WO2014061156A1 - Electric motor and manufacturing method - Google Patents
Electric motor and manufacturing method Download PDFInfo
- Publication number
- WO2014061156A1 WO2014061156A1 PCT/JP2012/077126 JP2012077126W WO2014061156A1 WO 2014061156 A1 WO2014061156 A1 WO 2014061156A1 JP 2012077126 W JP2012077126 W JP 2012077126W WO 2014061156 A1 WO2014061156 A1 WO 2014061156A1
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- WIPO (PCT)
- Prior art keywords
- stator
- bearing
- rotor
- electric motor
- bearing holding
- Prior art date
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Classifications
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K1/00—Details of the magnetic circuit
- H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
- H02K1/12—Stationary parts of the magnetic circuit
- H02K1/18—Means for mounting or fastening magnetic stationary parts on to, or to, the stator structures
- H02K1/185—Means for mounting or fastening magnetic stationary parts on to, or to, the stator structures to outer stators
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- H—ELECTRICITY
- H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
- H02K—DYNAMO-ELECTRIC MACHINES
- H02K11/00—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection
- H02K11/20—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection for measuring, monitoring, testing, protecting or switching
- H02K11/21—Devices for sensing speed or position, or actuated thereby
- H02K11/215—Magnetic effect devices, e.g. Hall-effect or magneto-resistive elements
-
- 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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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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
-
- 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
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/07—Fixing them on the shaft or housing with interposition of an element
- F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
-
- 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
-
- 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
Definitions
- the present invention relates to an electric motor that supports both ends of a rotating shaft with a bearing, and a method for manufacturing the same.
- Patent Document 1 discloses an electric pump that includes a hydraulic pump and a motor (electric motor) that drives the hydraulic pump.
- This motor is a normal permanent magnet field DC motor, and has a structure in which a rotor is surrounded by a cylindrical stator to which a permanent magnet is fixed.
- bearings that support both rotating shafts are held by different members.
- one bearing is held by a casing that accommodates a stator and a rotor, and the other bearing is held by a flat plate portion of a lid-like member that is assembled to the casing.
- the bearings at both ends of the rotating shaft of the rotor are held by different members, due to variations in the dimensional accuracy of the holding portions of the respective members, between the rotor shaft and the stator shaft. Inevitably causes a coaxial shift. For this reason, it is necessary to provide an air gap between the outer peripheral surface of the rotor and the inner peripheral surface of the stator in consideration of the coaxial shift when designing the electric motor.
- the present invention was made in order to solve the above-described problems, and is intended to obtain an electric motor capable of suppressing the coaxial shift between the rotor and the stator and improving the output performance, and a method for manufacturing the same. Objective.
- An electric motor according to the present invention is provided integrally with a rotor fixed coaxially to a rotation shaft, a cylindrical stator surrounding the rotor on the inner diameter side, coaxially with the stator and on each end face of the stator. And a bearing holder that holds both ends of the bearing of the rotating shaft.
- FIG. 3 is a diagram showing a configuration of a stator in the electric motor according to Embodiment 1.
- FIG. 5 is a diagram for explaining a method for manufacturing the stator of the electric motor according to Embodiment 1.
- FIG. 3 is a diagram illustrating a holding structure of a bearing holding portion in the electric motor according to Embodiment 1. It is a figure explaining the flow of the magnetic flux of the structure (structure which provided the magnet in the stator) which concerns on Embodiment 1, and the conventional structure.
- FIG. 1 is a cross-sectional view showing a configuration of an electric motor according to Embodiment 1 of the present invention, and shows a cross section along an axial direction.
- An electric motor shown in FIG. 1 includes a stator 1, bearing holders 2 a and 2 b, a rotating shaft 3, a rotor 4 coaxially fixed to the rotating shaft 3, and bearings 5 a and 5 b fixed to each end of the rotating shaft 3. , A spring washer 6, a housing 7 for accommodating these components, and a plate 8 for covering the opening.
- the stator 1 is a cylindrical stator that surrounds the rotor 4 on the inner diameter side, and bearing holding portions 2a and 2b are integrally provided on each end face thereof.
- the stator 1 is configured by laminating and integrating a ring-shaped magnetic steel plate 1 a having a plurality of teeth portions 1 b formed on an inner peripheral portion.
- a conductive coil is wound around the laminated tooth portion 1b to form a stator coil 1c.
- the stator 1 may be configured by stacking and integrating a magnetic steel plate 1 a and a magnet (permanent magnet).
- the rotor 4 rotates around the rotating shaft 3 by connecting the magnetic flux of the magnet and the rotating magnetic flux of the coil through the air gap with the stator 1.
- a rotor in which a plurality of magnets are arranged in the circumferential direction to form a pole is used.
- the rotor 4 is composed of a rotor core and a rotor coil in which a conductive wire is wound around the rotor core.
- the bearing holding portions 2a and 2b are so-called trumpet-shaped members whose outer diameter gradually narrows from a flange portion fixed to the end face of the stator 1 to a cylindrical portion to which the bearings 5a and 5b are fitted.
- the trumpet-shaped bearing holders 2a and 2b are formed by drawing a magnetic steel plate used for the stator 1 or cutting a general magnetic steel material, for example.
- the bearings 5a and 5b are bearings that support the rotating shaft 3 at both ends, and are realized by, for example, bearings as shown in FIG.
- the bearing holding portions 2a and 2b are not limited to the trumpet shape, and may have a structure that can be provided coaxially and integrally with the stator 1 to hold the bearings 5a and 5b. .
- the spring washer 6 is disposed in a stepped portion provided on the inner surface of the housing 7 facing the bearing 5a, and pressurizes the bearing 5a in the direction of the bearing 5b. Further, the load due to the spring force of the spring washer 6 is received by the plate 8 via the bearing 5b.
- FIG. 3 is a diagram illustrating a method for manufacturing the stator of the electric motor according to the first embodiment. As shown in FIG. 3A, centering is performed by passing a bearing holding portion 2a, a stator 1 and a bearing holding portion 2b through a cylindrical centering member 9 in this order. Note that the end face diameter of the centering member 9 is substantially equal to the inner diameter of the stator 1, for example.
- the stator 1 may be configured by laminating and integrating magnetic steel plates 1a in a cylindrical shape.
- a part of the laminated surface of each magnetic steel sheet 1a is dented to form the convex part 10 and the concave part 11, and the convex part 10 is overlapped and laminated on the concave part 11 and caulked.
- the inner periphery of the concave portion 11 is the inner periphery of the concave portion 11.
- the bearing holder 2a, the stator 1 and the bearing holder 2b that have been centered through the centering member 9 are integrally connected.
- the flange portions of the bearing holding portions 2a and 2b and the respective end surfaces of the stator 1 are connected by caulking, for example, by forming the above-described concave portions and convex portions.
- the thickness t2 of the magnetic steel plate forming the bearing holders 2a, 2b is at least equal to or greater than the thickness t1 of the magnetic steel plate 1a of the stator 1 (t1 ⁇ t2) in order to ensure the strength to hold the bearings 5a, 5b.
- the laminated magnetic steel plate 1a works as a damper by using a steel plate having a certain spring constant as the magnetic steel plate 1a forming the stator 1, the amplitude of the rotating shaft 3 in a specific operating frequency band is suppressed. It can be set as a damping structure.
- the bearing holding portions 2a and 2b into a trumpet shape formed from a plate material, the flange portion fixed to the end surface of the stator 1 functions as a damper that absorbs the amount of vibration generated in the rotating shaft 3 during operation.
- a damping structure is provided that suppresses the shake of the rotating shaft 3 itself.
- stator unit a unit composed of the bearing holders 2a, 2b and the stator 1 that are integrally connected
- stator unit a unit composed of the bearing holders 2a, 2b and the stator 1 that are integrally connected
- rotor unit a unit composed of the rotating shaft 3, the bearings 5a and 5b, and the rotor 4 fixed coaxially to the rotating shaft 3 is passed through the stator unit, and the bearing holding portion 2a, The bearings 5a and 5b of the rotating shaft 3 are both held by 2b.
- FIG. 3 shows the case where the stator 1 is composed of laminated steel plates.
- a structure in which the bearing holding portion 2a, the stator 1 and the bearing holding portion 2b are integrated is formed by cutting from a magnetic steel material. Also good. Further, before the stator unit is assembled to the housing 7, the rotor unit may be assembled to the stator unit.
- FIG. 4 is a diagram illustrating a holding structure of a bearing holding portion in the electric motor according to Embodiment 1.
- the bearing holding portion 2 a of the stator unit is fitted in a fitting recess 7 a formed in the housing 7 as indicated by reference symbol A.
- the clearance amount between the outer periphery of the bearing holder 2a and the inner circumference of the fitting recess 7a is adjusted so that the bearing holder 2a does not swing due to the rotation of the rotary shaft 3.
- the outer peripheral portion of the bearing holding portion abuts on the inner peripheral portion of the fitting recess, and the amount of deflection is within an allowable range.
- the bearing holding portion 2b of the stator unit is fitted into a fitting recess 8a formed in the plate 8, as indicated by reference numeral B. Also in this configuration, the clearance amount between the outer periphery of the bearing holder 2b and the inner periphery of the fitting recess 8a is adjusted so that the bearing holder 2b does not swing due to the rotation of the rotary shaft 3.
- the bearing holding part 2 a of the stator unit is fitted into a fitting recess 7 a formed in the housing 7, and the bearing holding part 2 b of the stator unit is placed inside the plate 8.
- the clearance amount between the outer periphery of the bearing holding portion 2a and the inner periphery of the fitting recess 7a is adjusted so that the swing of the bearing holding portion 2a due to the rotation of the rotating shaft 3 is eliminated.
- the clearance amount between the outer periphery of the bearing holder 2b and the inner circumference of the fitting recess 8a is adjusted so that the bearing holder 2b does not swing.
- a bearing is a raceway ring when either an inner ring or an outer ring is fixed and an unfixed raceway is moved in a radial direction or an axial direction before being installed on a shaft or a housing (housing). Is set (hereinafter referred to as an internal gap ⁇ ).
- This internal gap ⁇ must be set in consideration of thermal expansion or fitting of the inner ring, outer ring and ball. If the internal gap ⁇ is too small, the internal gap ⁇ decreases due to thermal expansion of the shaft, housing (housing), inner ring, outer ring, and ball. For this reason, the motor performance deteriorates due to the heat generation of the bearing and the increase in sliding resistance during actual use, and the bearing life is reduced due to abnormal heat generation.
- the internal gap ⁇ is set to be large, the above-described problems are solved, but the amount of shake due to the inclination of the shaft becomes large, and vibration and rotational noise increase. If the operating temperature range of the bearing is large (in the automobile engine room, for example, the operating temperature range is from -40 ° C to 150 ° C), increasing the internal clearance ⁇ may cause the above-described problems. Therefore, it is preferable to set the internal gap ⁇ as small as possible.
- the internal clearance ⁇ can be set small by preventing the bearing holding portion from being press-fitted into the fitting recess.
- the internal clearance of this bearing is ⁇ 1
- the inner ring side of the bearing is inserted, and the outer ring side is press-fitted (press-fitted)
- the internal clearance of this bearing is ⁇ 2.
- the internal clearance of the bearing is ⁇ 3
- both the inner ring side and the outer ring side of the bearing are press-fitted (condition 4).
- the internal clearance of this bearing is ⁇ 4.
- the larger the internal clearance ⁇ the more the bearing can be used in an environment where the operating temperature range is large, such as in an automobile engine room.
- the bearing holding part is not press-fitted into the fitting recess and the inner ring side and the outer ring side of the bearing (the outer peripheral side of the bearing holding part when held by the bearing holding part) are not press-fitted (condition 1).
- the operating temperature range can be set large.
- the internal clearance of the bearing becomes large, the above-described malfunction due to the shaft swing may occur.
- the amount of shake can be suppressed by setting the clearance amount so that the amount of shake is in an allowable range by contacting the portion.
- the stator 1 having a stator coil has been taken as an example.
- a magnet permanent magnet
- the rotor core is magnetized by the magnetic flux of the magnet. It is good also as an electric motor.
- the magnetic flux leakage can be reduced by using the bearing holders 2a and 2b, the rotating shaft 3, the rotor 4 and the bearings 5a and 5b as magnetic bodies.
- FIG. 5 is a diagram for explaining the flow of magnetic flux between the configuration of the electric motor according to Embodiment 1 (configuration in which a magnet is provided on the stator) and the conventional configuration.
- the configuration shown in FIG. 5A is a conventional electric motor that does not have the bearing holding portions 2a and 2b.
- the stator 1 is provided with a magnet 1A, and constitutes a magnetic flux circuit a that magnetizes the rotor 4 (magnetic flux amount A).
- the magnet 1A forms a magnetic flux circuit b which does not pass through the rotor 4 and does not contribute to the magnetization of the rotor 4 due to the structure of the electric motor (magnetic flux amount B).
- the magnet 1A does not magnetize the rotor 4 with all the magnetic flux generated by itself, but the total magnetic flux amount Z is the sum of the magnetic flux amount A of the magnetic flux circuit a and the magnetic flux amount B of the magnetic flux circuit b. Become. Such leakage magnetic flux in the magnetic flux circuit b becomes noise and affects the operation of the peripheral electronic component 12.
- the bearing holding portions 2a and 2b, the rotating shaft 3, the rotor 4 and the bearings 5a and 5b are made of a magnetic material.
- the magnetic flux amount A of the magnetic flux circuit a does not change, and the magnetic flux leakage circuit is reduced by the magnetic flux circuit c to become the magnetic flux circuit b1 (magnetic flux amount B1 ⁇ magnetic flux amount B). That is, the total magnetic flux amount Z of the magnetic flux circuit magnet 1A is the sum of the magnetic flux amount A of the magnetic flux circuit a, the magnetic flux amount B1 of the magnetic flux circuit b1, and the magnetic flux amount C of the magnetic flux circuit c. Therefore, it is possible to reduce the leakage magnetic flux that becomes noise of the peripheral electronic component 12.
- the rotor 4 that is coaxially fixed to the rotating shaft 3, the cylindrical stator 1 that surrounds the rotor 4 on the inner diameter side, and the stator 1 are coaxial.
- bearing holding portions 2a and 2b that are integrally provided on each end face of the stator 1 and hold both bearings 5a and 5b of the rotating shaft 3 are provided.
- the coaxial displacement between the rotor 4 and the stator 1 is suppressed by the bearing holders 2a and 2b provided coaxially with the stator 1 and on each end face of the stator 1, It is possible to reduce the air gap between the rotor 4 and the stator 1. Thereby, the output performance of the electric motor according to the first embodiment can be improved.
- the bearing holders 2a and 2b have a trumpet shape in which the outer diameter gradually narrows, and hold the bearings 5a and 5b of the rotary shaft 3 on the inner diameter side.
- the flange portion fixed to the end face of 1 functions as a damper that absorbs the amount of vibration generated in the rotating shaft 3 during operation, and can suppress the vibration of the rotating shaft 3 itself.
- the centering member 9 is centered by passing the one bearing holding portion 2a, the stator 1 and the other bearing holding portion 2b through the columnar centering member 9 in order.
- the bearing holders 2a and 2b that have been centered through the centering member 9 and the stator 1 are connected together, the rotor unit is passed through the stator unit, and the shaft is rotated by the bearing holders 2a and 2b. 3 bearings 5a and 5b are both held.
- the centering member 9 can easily center the bearing holding portions 2a, 2b and the stator 1. Thereby, it is possible to simplify the manufacture of the electric motor.
- the stator 1 is a stator formed by laminating and integrating the magnetic steel plates 1a, and the magnetic steel plates forming the bearing holding portions 2a and 2b are the magnetic steel plates of the stator 1.
- the thickness t2 is equal to or greater than the thickness t1 of 1a.
- the housing 7 that accommodates the rotor 4 and the stator 1 and the plate 8 that covers the opening of the housing 7 are provided, and any one of the bearing holding portions 2a and 2b is disposed in the housing. 7 or the fitting recesses 7a and 8a formed inside the plate 8 or the bearing holding portion 2a is fitted and fixed to the fitting recess 7a formed inside the housing 7, and the bearing holding portion 2b. Is fitted and fixed in a fitting recess 8 a formed in the plate 8. With this configuration, it is possible to suppress the shake of the bearing holders 2 a and 2 b due to the rotation of the rotary shaft 3.
- the magnet 1A is disposed on the stator 1, and the bearing holders 2a and 2b, the bearings 5a and 5b, the rotating shaft 3 and the rotor 4 are made of a magnetic material.
- a new magnetic flux circuit can be formed via the bearing holding portions 2a and 2b with the magnetic flux of the magnet 1A, and the leakage magnetic flux that becomes noise of the peripheral electronic component 12 can be reduced.
- any component of the embodiment can be modified or any component of the embodiment can be omitted within the scope of the invention.
- the electric motor according to the present invention can be applied to various electric motors such as a synchronous electric motor, for example, because the coaxial displacement between the rotor and the stator is suppressed and the output performance can be improved.
Abstract
Description
また、回転子と固定子との同軸ずれは、軸回転時の軸受けの径方向の負荷を増大させるため、軸受けの摺動抵抗が大きくなる。これにより、電動機自体の機械的な損失が大きくなって出力性能が低下する。この摺動抵抗の増加は、軸受けの短命化の要因にもなる。
さらに、同軸ずれ量が増加した場合、高回転時に回転子が固定子に接触する軸触れ量が増加するため、回転軸が損傷する可能性もある。 When the air gap between the rotor and the stator is increased, the magnetic resistance is increased accordingly, and the output performance of the electric motor is remarkably deteriorated.
Further, the coaxial displacement between the rotor and the stator increases the radial load of the bearing during shaft rotation, and therefore the sliding resistance of the bearing increases. As a result, the mechanical loss of the motor itself increases and the output performance decreases. This increase in sliding resistance also causes a short life of the bearing.
Furthermore, when the amount of coaxial deviation increases, the amount of shaft contact with which the rotor contacts the stator during high rotation increases, which may damage the rotating shaft.
しかしながら、従来のように回転軸の軸受けをそれぞれ別の部材で保持する構成では、互いが同軸になるように、高い寸法精度の加工が必要となる。
例えば、軸受けとなるベアリングの一方を筐体に嵌合保持する場合、もう一方のベアリングの保持部との同軸を考慮しながら、嵌合箇所を高精度の切削加工で作成しなければならない。 Therefore, in order to prevent the above problems and improve the output performance of the electric motor, it is necessary to reduce the coaxial gap between the rotor and the stator as much as possible to reduce the air gap.
However, in the conventional configuration in which the bearings of the rotating shaft are held by different members, processing with high dimensional accuracy is required so that they are coaxial with each other.
For example, when one of the bearings serving as a bearing is fitted and held in the housing, the fitting portion must be created by high-precision cutting while considering the coaxial with the holding portion of the other bearing.
実施の形態1.
図1は、この発明の実施の形態1に係る電動機の構成を示す断面図であって、軸方向に沿った断面を示している。図1に示す電動機は、固定子1、軸受け保持部2a,2b、回転軸3、回転軸3に同軸に固着された回転子4、回転軸3の各端部に固着された軸受け5a,5b、バネワッシャ6、これらの構成を収容するハウジング7およびその開口部を覆うプレート8を備えて構成される。 Hereinafter, in order to describe the present invention in more detail, modes for carrying out the present invention will be described with reference to the accompanying drawings.
1 is a cross-sectional view showing a configuration of an electric motor according to
なお、ラッパ形状の軸受け保持部2a,2bは、例えば、固定子1に使用される磁性鋼板を絞り加工して作成するか、一般の磁性鋼材を切削加工して作成する。
軸受け5a,5bは、回転軸3を両持ち支持する軸受けであって、例えば、図1に示すようにベアリングで実現される。なお、この発明において、軸受け保持部2a,2bは、ラッパ形状に限定されるものではなく、固定子1に同軸で一体に設けられて軸受け5a,5bを保持できる構造を有していればよい。 The
The trumpet-shaped
The
なお、軸受け保持部に軸受けが遊嵌される場合は、軸受けの外周と軸受け保持部の内周との間にダンパを設けてもよい。 In the holding of the
When the bearing is loosely fitted to the bearing holding portion, a damper may be provided between the outer periphery of the bearing and the inner periphery of the bearing holding portion.
図3は、実施の形態1に係る電動機の固定子の製造方法を説明する図である。図3(a)に示すように、円柱状の芯出し部材9に、軸受け保持部2a、固定子1、軸受け保持部2bを順に通して芯出しを行う。なお、芯出し部材9の端面径は、例えば固定子1の内径に略等しい。 Next, a method for manufacturing the
FIG. 3 is a diagram illustrating a method for manufacturing the stator of the electric motor according to the first embodiment. As shown in FIG. 3A, centering is performed by passing a
また、軸受け保持部2a,2bを板材から形成したラッパ形状とすることで、固定子1の端面に固着されるフランジ部が、動作中に回転軸3に発生する振れ量を吸収するダンパとして働き、回転軸3自体の振れを抑制する減衰構造となる。 The thickness t2 of the magnetic steel plate forming the
Further, by forming the
図4は、実施の形態1に係る電動機における軸受け保持部の保持構造を示す図である。図4(a)では、符号Aで示すように、固定子ユニットの軸受け保持部2aを、ハウジング7内に形成した嵌合凹部7aに嵌合している。この構成において、回転軸3の回転による軸受け保持部2aの振れがなくなるように、軸受け保持部2aの外周と嵌合凹部7aの内周とのクリアランス量を調整しておく。例えば、動作中に軸受け保持部の外周部が嵌合凹部の内周部に当接して振れ量が許容範囲となるクリアランス量とする。 The assembly of the stator unit inside the electric motor can be configured as shown in FIG. 4 in order to suppress the shake of the bearing holding portion due to the rotation of the
FIG. 4 is a diagram illustrating a holding structure of a bearing holding portion in the electric motor according to
また、内部隙間σが小さ過ぎる場合には、軸、筐体(ハウジング)、内輪、外輪およびボールの熱膨張によって内部隙間σが減少する。このため、実使用時に軸受けの発熱および摺動抵抗の増加からモータ性能が悪化し、異常発熱によって軸受け寿命が低下する。
一方、内部隙間σを大きく設定した場合は、上述した不具合は解消するが、軸の傾きによる振れ量が大きくなり、振動および回転音の増大が発生する。
なお、軸受けの使用温度範囲が大きい場合(自動車エンジン室内では、例えば-40℃から150℃までが使用温度範囲となる)は、内部隙間σを大きくすると、上述のような不具合が発生する要因となるため、できる限り内部隙間σを小さく設定することが好ましい。 Generally, a bearing is a raceway ring when either an inner ring or an outer ring is fixed and an unfixed raceway is moved in a radial direction or an axial direction before being installed on a shaft or a housing (housing). Is set (hereinafter referred to as an internal gap σ). This internal gap σ must be set in consideration of thermal expansion or fitting of the inner ring, outer ring and ball.
If the internal gap σ is too small, the internal gap σ decreases due to thermal expansion of the shaft, housing (housing), inner ring, outer ring, and ball. For this reason, the motor performance deteriorates due to the heat generation of the bearing and the increase in sliding resistance during actual use, and the bearing life is reduced due to abnormal heat generation.
On the other hand, when the internal gap σ is set to be large, the above-described problems are solved, but the amount of shake due to the inclination of the shaft becomes large, and vibration and rotational noise increase.
If the operating temperature range of the bearing is large (in the automobile engine room, for example, the operating temperature range is from -40 ° C to 150 ° C), increasing the internal clearance σ may cause the above-described problems. Therefore, it is preferable to set the internal gap σ as small as possible.
例えば、軸受けの内輪側を挿入(圧入しない嵌合)、外輪側を挿入した場合(条件1)において、この軸受けの内部隙間をσ1とし、軸受けの内輪側を挿入、外輪側を圧入(圧入する嵌合)した場合(条件2)において、この軸受けの内部隙間をσ2とする。
また、軸受けの内輪側を圧入し、外輪側を挿入した場合(条件3)において、この軸受けの内部隙間をσ3とし、軸受けの内輪側および外輪側の双方を圧入した場合(条件4)において、この軸受けの内部隙間をσ4とする。
条件1~4の軸受けを使用した際の内部隙間の大小関係は、σ1>σ2=σ3>σ4となる。なお、熱膨張を考慮すると内部隙間σが大きいほど、自動車エンジン室内のように使用温度範囲が大きい環境においても軸受けを使用することができる。 As shown in FIG. 4, the internal clearance σ can be set small by preventing the bearing holding portion from being press-fitted into the fitting recess.
For example, when the inner ring side of the bearing is inserted (fitted without press-fitting) and the outer ring side is inserted (condition 1), the internal clearance of this bearing is σ1, the inner ring side of the bearing is inserted, and the outer ring side is press-fitted (press-fitted) In the case of fitting) (condition 2), the internal clearance of this bearing is σ2.
Further, when the inner ring side of the bearing is press-fitted and the outer ring side is inserted (condition 3), the internal clearance of the bearing is σ3, and both the inner ring side and the outer ring side of the bearing are press-fitted (condition 4). The internal clearance of this bearing is σ4.
The size relationship of the internal gap when using the bearings of
なお、軸受けの内部隙間が大きくなると、上述した軸の振れによる不具合が発生する可能性があるが、図4に示したように、動作中に軸受け保持部の外周部が嵌合凹部の内周部に当接して振れ量が許容範囲となるクリアランス量とすることにより、振れ量を抑制することができる。 Therefore, it is assumed that the bearing holding part is not press-fitted into the fitting recess and the inner ring side and the outer ring side of the bearing (the outer peripheral side of the bearing holding part when held by the bearing holding part) are not press-fitted (condition 1). In this case, the operating temperature range can be set large.
In addition, if the internal clearance of the bearing becomes large, the above-described malfunction due to the shaft swing may occur. However, as shown in FIG. The amount of shake can be suppressed by setting the clearance amount so that the amount of shake is in an allowable range by contacting the portion.
しかしながら、図5(a)に示すように、マグネット1Aは、電動機の構造上、回転子4を経由せず、回転子4の磁化に寄与しない磁束回路bを形成する(磁束量B)。
すなわち、マグネット1Aは、自身が発生する磁束の全てで回転子4を磁化するのではなく、その総磁束量Zは、磁束回路aの磁束量Aと磁束回路bの磁束量Bとの和となる。
このような磁束回路bにおける漏れ磁束は、ノイズとなって周辺電子部品12の動作に影響を与える。 FIG. 5 is a diagram for explaining the flow of magnetic flux between the configuration of the electric motor according to Embodiment 1 (configuration in which a magnet is provided on the stator) and the conventional configuration. The configuration shown in FIG. 5A is a conventional electric motor that does not have the
However, as shown in FIG. 5A, the
That is, the
Such leakage magnetic flux in the magnetic flux circuit b becomes noise and affects the operation of the peripheral
これにより、図5(b)に示すように、マグネット1Aの磁束によって、マグネット1Aから、軸受け保持部2b、軸受け5b、回転軸3、回転子4、軸受け5a、軸受け保持部2bの順で、マグネット1Aに戻る磁束回路cを形成することができる(磁束量C)。
この構成では、磁束回路aの磁束量Aは変化せず、磁束回路cによって漏れ磁束が低減して、磁束回路b1となる(磁束量B1<磁束量B)。すなわち、磁束回路マグネット1Aの総磁束量Zは、磁束回路aの磁束量Aと、磁束回路b1の磁束量B1と、磁束回路cの磁束量Cとの和となる。従って、周辺電子部品12のノイズとなる漏れ磁束を低減することができる。 Therefore, in the electric motor in which the
Thereby, as shown in FIG.5 (b), with the magnetic flux of
In this configuration, the magnetic flux amount A of the magnetic flux circuit a does not change, and the magnetic flux leakage circuit is reduced by the magnetic flux circuit c to become the magnetic flux circuit b1 (magnetic flux amount B1 <magnetic flux amount B). That is, the total magnetic flux amount Z of the magnetic
Claims (6)
- 回転軸に同軸に固着された回転子と、
内径側に前記回転子を囲繞する円筒状の固定子と、
前記固定子と同軸にかつ当該固定子の各端面に一体に設けられて、前記回転軸の軸受けを両持ち保持する軸受け保持部とを備える電動機。 A rotor fixed coaxially to the rotation axis;
A cylindrical stator surrounding the rotor on the inner diameter side;
An electric motor provided with a bearing holding portion that is provided coaxially with the stator and integrally on each end face of the stator and holds both ends of the bearing of the rotating shaft. - 前記軸受け保持部は、外径が徐々に窄まるラッパ形状を有し、内径側で前記回転軸の軸受けを保持することを特徴とする請求項1記載の電動機。 The electric motor according to claim 1, wherein the bearing holding portion has a trumpet shape in which an outer diameter gradually narrows, and holds the bearing of the rotating shaft on an inner diameter side.
- 前記回転子および前記固定子を収容するハウジングと、
前記ハウジングの開口を覆うプレートとを備え、
前記軸受け保持部のいずれか一方を、前記ハウジングまたは前記プレートの内部に形成した嵌合凹部に嵌合固定する、あるいは、前記軸受け保持部の一方を、前記ハウジングの内部に形成した嵌合凹部に嵌合固定し、前記軸受け保持部のもう一方を、前記プレートの内部に形成した嵌合凹部に嵌合固定することを特徴とする請求項1記載の電動機。 A housing for housing the rotor and the stator;
A plate covering the opening of the housing,
Either one of the bearing holding portions is fitted and fixed in a fitting recess formed in the housing or the plate, or one of the bearing holding portions is fitted in a fitting recess formed in the housing. The electric motor according to claim 1, wherein the electric motor is fitted and fixed, and the other of the bearing holding portions is fitted and fixed in a fitting concave portion formed in the plate. - 前記固定子は、磁性鋼板を積層一体化して形成した固定子であり、
前記軸受け保持部を形成する磁性鋼板は、前記固定子の前記磁性鋼板の厚さ以上の厚さを有することを特徴とする請求項1記載の電動機。 The stator is a stator formed by laminating and integrating magnetic steel plates,
The electric motor according to claim 1, wherein the magnetic steel plate forming the bearing holding portion has a thickness equal to or greater than the thickness of the magnetic steel plate of the stator. - 前記固定子は、永久磁石が配設されており、
前記軸受け保持部、前記軸受け、前記回転軸および前記回転子は、磁性体で構成されていることを特徴とする請求項1記載の電動機。 The stator is provided with a permanent magnet,
The electric motor according to claim 1, wherein the bearing holding portion, the bearing, the rotating shaft, and the rotor are made of a magnetic material. - 回転軸に同軸に固着された回転子と、
内径側に前記回転子を囲繞する円筒状の固定子と、
前記固定子と同軸にかつ当該固定子の各端面に一体に設けられて、前記回転軸の軸受けを両持ち保持する軸受け保持部とを備える電動機の製造方法において、
円柱状の芯出し部材に、一方の前記軸受け保持部、前記固定子、もう一方の前記軸受け保持部を順に通して芯出しを行うステップと、
前記芯出し部材に通して芯出しを行った前記軸受け保持部と前記固定子とを一体に接続するステップと、
前記回転軸、前記軸受けおよび前記回転軸に同軸に固着された回転子からなるユニットを、一体に接続された前記軸受け保持部と前記固定子とからなるユニットに通して、前記軸受け保持部により前記回転軸の軸受けを両持ち保持するステップとを備えることを特徴とする電動機の製造方法。 A rotor fixed coaxially to the rotation axis;
A cylindrical stator surrounding the rotor on the inner diameter side;
In a method of manufacturing an electric motor comprising a bearing holding portion that is coaxial with the stator and integrally provided on each end face of the stator and holds both ends of the bearing of the rotating shaft.
A step of performing centering by sequentially passing one of the bearing holders, the stator, and the other bearing holder in a cylindrical centering member;
A step of integrally connecting the bearing holding portion and the stator that have been centered through the centering member;
A unit consisting of the rotating shaft, the bearing and a rotor fixed coaxially to the rotating shaft is passed through a unit consisting of the bearing holding portion and the stator connected together, and the bearing holding portion causes the And a step of holding both ends of the bearing of the rotating shaft.
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WO2019052834A1 (en) * | 2017-09-13 | 2019-03-21 | Valeo Systemes D Essuyage | Wiper motor and method for its assembly |
JP2019047572A (en) * | 2017-08-30 | 2019-03-22 | アイシン精機株式会社 | Electric motor |
WO2021165026A1 (en) * | 2020-02-17 | 2021-08-26 | Scanlab Gmbh | Galvanometer drive with zero-backlash mounting |
EP4037167A1 (en) * | 2021-02-02 | 2022-08-03 | The Boeing Company | Rotary electric machine |
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CN107659010A (en) * | 2017-10-30 | 2018-02-02 | 南京磁谷科技有限公司 | A kind of compressing structure of motor stator |
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Cited By (6)
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JP2019047572A (en) * | 2017-08-30 | 2019-03-22 | アイシン精機株式会社 | Electric motor |
WO2019052834A1 (en) * | 2017-09-13 | 2019-03-21 | Valeo Systemes D Essuyage | Wiper motor and method for its assembly |
JP2020533937A (en) * | 2017-09-13 | 2020-11-19 | ヴァレオ システム デシュヤージュValeo Systemes D’Essuyage | Wiper motor and its assembly method |
JP7258015B2 (en) | 2017-09-13 | 2023-04-14 | ヴァレオ システム デシュヤージュ | Wiper motor and its assembly method |
WO2021165026A1 (en) * | 2020-02-17 | 2021-08-26 | Scanlab Gmbh | Galvanometer drive with zero-backlash mounting |
EP4037167A1 (en) * | 2021-02-02 | 2022-08-03 | The Boeing Company | Rotary electric machine |
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