 12a has a shape having a cylindrical cylindrical portion 12c and an end wall 12b serving as a circular surface at the bottom thereof.
- the ball bearing 14 is inserted into the bearing housing 12a such that the outer peripheral surface of the bearing outer ring 14b faces the inner peripheral surface of the cylindrical portion 12c of the bearing housing 12a.
- a washer 20 is inserted between one bearing seal plate 14d of the ball bearing 14 and the end wall 12b of the bearing housing 12a.
- the washer 20 is arranged so that the claw 20a of the washer 20 faces the bearing seal plate 14d. With this configuration, the claw 20a of the washer 20 abuts on the bearing seal plate 14d with a light load, and the ball bearing 14 slides freely in the axial direction between the bearing housing 12a and the bearing outer ring 14b. It is held ready to move.
- the ball bearing 15 on the bracket 13 side is inserted and held in the bearing housing 13a of the bracket 13 as shown in FIG.
- the bearing outer ring 15b of the ball bearing 15 and the bearing housing 13a are fixed by adhesion with an adhesive or press-fitted and fixed by press-fitting.
- the surface of the bearing seal plate 14d that comes into contact with the claw 20a is a rubber type.
- a rubber type By adopting such a rubber type, the deformation of the bearing seal plate 14d due to the bearing pressurizing load is prevented, and the coefficient of friction with the washer 20 is further increased to enhance the effect of preventing the creep phenomenon.
- the washer 20 is arranged so that the claw 20a is on the bearing seal plate 14d side.
- the washer 20 is arranged so that the claw 20a is on the end wall 12b side of the bearing housing 12a. You may arrange. Even with such an arrangement, similarly, the coefficient of static friction between the claw 20a and the opposite end wall 12b is increased, and an effect of preventing a creep phenomenon can be obtained.
- the side on which the nail 20a is arranged is determined as follows.
- the coefficient of static friction between the ball bearing 14, that is, the bearing seal plate 14 d and the tip of the claw 20 a of the washer 20 is ⁇ 1, and between the end wall 12 b of the bearing housing 12 a and the tip of the claw 20 a of the washer 20.
- the coefficient of static friction is set to ⁇ 2.
- the washer 20 may be inserted so that the claws 20a face each other in the direction in which the static friction coefficients ⁇ 1 and ⁇ 2 are small.
- the configuration of the present embodiment shown in FIG. 3 shows the case of ⁇ 1 ⁇ 2, and in this case, the washer 20 is arranged so that the claw 20a is sandwiched between the yoke 21b and the bearing seal plate 14d. Yes.
- the resistance force against the idling force is reinforced by disposing the claw 20a on the bearing seal plate 14d side having a small static friction coefficient against the creep phenomenon thus generated.
- FIG. 4A is a diagram showing a bearing outer ring dimension D1 and a bearing inner ring dimension D2.
- the bearing outer ring dimension D ⁇ b> 1 is a dimension between the bearing outer ring 14 b of the ball bearing 14 and the bearing outer ring 15 b of the ball bearing 15.
- the bearing inner ring dimension D ⁇ b> 2 is a dimension between the bearing inner ring 14 a of the ball bearing 14 and the bearing inner ring 15 a of the ball bearing 15.
- the dimensional difference during heating becomes significant.
- the washer 20 is used in more detail as follows in order to suppress the occurrence of backlash inside the ball bearing due to such a dimensional difference.
- the bearing outer ring 14b of the ball bearing 14 and the bearing housing 12a of the bracket 12 can be freely slid in the axial direction. For this reason, even if a dimensional difference occurs between the bearing outer ring dimension D1 and the bearing inner ring dimension D2, it slides in the axial length direction between the bearing outer ring 14b and the bearing housing 12a. The influence on the inside of the ball bearing can be absorbed.
- FIG. 4B is a diagram showing a state in which the ball bearing 14 slides in the axial length direction with a dimensional difference dD.
- FIG. 4B shows an example in which the bearing outer ring dimension D1 is longer than the bearing inner ring dimension D2.
- the bearing outer ring dimension D1 is longer than the bearing inner ring dimension D2.
- the influence by the dimension D1 between bearing outer rings which became long is absorbed by the height h at the time of deformation
- the claw 20a disposed in the circumferential direction of the washer 20 is used to prevent the creep phenomenon by engaging the claw 20a in a wedge shape against the idling force applied as the circumferential force. With respect to the force applied in the thrust direction due to the dimensional difference as described above, the claw 20a is deformed to prevent the ball bearings 14 and 15 from rattling. In this embodiment, in this way, the motor 10 with stable low vibration and low noise is provided by preventing the play inside the ball bearing together with the creep phenomenon.
- FIG. 5 is an enlarged partial cross-sectional view of a portion of the bearing housing 52a of the bracket 12 according to the second embodiment of the present invention.
- the electric motor 10 of the present embodiment is different from the first embodiment in the configuration of the bearing housing 52a on the side opposite to the output shaft of the rotating shaft 43 and the configuration of the washer 25 disposed on the bearing housing 52a.
- Other configurations are the same as those in the first embodiment, and detailed description thereof is omitted.
- the bracket 12 in order to hold the ball bearing 14, the bracket 12 is formed with a bearing housing 52 a that is a cylindrical depression.
- the bearing housing 52a generally has a shape having a cylindrical cylindrical portion 52c and an end wall 52b which is a circular surface at the bottom thereof.
- the ball bearing 14 is inserted into the bearing housing 52a such that the outer peripheral surface of the bearing outer ring 14b faces the inner peripheral surface of the cylindrical portion 52c of the bearing housing 52a.
- a washer 25 is inserted between one bearing seal plate 14d of the ball bearing 14 and the end wall 52b of the bearing housing 52a.
- FIG. 6A is an external view of the washer 25 according to Embodiment 2 of the present invention.
- FIG. 6B is an external view of another configuration example of the washer 25 according to Embodiment 2 of the present invention.
- the washer 25 has an annular yoke 25b and a plurality of claws 20a for applying a bearing preload to the ball bearing 14. More specifically, the washer 25 is configured by arranging a plurality of U-shaped claws 20a similar to those of the first embodiment at equal intervals on the inner peripheral side of the yoke 25b which is a flat washer. ing.
- the claws 20 a of the washer 25 are arranged so as to face both sides of the ball bearing 14 and the end wall 52 b of the bracket 12. That is, each nail
- FIG. 6A shows an example in which the three claws 20a are oriented in the direction of the ball bearing 14 and the other three claws 20a are oriented in the direction of the end wall 52b.
- the washer 25 shown in FIG. 6B has a configuration in which a plurality of claws 20a having the same U-shape as in FIG. 6A are arranged on an annular corrugated yoke 26b so that the tips thereof are alternately reversed. It is.
- each claw 20a in FIG. 6A and FIG. 6B is arranged so that the both ends thereof are along the circumferential direction as in the first embodiment.
- FIG. 7A is a front view of the bearing housing 52a of the bracket 12 according to Embodiment 2 of the present invention
- FIG. 7B is a sectional view of the same.
- the bracket 12 has a bearing housing 52a that holds the ball bearing 14 at the center.
- the end wall 52b of the bearing housing 52a is provided with a plurality of end wall steps 52d extending radially in the radial direction. Such an end wall step 52d is provided to engage with the claw 20a of the washer 25.
- FIG. 7A shows an example in which three end wall steps 52d are provided in accordance with the number of claws 20a on the end wall 52b side in FIGS. 6A and 6B.
- the ball bearing 14 has a bearing seal plate 14 d whose surface is covered with rubber on the side surface facing the washer 25, and the claw 20 a of the washer 25. Is in contact with the bearing seal plate 14d with a light load. The claw 20a facing the end wall 52b of the bracket 12 is engaged with the end wall step 52d.
- the claw 20a of the washer 25 is provided on both sides in the present embodiment. For this reason, it is possible to prevent idling of both the idling between the ball bearing 14 and the washer 25 and the idling between the washer 25 and the bearing housing 52a.
- this configuration not only makes it possible to prevent slipping more reliably, but also eliminates the need to regulate directionality when the washer 25 is inserted when the electric motor 10 is assembled. The property can be further improved.
- the bracket 13 on the output shaft side is described as a synthetic resin material
- the bracket 12 on the counter-output shaft side is described as a steel plate material.
- both are made of a synthetic resin material or a steel plate material. May be.
- the surface of the bearing seal plate 14d of the ball bearing 14 is described as a rubber type, but a steel plate material may be used.
- the electric motor of the present invention includes a washer between one ball bearing and the end wall of the bearing housing, and the washer has a plurality of claws.
- the electric motor of the present invention it is possible to obtain a low-vibration and low-noise electric motor capable of preventing a bearing slipping phenomenon while securing a stable bearing preload.
- the electric motor of the present invention is optimal for preventing the idling of ball bearings and improving the reliability of electric motors using synthetic resin brackets, and is intended for use in high-speed rotation conditions and applications requiring high-temperature reliability. Also useful.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Power Engineering (AREA)
- Motor Or Generator Frames (AREA)
- Support Of The Bearing (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
Description
図1は、本発明の実施の形態1における電動機10の一部断面の側面図である。本実施の形態では、電動機10として、整流子電動機および送風用ファンを備え、電気掃除機などの電動送風機として利用される電動機の一例を挙げて説明する。
図5は、本発明の実施の形態2におけるブラケット12の軸受ハウジング52aの箇所を拡大した部分断面図である。本実施の形態の電動機10は、実施の形態1との比較において、回転軸43の反出力軸側での軸受ハウジング52aの構成と軸受ハウジング52aに配置されるワッシャー25の構成とが異なっている。その他の構成については、実施の形態1と同様であり、詳細な説明は省略する。
11 整流子電動機
12 第1のブラケット
12a,13a,52a 軸受ハウジング
12b,52b 端壁
12c,52c 円筒部
13 第2のブラケット
14,15 玉軸受
14a,15a 軸受内輪
14b,15b 軸受外輪
14c 鉄ボール
14d 軸受シール板
17 ファンケース
17a 吸気口
18 ファン
19 エアガイド
20,25 ワッシャー
20a 爪
20b,21b,25b,26b ヨーク
30 固定子
31 界磁コア
32 界磁巻線
35 ブラシ
40 回転子
41 電機子コア
42 電機子巻線
43 回転軸
45 整流子
52d 端壁段差
Claims (9)
- 回転軸を有する回転子と、前記回転軸を支持する一対の玉軸受と、前記玉軸受を保持するための軸受ハウジングを有する2つのブラケットとを含む電動機であって、
一方の前記玉軸受と前記軸受ハウジングの端壁との間にワッシャーを備え、
前記ワッシャーは、複数個の爪を有することを特徴とする電動機。 - 前記ワッシャーは、環状のヨークと、中央部が前記ヨークに固着した複数個の前記爪とを含み、
前記爪は、U字状に湾曲した形状であることを特徴とする請求項1に記載の電動機。 - 前記ヨークを波形としたことを特徴とする請求項2に記載の電動機。
- 他方の前記玉軸受と前記軸受ハウジングとは固定されていることを特徴とする請求項1に記載の電動機。
- 前記一方の玉軸受と前記ワッシャーの爪との間の静摩擦係数をμ1、前記一方の軸受ハウジングの端壁と前記ワッシャーの爪との間の静摩擦係数をμ2としたとき、
μ1とμ2とのどちらか小さい方向に向けて、前記爪を配置したことを特徴とする請求項1に記載の電動機。 - 前記爪を、前記一方の玉軸受および前記一方の軸受ハウジングの端壁の双方に対向するように両面に向けて配置したことを特徴とする請求項1に記載の電動機。
- 前記ブラケットの少なくとも一方が合成樹脂製であることを特徴とする請求項1に記載の電動機。
- 前記一方の玉軸受は、軸受シール板を有し、
前記軸受シール板は、ラバータイプであることを特徴とする請求項1に記載の電動機。 - 前記爪と対向する前記一方の軸受ハウジングの端壁面に、前記爪と勘合する端壁段差を設けたことを特徴とする請求項1に記載の電動機。
Priority Applications (3)
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CN201280047923.1A CN103842670B (zh) | 2011-09-29 | 2012-08-21 | 电动机 |
US14/239,949 US9509191B2 (en) | 2011-09-29 | 2012-08-21 | Electric motor with ball bearing assembly for rotary shaft |
JP2013535840A JP5873977B2 (ja) | 2011-09-29 | 2012-08-21 | 電動機 |
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PCT/JP2012/005216 WO2013046526A1 (ja) | 2011-09-29 | 2012-08-21 | 電動機 |
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US (1) | US9509191B2 (ja) |
JP (1) | JP5873977B2 (ja) |
CN (1) | CN103842670B (ja) |
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Cited By (1)
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WO2015043631A1 (en) * | 2013-09-25 | 2015-04-02 | Aktiebolaget Skf | Rolling bearing with seal and axial pre-stressing member |
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DE102014216506A1 (de) * | 2014-08-20 | 2016-02-25 | Aktiebolaget Skf | Wälzlager und Montageverfahren |
CN104852507A (zh) * | 2015-05-19 | 2015-08-19 | 巢惠英 | 一种吸尘器电动机 |
CN105822657B (zh) * | 2016-06-06 | 2019-05-03 | 吉林大学 | 一种可导电的曲轴 |
JP2019027523A (ja) * | 2017-07-31 | 2019-02-21 | 日本電産サンキョー株式会社 | 軸受組立体およびモータ |
KR102020727B1 (ko) | 2018-04-26 | 2019-09-10 | 엘지전자 주식회사 | 팬 모터 |
KR102396910B1 (ko) | 2018-04-26 | 2022-05-13 | 엘지전자 주식회사 | 팬 모터 |
US11353061B1 (en) * | 2020-12-14 | 2022-06-07 | Schaeffler Technologies AG & Co. KG | Preloaded shaft assembly |
US11933357B2 (en) * | 2021-06-16 | 2024-03-19 | Schaeffler Technologies AG & Co. KG | Bearing with integrated axial preload and method thereof |
US11873878B2 (en) * | 2021-07-06 | 2024-01-16 | GM Global Technology Operations LLC | Noise vibration harshness reduction assembly and methods, an axial ring configured to attenuate sound inducing vibrations |
KR20230095485A (ko) * | 2021-12-22 | 2023-06-29 | 엘지이노텍 주식회사 | 모터 |
KR20240051694A (ko) * | 2022-10-13 | 2024-04-22 | 엘지전자 주식회사 | 팬 모터 |
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- 2012-08-21 WO PCT/JP2012/005216 patent/WO2013046526A1/ja active Application Filing
- 2012-08-21 JP JP2013535840A patent/JP5873977B2/ja active Active
- 2012-08-21 US US14/239,949 patent/US9509191B2/en active Active
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WO2015043631A1 (en) * | 2013-09-25 | 2015-04-02 | Aktiebolaget Skf | Rolling bearing with seal and axial pre-stressing member |
Also Published As
Publication number | Publication date |
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US20140184004A1 (en) | 2014-07-03 |
JP5873977B2 (ja) | 2016-03-01 |
US9509191B2 (en) | 2016-11-29 |
CN103842670B (zh) | 2016-10-05 |
CN103842670A (zh) | 2014-06-04 |
JPWO2013046526A1 (ja) | 2015-03-26 |
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