WO2018052092A1 - Gear assembly, planetary gear mechanism using gear assembly, and motor with built-in gear mechanism - Google Patents

Gear assembly, planetary gear mechanism using gear assembly, and motor with built-in gear mechanism Download PDF

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Publication number
WO2018052092A1
WO2018052092A1 PCT/JP2017/033333 JP2017033333W WO2018052092A1 WO 2018052092 A1 WO2018052092 A1 WO 2018052092A1 JP 2017033333 W JP2017033333 W JP 2017033333W WO 2018052092 A1 WO2018052092 A1 WO 2018052092A1
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WIPO (PCT)
Prior art keywords
gear
planetary gear
shaft
planetary
gear mechanism
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PCT/JP2017/033333
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French (fr)
Japanese (ja)
Inventor
卓志 松任
川合　正浩
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Ntn株式会社
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Publication of WO2018052092A1 publication Critical patent/WO2018052092A1/en

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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
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • 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
    • 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
    • F16C19/08—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 two or more rows of balls
    • 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
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/64—Special methods of manufacture
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/36—Toothed gearings for conveying rotary motion with gears having orbital motion with two central gears coupled by intermeshing orbital gears
    • 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
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters
    • H02K7/116—Structural association with clutches, brakes, gears, pulleys or mechanical starters with gears

Definitions

  • the present invention relates to a gear assembly combining a helical gear (helical gear) and a support shaft that rotatably supports the gear assembly, a planetary gear mechanism using the gear assembly, and a motor incorporating the planetary gear mechanism.
  • a planetary gear unit incorporated in a reduction gear or a speed increaser incorporates a plurality of planetary gears that mesh with both a sun gear and a ring gear.
  • the planetary gear is generally composed of a helical gear.
  • a helical gear with a shaft hole is rotatably supported by a support shaft inserted through the shaft hole, or a needle bearing or ball bearing is used with a bearing interposed between the shaft and the support shaft. I support it as possible.
  • the support by a ball bearing is shown by the following patent document 2, for example.
  • the needle bearing is shown by the following patent document 3. FIG.
  • a pinion gear (planetary gear constituted by a helical gear) is rotatably supported by a needle bearing interposed between a pin (support shaft) fixed to a planetary carrier, and an end face of the pinion gear
  • a thrust washer (this is a kind of thrust plate) is interposed between the carrier and the planetary carrier.
  • a thrust load is generated during rotation.
  • the thrust load is not negligible particularly in the planetary gear device provided in the speed increaser because the planetary gear rotates at a high speed.
  • a thrust needle bearing and a thrust plate are provided to receive the thrust load.
  • the bearing interposed between the support shaft and the planetary gear is a needle bearing that cannot cope with the thrust load
  • a thrust needle bearing or a thrust plate is essential.
  • the bearing is a ball bearing, it can be received without a thrust needle bearing or thrust plate if the thrust load is not very large.
  • a planetary gear using a general ball bearing having a dedicated inner race and outer race causes the following problems.
  • this axial force acts as a moment force on the bearing, it is inclined when the rolling element located at the inner diameter portion is a needle roller.
  • JP 2007-154911 A JP 2012-189202 A JP 2005-325965 A
  • the structure that directly supports the planetary gear with the support shaft can be used for gear mechanisms that do not receive a load in the thrust direction and gear mechanisms that use a light radial load. Is difficult.
  • a gear device in which thrust needle bearings and thrust plates are installed at both ends of the planetary gear inevitably deteriorates assembling due to an increase in the number of assembling steps.
  • the use of a thrust plate also causes an increase in gear rotation load due to friction.
  • the present invention has been made in view of the above state of the art, and the problem is that a gear assembly using a helical gear having a function of receiving a thrust load, a planetary gear mechanism using the gear assembly, and a planetary gear thereof. It is to realize and provide a motor with a built-in gear mechanism.
  • the present invention provides a gear assembly that combines a helical gear having a shaft hole and a support shaft that is passed through the shaft hole and rotatably supports the helical gear.
  • a gear assembly in which a ball bearing is disposed between a shaft, an inner race of the ball bearing is constituted by the support shaft, and an outer race is constituted by the helical gear.
  • a planetary gear mechanism including a planetary gear including a support shaft and a ball bearing constituted by the gear assembly, a planetary carrier assembled with the planetary gear, and a sun gear and a ring gear that mesh with the planetary gear, respectively. Further, the following gear mechanism built-in motors (1) and (2) are also provided.
  • the planetary gear mechanism is combined with an electric motor including a motor case, a stator core, a rotor, and a rotary shaft that serves as an output shaft, the planetary gear mechanism is built in a casing of the motor, and the rotary shaft is Gear mechanism built-in motor connected to planetary carrier of planetary gear mechanism.
  • the planetary gear mechanism is combined with an electric motor having a motor case, a stator core, a rotor, and a rotary shaft that is an output shaft, the planetary gear mechanism is built in a casing of the motor, and the rotary shaft is connected to the planetary gear.
  • Gear mechanism built-in motor connected to the sun gear of the gear mechanism.
  • the planetary gear mechanism functions as a speed increaser.
  • the planetary gear mechanism functions as a speed reducer.
  • the gear assembly according to the present invention may have the forms listed below. 1) A single row ball bearing is disposed between the helical gear and the support shaft. 2) A double row ball bearing is arranged between the helical gear and the support shaft. 3) An angular ball bearing is arranged between the helical gear and the support shaft. 4)
  • the support shaft is a solid shaft. 5) The support shaft has a first hole provided in the shaft center portion with one end opened to the end surface of the support shaft, and at least one second extending radially from the first hole and exiting to the outer periphery of the support shaft. With oil supply holes composed of holes. 6) A planetary gear for a planetary gear mechanism.
  • the support shaft of the gear assembly that constitutes the planetary gear can be fixed by caulking the planetary carrier.
  • the helical gear and the support shaft constitute an outer race and an inner race of ball bearings.
  • each of the support shaft and the helical gear has a raceway surface formed by an annular groove having an arcuate cross section at a corresponding position, and a rolling element (ball) is placed in the annular groove constituting the raceway surface. Part of the ball bearing is formed.
  • Ball bearings use balls (steel balls), and edge load due to moment load does not occur, so the change rate (decrease rate) in the calculated life is expected to be small.
  • the support shaft and the helical gear have a structure that combines the inner race and outer race of the ball bearing, a planetary gear mechanism that interposes a ball bearing having a dedicated inner race and outer race between the support shaft and the helical gear. Compared with the above, the radial dimension is reduced, and this also leads to miniaturization of various devices and apparatuses having a planetary gear mechanism.
  • a gear assembly in which a double-row ball bearing is arranged between the helical gear and the support shaft is excellent in supporting stability of the helical gear.
  • a gear assembly having an oil supply hole inside the support shaft can supply lubricating oil to improve the life of the ball bearing.
  • the planetary gear mechanism in which the support shaft is fixed to the planetary carrier by caulking and fixing does not require a nut for fixing the support shaft.
  • the number of parts can be reduced, and the axial dimension can be further shortened.
  • FIG. 6 is a cross-sectional view taken along the line XX in FIG. 5. It is sectional drawing which shows an example of the planetary gear mechanism (reduction gear) using the gear assembly of this invention.
  • FIG. 8 is a cross-sectional view taken along YY in FIG. 7. It is sectional drawing which shows an example of the motor which incorporated the speed up gear of FIG. It is sectional drawing which shows an example of the motor which incorporated the reduction gear of FIG.
  • a gear assembly 1 in FIG. 1 is configured by combining a helical gear 2, a support shaft 3, and a ball bearing 4.
  • the helical gear 2 has a cylindrical shaft hole 2a, and a support shaft 3 is inserted through the shaft hole 2a.
  • the ball bearing 4 is disposed between the helical gear 2 and the support shaft 3, and the helical gear 2 is rotatably supported on the support shaft 3 via rolling elements (balls) 4 a of the ball bearing 4.
  • the ball bearing 4 has an inner race constituted by the support shaft 3 and an outer race constituted by the helical gear 2.
  • Each of the helical gear 2 and the support shaft 3 has raceway surfaces 4b and 4c constituted by annular grooves having an arcuate cross section at corresponding positions, and the rolling elements 4a are arranged in the annular grooves constituting the raceway surfaces 4b and 4c.
  • the ball bearing 4 is configured by entering a part thereof.
  • the rolling element 4a is positioned by a cage 4d.
  • the ball bearing 4 disposed between the helical gear 2 and the support shaft 3 may be a double row ball bearing as shown in FIG.
  • the support stability of the helical gear 2 is superior to the single row ball bearing of FIG. 1 in the double row ball bearing of FIG.
  • the ball bearing 4 disposed between the helical gear 2 and the support shaft 3 may be an angular ball bearing as shown in FIG.
  • the support shaft 3 may be either a solid shaft as shown in FIG. 1 or a shaft provided with an oil supply hole 5 as shown in FIG.
  • the oil supply hole 5 has at least one first hole 5a provided in the shaft center portion with one end opened to the end surface of the support shaft 3, and extending radially from the first hole 5a to the outer periphery of the support shaft 3. The thing consisting of the 2nd hole 5b was illustrated.
  • the ball bearing 4 illustrated in FIGS. 1 to 3 is assembled in the following procedure. First, the support shaft 3 inserted through the shaft hole 2a of the helical gear 2 is biased from the shaft center portion, and in this state, the raceway surfaces 4b, 4c start from the location where the space entrance between the helical gear 2 and the support shaft 3 is wide open. A necessary number of rolling elements 4a are inserted between them.
  • each rolling element 4a is moved to a position that keeps a predetermined interval, and the support shaft 3 is arranged concentrically with the shaft hole 2a. Thereafter, a cage 4d is attached to position each rolling element 4a.
  • FIG. 5 and FIG. 7 show a planetary gear mechanism 10 using the above-described gear assembly (the gear assembly used here is the gear assembly of FIG. 2).
  • the planetary gear mechanism 10 in FIG. 5 constitutes a speed increaser, and includes a sun gear 11, a ring gear 12, a planetary gear 13, and a planetary carrier 14.
  • the sun gear 11 is attached to an output shaft (not shown).
  • the ring gear 12 is fixed to a fixing member, such as a motor case, and is concentrically disposed on the outer periphery of the sun gear 11.
  • a planetary gear 13 including a support shaft and a ball bearing is configured by the gear assembly 1 described above.
  • a plurality of the planetary gears 13 are arranged in a space between the sun gear 11 and the ring gear 12 so as to mesh with both the sun gear 11 and the ring gear 12.
  • two end plates 14 a and 14 b that support both ends of the support shaft 15 are connected to each other via the support shaft 3, but the end plates 14 a and 14 b do not interfere with the planetary gear 13. It may be connected via a bridge (not shown).
  • the planetary carrier 14 has an input shaft 16 integrally formed.
  • the input shaft 16 is obtained by connecting a separately machined shaft to the planetary carrier 14 by a method such as fastening with a bolt or welding. May be.
  • the planetary gear 13 meshed with the ring gear 12 revolves around the sun gear 11 while rotating, whereby the sun gear 11 meshed with the planetary gear 13 rotates and the output to which the sun gear 11 is attached is rotated.
  • the shaft rotates at an increased speed.
  • the arrow of FIG. 5 represents the transmission path
  • the arrow of FIG. 6 represents the rotation direction of each gear.
  • the planetary gear mechanism 10 in FIG. 7 constitutes a speed reducer, and has a sun gear 11, a ring gear 12, a planetary gear 13, and a planetary carrier 14 as in the case of the speed increaser.
  • the sun gear 11 is attached to an input shaft (not shown).
  • an output shaft 17 is formed integrally with the illustrated planetary carrier 14.
  • FIG. 9 shows a motor incorporating the planetary gear mechanism (speed increaser) 10 shown in FIG.
  • the gear mechanism built-in motor 20 is an electric motor 21 integrated with the planetary gear mechanism 10 described above.
  • the motor 21 has a motor case 22, a stator core 23, a rotor 24, and a rotating shaft (motor output shaft) 25.
  • the planetary gear mechanism 10 is disposed inside the motor case 22 and accelerates and outputs the rotation of the rotating shaft 25.
  • the rotary shaft 25 is an axis corresponding to the input shaft 16 in FIG. 5, which is a hollow shaft integrated with the planetary carrier 14.
  • the rotary shaft 25 is rotatably supported by a bearing 26 assembled to the motor case 22.
  • the ring gear 12 of the planetary gear mechanism 10 is fixed to the inner surface of the motor case 22.
  • the sun gear 11 is formed integrally with an output shaft 27 inserted into the planetary carrier 14 (the sun gear 11 may be an independent product as shown in FIG. 5 attached to the output shaft).
  • the output shaft 27 is rotatably supported by a bearing 28 assembled to the motor case 22.
  • the entrance of the space between the output shaft 27 and the motor case 22 is sealed with a seal member 29.
  • the gear mechanism built-in motor 20 in FIG. 9 is used in a continuously variable transmission (CVT) immediately after the engine is started in a vehicle having a rotational drive of an turbocharger (engine supercharger) turbine wheel and an idling stop function. It can be suitably used for an electric oil pump or the like provided for the purpose of securing the hydraulic pressure for clutch engagement.
  • CVT continuously variable transmission
  • FIG. 10 shows an electric motor incorporating the planetary gear mechanism (reduction gear) 10 of FIG.
  • the gear mechanism built-in motor 20 includes a motor case 22, a stator core 23, a rotor 24, a rotating shaft 25, and a planetary gear mechanism 10 that decelerates and outputs the rotation of the rotating shaft 25.
  • the sun gear 11 of the planetary gear mechanism 10 is integrally provided on the rotation shaft 25 (the sun gear 11 may be attached to the output shaft 25 as an independent product as shown in FIG. 7). Further, the planetary carrier 14 of the planetary gear mechanism 10 is integrally formed with a hollow output shaft 27 (this corresponds to the output shaft 17 in FIG. 7).
  • the gear mechanism built-in motor 20 in FIG. 10 is suitably used as a drive source for devices that require a driving force larger than the rotational torque generated by the motor because the force transmitted by the deceleration of the rotation is amplified. Can do.
  • the gear assembly of the present invention can be suitably used for a planetary gear of a planetary gear mechanism, but its application is not limited to a planetary gear.
  • the planetary gear mechanism of the present invention can be suitably used for a motor (for increasing or decreasing the rotation of a motor), but its application is not limited to a motor.

Abstract

This gear assembly is configured by combining a helical gear (2) that has a shaft hole (2a) and a spindle (3) that rotatably supports the helical gear (2), wherein: a ball bearing (4) is arranged between the helical gear (2) and the spindle (3); and the spindle (3) and the helical gear (2) respectively constitute the inner race and the outer race of the ball bearing (4). A planetary gear mechanism that uses the gear assembly and a motor that includes the planetary gear mechanism are provided.

Description

ギヤアセンブリとそれを用いた遊星歯車機構及び歯車機構内蔵モータGear assembly, planetary gear mechanism using the same, and motor with built-in gear mechanism
　この発明は、ヘリカルギヤ（はす歯歯車）とそれを回転可能に支持する支軸を組み合わせたギヤアセンブリと、それを用いた遊星歯車機構と、その遊星歯車機構を内蔵したモータに関する。 The present invention relates to a gear assembly combining a helical gear (helical gear) and a support shaft that rotatably supports the gear assembly, a planetary gear mechanism using the gear assembly, and a motor incorporating the planetary gear mechanism.
　減速機や増速機に組み込まれる遊星歯車装置には、サンギヤとリングギヤの両者に噛み合うプラネタリギヤが複数個組み込まれている。 A planetary gear unit incorporated in a reduction gear or a speed increaser incorporates a plurality of planetary gears that mesh with both a sun gear and a ring gear.
　そのプラネタリギヤは、ヘリカルギヤで構成されたものが一般的である。そのプラネタリギヤの従来品は、軸穴を設けたヘリカルギヤを軸穴に挿通される支軸で直接回転可能に支えるか、又は、支軸との間に軸受を介在してニードルベアリングや玉軸受で回転可能に支持している。玉軸受による支持は、例えば、下記特許文献２に示されている。また、ニードルベアリングは、下記特許文献３に示されている。 The planetary gear is generally composed of a helical gear. In the conventional planetary gear, a helical gear with a shaft hole is rotatably supported by a support shaft inserted through the shaft hole, or a needle bearing or ball bearing is used with a bearing interposed between the shaft and the support shaft. I support it as possible. The support by a ball bearing is shown by the following patent document 2, for example. Moreover, the needle bearing is shown by the following patent document 3. FIG.
　そして、こうして形成されたギヤアセンブリを、プラネタリキャリアに組み付けている。このとき、プラネタリギヤの両側部とプラネタリキャリアとの間には、スラストニードルベアリングやスラストプレートなどを介装している。（下記特許文献１参照。） And the gear assembly thus formed is assembled to the planetary carrier. At this time, a thrust needle bearing, a thrust plate, or the like is interposed between both side portions of the planetary gear and the planetary carrier. (See Patent Document 1 below.)
　その特許文献１には、ピニオンギヤ（ヘリカルギヤで構成されたプラネタリギヤ）を、プラネタリキャリアに固定されたピン（支軸）との間に介装されたニードルベアリングで回転可能に支持し、そのピニオンギヤの端面とプラネタリキャリアとの間にスラストワッシャ（これは一種のスラストプレート）を介装した歯車構造が記載されている。 In Patent Document 1, a pinion gear (planetary gear constituted by a helical gear) is rotatably supported by a needle bearing interposed between a pin (support shaft) fixed to a planetary carrier, and an end face of the pinion gear A gear structure is described in which a thrust washer (this is a kind of thrust plate) is interposed between the carrier and the planetary carrier.
　ヘリカルギヤを採用したプラネタリギヤについては、回転時にスラスト荷重が発生する。そのスラスト荷重は、増速機に設けられる遊星歯車装置では特に、プラネタリギヤが高速回転するので無視できないものになる。 プ ラ For planetary gears that use helical gears, a thrust load is generated during rotation. The thrust load is not negligible particularly in the planetary gear device provided in the speed increaser because the planetary gear rotates at a high speed.
　そのために、スラストニードルベアリングやスラストプレートを設けてスラスト荷重を受け止めている。支軸とプラネタリギヤとの間に介装する軸受がスラスト荷重に対応できないニードルベアリングである場合には、スラストニードルベアリングやスラストプレートが必須である。 Therefore, a thrust needle bearing and a thrust plate are provided to receive the thrust load. In the case where the bearing interposed between the support shaft and the planetary gear is a needle bearing that cannot cope with the thrust load, a thrust needle bearing or a thrust plate is essential.
　一方、前記軸受が玉軸受であるものは、あまり大きくないスラスト荷重であれば、スラストニードルベアリングやスラストプレート無しで受け止めることが可能である。しかしながら、専用のインナーレースとアウターレースを備える一般的な玉軸受を使用したプラネタリギヤは、下記の問題を生起させる。 On the other hand, if the bearing is a ball bearing, it can be received without a thrust needle bearing or thrust plate if the thrust load is not very large. However, a planetary gear using a general ball bearing having a dedicated inner race and outer race causes the following problems.
　前述したプラネタリギヤにはヘリカルギヤが用いられるので、内径の軸受には、ギヤからの、接線力、半径方向力、ギヤのねじり角による軸方向力が作用する。 Since a helical gear is used for the planetary gear described above, a tangential force, radial force, and axial force from the gear torsion angle are applied to the inner diameter bearing.
　この軸方向力は、軸受にはモーメント力として作用するため、内径部に位置する転動体が針状ころの場合傾くことになる。 Since this axial force acts as a moment force on the bearing, it is inclined when the rolling element located at the inner diameter portion is a needle roller.
　この傾きにより、針状ころ端部の面圧が非常に高くなり、ラジアル荷重だけの場合よりも計算寿命が３０％以下にまで低下すると言われている。 ) It is said that due to this inclination, the surface pressure at the end of the needle roller becomes very high, and the calculated life is reduced to 30% or less than the case of only radial load.
特開２００７－１５４９１１号公報JP 2007-154911 A 特開２０１２－１８９２０２号公報JP 2012-189202 A 特開２００５－３２５９６５号公報JP 2005-325965 A
　プラネタリギヤを支軸で直接支える構造は、スラスト方向の負荷が加わらない歯車機構や、ラジアル荷重が軽荷重の歯車機構には利用できるが、スラスト荷重が加わる歯車機構では、高回転使用での寿命確保が難しい。 The structure that directly supports the planetary gear with the support shaft can be used for gear mechanisms that do not receive a load in the thrust direction and gear mechanisms that use a light radial load. Is difficult.
　また、上述したように、プラネタリギヤの両端部に、スラストニードルベアリングやスラストプレートを設置する歯車装置は、組み立て工数の増加による組み立て性の悪化が避けられない。これに加え、スラストプレートを用いるものは、摩擦によるギヤ回転の負荷増も招く。 Also, as described above, a gear device in which thrust needle bearings and thrust plates are installed at both ends of the planetary gear inevitably deteriorates assembling due to an increase in the number of assembling steps. In addition, the use of a thrust plate also causes an increase in gear rotation load due to friction.
　また、スラストニードルベアリングやスラストプレートの設置によって遊星歯車機構の軸方向寸法が大きくなり、遊星歯車機構を有する各種機器・装置の小型化の要求にも応え辛い。 Also, the installation of thrust needle bearings and thrust plates increases the axial dimension of the planetary gear mechanism, making it difficult to meet the demands for miniaturization of various equipment and devices having planetary gear mechanisms.
　プラネタリギヤと支軸の間に一般的な玉軸受を介装する前記特許文献２に記載のプラネタリギヤは、玉軸受の使用によって径方向の寸法が大きくなる。従って、この構造のプラネタリギヤを採用した遊星歯車機構を有する各種機器・装置も、小型化の要求に応え辛い。 The planetary gear described in Patent Document 2 in which a general ball bearing is interposed between the planetary gear and the support shaft has a larger radial dimension due to the use of the ball bearing. Therefore, various devices and apparatuses having a planetary gear mechanism that employs a planetary gear of this structure are also difficult to meet the demand for downsizing.
　この発明は、上記の現状技術に鑑みてなされたものであって、その課題は、スラスト荷重を受け止める機能を備えたヘリカルギヤ使用のギヤアセンブリと、そのギヤアセンブリを用いた遊星歯車機構と、その遊星歯車機構を内蔵したモータを実現して提供することである。 The present invention has been made in view of the above state of the art, and the problem is that a gear assembly using a helical gear having a function of receiving a thrust load, a planetary gear mechanism using the gear assembly, and a planetary gear thereof. It is to realize and provide a motor with a built-in gear mechanism.
　上記の課題を解決するため、この発明においては、軸穴を有するヘリカルギヤと、前記軸穴に通されて前記ヘリカルギヤを回転可能に支持する支軸を組み合わせたギヤアセンブリであって、前記ヘリカルギヤと支軸との間に玉軸受が配置され、前記玉軸受のインナーレースが前記支軸によって、アウターレースが前記ヘリカルギヤによってそれぞれ構成されたギヤアセンブリを提供する。 In order to solve the above-described problems, the present invention provides a gear assembly that combines a helical gear having a shaft hole and a support shaft that is passed through the shaft hole and rotatably supports the helical gear. Provided is a gear assembly in which a ball bearing is disposed between a shaft, an inner race of the ball bearing is constituted by the support shaft, and an outer race is constituted by the helical gear.
　また、このギヤアセンブリで構成される支軸と玉軸受の含まれたプラネタリギヤと、このプラネタリギヤを組み付けたプラネタリキャリアと、前記プラネタリギヤがそれぞれ噛合するサンギヤ及びリングギヤを備えた遊星歯車機構も同時に提供する。さらに、下記（１）、（２）の歯車機構内蔵モータも併せて提供する。 Also provided is a planetary gear mechanism including a planetary gear including a support shaft and a ball bearing constituted by the gear assembly, a planetary carrier assembled with the planetary gear, and a sun gear and a ring gear that mesh with the planetary gear, respectively. Further, the following gear mechanism built-in motors (1) and (2) are also provided.
（１）前記遊星歯車機構と、モータケース、ステータコア、ロータ及び出力軸となる回転軸を備えた電動式のモータを組み合わせ、前記遊星歯車機構を、モータのケーシングに内蔵し、前記回転軸を前記遊星歯車機構のプラネタリキャリアに連結した歯車機構内蔵モータ。 (1) The planetary gear mechanism is combined with an electric motor including a motor case, a stator core, a rotor, and a rotary shaft that serves as an output shaft, the planetary gear mechanism is built in a casing of the motor, and the rotary shaft is Gear mechanism built-in motor connected to planetary carrier of planetary gear mechanism.
（２）前記遊星歯車機構と、モータケース、ステータコア、ロータ及び出力軸となる回転軸を備えた電動式のモータを組み合わせ、前記遊星歯車機構をモータのケーシングに内蔵し、前記回転軸を前記遊星歯車機構のサンギヤに連結した歯車機構内蔵モータ。 (2) The planetary gear mechanism is combined with an electric motor having a motor case, a stator core, a rotor, and a rotary shaft that is an output shaft, the planetary gear mechanism is built in a casing of the motor, and the rotary shaft is connected to the planetary gear. Gear mechanism built-in motor connected to the sun gear of the gear mechanism.
　出力軸を遊星歯車機構のプラネタリキャリアに連結した歯車機構内蔵モータは、前記遊星歯車機構が増速機として働く。 In the gear mechanism built-in motor in which the output shaft is connected to the planetary carrier of the planetary gear mechanism, the planetary gear mechanism functions as a speed increaser.
　また、出力軸を遊星歯車機構のサンギヤに連結した歯車機構内蔵モータは、前記遊星歯車機構が減速機として働く。 Also, in the gear mechanism built-in motor in which the output shaft is connected to the sun gear of the planetary gear mechanism, the planetary gear mechanism functions as a speed reducer.
　この発明のギヤアセンブリは、以下に列挙する形態のものが考えられる。
１）ヘリカルギヤと支軸との間に単列玉軸受を配置したもの。
２）ヘリカルギヤと支軸との間に複列玉軸受を配置したもの。
３）ヘリカルギヤと支軸との間にアンギュラ玉軸受を配置したもの。
４）前記支軸が中実の軸であるもの。
５）前記支軸が、一端を支軸の端面に開放させて軸心部に設けた第１の孔と、その第１の孔から放射状に延びて支軸の外周に抜ける少なくとも１つの第２の孔とで構成される給油孔を備えたもの。
６）遊星歯車機構のプラネタリギヤとして構成されたもの。 The gear assembly according to the present invention may have the forms listed below.
1) A single row ball bearing is disposed between the helical gear and the support shaft.
2) A double row ball bearing is arranged between the helical gear and the support shaft.
3) An angular ball bearing is arranged between the helical gear and the support shaft.
4) The support shaft is a solid shaft.
5) The support shaft has a first hole provided in the shaft center portion with one end opened to the end surface of the support shaft, and at least one second extending radially from the first hole and exiting to the outer periphery of the support shaft. With oil supply holes composed of holes.
6) A planetary gear for a planetary gear mechanism.
　この発明の遊星歯車機構は、プラネタリギヤを構成するギヤアセンブリの支軸を、プラネタリキャリアに加締めて固定することができる。 In the planetary gear mechanism of the present invention, the support shaft of the gear assembly that constitutes the planetary gear can be fixed by caulking the planetary carrier.
　この発明のギヤアセンブリは、前記ヘリカルギヤと支軸が玉軸受のアウターレースとインナーレースを構成している。具体的には、支軸とヘリカルギヤの各々が、断面円弧状の環状溝によって構成された軌道面を対応した位置に有しており、その軌道面を構成する環状溝に転動体（ボール）の一部が入り込んで玉軸受が構成されている。 In the gear assembly of the present invention, the helical gear and the support shaft constitute an outer race and an inner race of ball bearings. Specifically, each of the support shaft and the helical gear has a raceway surface formed by an annular groove having an arcuate cross section at a corresponding position, and a rolling element (ball) is placed in the annular groove constituting the raceway surface. Part of the ball bearing is formed.
　そのため、転動体の軸方向移動が前記環状溝によって阻止され、これにより、スラスト荷重の受け止めがなされる。 Therefore, the axial movement of the rolling elements is blocked by the annular groove, thereby receiving the thrust load.
　従って、スラストニードルベアリングやスラストプレート無しで使用することができ、このギヤアセンブリを設置する歯車装置の組み立て工数の低減、組み立て性の向上、ギヤ回転の負荷軽減が可能になる。 Therefore, it can be used without a thrust needle bearing or a thrust plate, and it is possible to reduce the number of assembling steps of the gear device in which this gear assembly is installed, improve the assembling ability, and reduce the load of the gear rotation.
　また、ヘリカルギヤと支軸との間に玉軸受が介装されているので、高回転使用での寿命向上も図れる。 Also, since a ball bearing is interposed between the helical gear and the support shaft, it is possible to improve the service life at high rotation.
　玉軸受は、玉（鋼球）を使用しており、モーメント荷重によるエッジロードが発生しないため、計算寿命の変化率（低下率）も少なくなると思われる。 玉 Ball bearings use balls (steel balls), and edge load due to moment load does not occur, so the change rate (decrease rate) in the calculated life is expected to be small.
　このほか、スラストニードルベアリングやスラストプレートが不要なため、歯車装置の軸方向寸法が短縮され、遊星歯車機構を有する各種機器・装置の小型化も可能になる。 In addition, since a thrust needle bearing and a thrust plate are not required, the axial dimension of the gear device is shortened, and various devices and devices having a planetary gear mechanism can be miniaturized.
　支軸とヘリカルギヤが玉軸受のインナーレースとアウターレースを兼用した構造になっているので、支軸とヘリカルギヤとの間に、専用のインナーレースとアウターレースを有する玉軸受を介装する遊星歯車機構と比較すると径方向寸法が縮小され、この場合も、遊星歯車機構を有する各種機器・装置の小型化に繋がる。 Since the support shaft and the helical gear have a structure that combines the inner race and outer race of the ball bearing, a planetary gear mechanism that interposes a ball bearing having a dedicated inner race and outer race between the support shaft and the helical gear. Compared with the above, the radial dimension is reduced, and this also leads to miniaturization of various devices and apparatuses having a planetary gear mechanism.
　なお、ヘリカルギヤと支軸との間に複列玉軸受を配置したギヤアセンブリは、ヘリカルギヤの支持安定性に優れる。 Note that a gear assembly in which a double-row ball bearing is arranged between the helical gear and the support shaft is excellent in supporting stability of the helical gear.
　また、支軸の内部に給油孔を備えたギヤアセンブリは、潤滑油を供給して玉軸受の寿命を向上させることができる。 Also, a gear assembly having an oil supply hole inside the support shaft can supply lubricating oil to improve the life of the ball bearing.
　さらに、支軸を加締め固定によってプラネタリキャリアに取り付けた遊星歯車機構は、支軸固定のためのナットなどが不要である。これにより、部品数を削減でき、軸方向寸法の更なる短縮も図れる。 Furthermore, the planetary gear mechanism in which the support shaft is fixed to the planetary carrier by caulking and fixing does not require a nut for fixing the support shaft. Thereby, the number of parts can be reduced, and the axial dimension can be further shortened.
この発明のギヤアセンブリの一例を示す断面図である。It is sectional drawing which shows an example of the gear assembly of this invention. この発明のギヤアセンブリの他の例を示す断面図である。It is sectional drawing which shows the other example of the gear assembly of this invention. この発明のギヤアセンブリのさらに他の例を示す断面図である。It is sectional drawing which shows the further another example of the gear assembly of this invention. この発明のギヤアセンブリの一例を示す斜視図である。It is a perspective view which shows an example of the gear assembly of this invention. この発明のギヤアセンブリを用いた遊星歯車機構（増速機）の一例を示す断面図である。It is sectional drawing which shows an example of the planetary gear mechanism (speed increaser) using the gear assembly of this invention. 図５のＸ－Ｘに沿った断面図である。FIG. 6 is a cross-sectional view taken along the line XX in FIG. 5. この発明のギヤアセンブリを用いた遊星歯車機構（減速機）の一例を示す断面図である。It is sectional drawing which shows an example of the planetary gear mechanism (reduction gear) using the gear assembly of this invention. 図７のＹ－Ｙに沿った断面図である。FIG. 8 is a cross-sectional view taken along YY in FIG. 7. 図５の増速機を内蔵したモータの一例を示す断面図である。It is sectional drawing which shows an example of the motor which incorporated the speed up gear of FIG. 図７の減速機を内蔵したモータの一例を示す断面図である。It is sectional drawing which shows an example of the motor which incorporated the reduction gear of FIG.
　以下、この発明のギヤアセンブリと、そのギヤアセンブリを用いた遊星歯車機構と、その遊星歯車機構を内蔵したモータの実施の形態を、添付図面の図１～図１０に基づいて説明する。 Hereinafter, embodiments of a gear assembly of the present invention, a planetary gear mechanism using the gear assembly, and a motor incorporating the planetary gear mechanism will be described with reference to FIGS. 1 to 10 of the accompanying drawings.
　図１～図４は、ギヤアセンブリの実施形態を現したものである。図１のギヤアセンブリ１は、ヘリカルギヤ２と、支軸３と、玉軸受４を組み合わせて構成されている。 1 to 4 show an embodiment of a gear assembly. A gear assembly 1 in FIG. 1 is configured by combining a helical gear 2, a support shaft 3, and a ball bearing 4.
　ヘリカルギヤ２は、円筒状の軸穴２ａを有しており、その軸穴２ａに支軸３が挿通されている。 The helical gear 2 has a cylindrical shaft hole 2a, and a support shaft 3 is inserted through the shaft hole 2a.
　玉軸受４は、ヘリカルギヤ２と支軸３との間に配置され、この玉軸受４の転動体（ボール）４ａを介してヘリカルギヤ２が支軸３に回転可能に支持されている。 The ball bearing 4 is disposed between the helical gear 2 and the support shaft 3, and the helical gear 2 is rotatably supported on the support shaft 3 via rolling elements (balls) 4 a of the ball bearing 4.
　玉軸受４は、インナーレースが支軸３によって構成され、さらに、アウターレースがヘリカルギヤ２によって構成されている。 The ball bearing 4 has an inner race constituted by the support shaft 3 and an outer race constituted by the helical gear 2.
　ヘリカルギヤ２と支軸３の各々は、断面円弧状の環状溝によって構成される軌道面４ｂ、４ｃを対応した位置に有しており、その軌道面４ｂ、４ｃを構成する環状溝に転動体４ａの一部が入り込んで玉軸受４が構成されている。転動体４ａは、保持器４ｄによって位置決めがなされている。 Each of the helical gear 2 and the support shaft 3 has raceway surfaces 4b and 4c constituted by annular grooves having an arcuate cross section at corresponding positions, and the rolling elements 4a are arranged in the annular grooves constituting the raceway surfaces 4b and 4c. The ball bearing 4 is configured by entering a part thereof. The rolling element 4a is positioned by a cage 4d.
　ヘリカルギヤ２と支軸３との間に配置する玉軸受４は、図２に示すような、複列玉軸受であってもよい。ヘリカルギヤ２の支持安定性は、図１の単列玉軸受けよりも図２の複列玉軸受の方が優れる。 The ball bearing 4 disposed between the helical gear 2 and the support shaft 3 may be a double row ball bearing as shown in FIG. The support stability of the helical gear 2 is superior to the single row ball bearing of FIG. 1 in the double row ball bearing of FIG.
　ヘリカルギヤ２と支軸３との間に配置する玉軸受４は、図３に示すような、アンギュラ玉軸受であってもよい。 The ball bearing 4 disposed between the helical gear 2 and the support shaft 3 may be an angular ball bearing as shown in FIG.
　支軸３は、図１に示すような中実の軸、内部に図２に示すような給油孔５を備える軸のどちらであってもよい。給油孔５は、一端を支軸３の端面に開放させて軸心部に設けた第１の孔５ａと、その第１の孔５ａから放射状に延びて支軸３の外周に抜ける少なくとも１つの第２の孔５ｂとからなるものを例示した。 The support shaft 3 may be either a solid shaft as shown in FIG. 1 or a shaft provided with an oil supply hole 5 as shown in FIG. The oil supply hole 5 has at least one first hole 5a provided in the shaft center portion with one end opened to the end surface of the support shaft 3, and extending radially from the first hole 5a to the outer periphery of the support shaft 3. The thing consisting of the 2nd hole 5b was illustrated.
　図１～図３に例示した玉軸受４は、以下の手順で組み付けられている。
　まず、ヘリカルギヤ２の軸穴２ａに挿通した支軸３を軸心部から偏らせ、この状態で、ヘリカルギヤ２と支軸３との間の空間の入口が大きく開いた箇所から軌道面４ｂ、４ｃ間に必要個数の転動体４ａを挿入する。 The ball bearing 4 illustrated in FIGS. 1 to 3 is assembled in the following procedure.
First, the support shaft 3 inserted through the shaft hole 2a of the helical gear 2 is biased from the shaft center portion, and in this state, the raceway surfaces 4b, 4c start from the location where the space entrance between the helical gear 2 and the support shaft 3 is wide open. A necessary number of rolling elements 4a are inserted between them.
　そして、各転動体４ａを所定の間隔を保つ位置に移動させて支軸３を軸穴２ａと同心位置に配置し、その後、保持器４ｄを取り付けて各転動体４ａを位置決めする。 Then, each rolling element 4a is moved to a position that keeps a predetermined interval, and the support shaft 3 is arranged concentrically with the shaft hole 2a. Thereafter, a cage 4d is attached to position each rolling element 4a.
　以上の手順を経ると、ヘリカルギヤ２と、支軸３と、玉軸受４が一体化された図４に示すような外観を有するギヤアセンブリ１が完成する。 After the above procedure, the gear assembly 1 having an appearance as shown in FIG. 4 in which the helical gear 2, the support shaft 3, and the ball bearing 4 are integrated is completed.
　上述したギヤアセンブリ（ここで用いたものは図２のギヤアセンブリ）１を用いた遊星歯車機構１０を図５及び図７に示す。 FIG. 5 and FIG. 7 show a planetary gear mechanism 10 using the above-described gear assembly (the gear assembly used here is the gear assembly of FIG. 2).
　図５の遊星歯車機構１０は、増速機を構成するものであって、サンギヤ１１、リングギヤ１２、プラネタリギヤ１３及びプラネタリキャリア１４を有する。 The planetary gear mechanism 10 in FIG. 5 constitutes a speed increaser, and includes a sun gear 11, a ring gear 12, a planetary gear 13, and a planetary carrier 14.
　サンギヤ１１は、出力軸（図示せず）に取り付けられる。リングギヤ１２は、固定部材、例えばモータケースなどに固定されてサンギヤ１１の外周に同心的に配置される。 The sun gear 11 is attached to an output shaft (not shown). The ring gear 12 is fixed to a fixing member, such as a motor case, and is concentrically disposed on the outer periphery of the sun gear 11.
　遊星歯車機構１０においては、既述のギヤアセンブリ１によって支軸と玉軸受を備えたプラネタリギヤ１３が構成されている。 In the planetary gear mechanism 10, a planetary gear 13 including a support shaft and a ball bearing is configured by the gear assembly 1 described above.
　そのプラネタリギヤ１３は、サンギヤ１１とリングギヤ１２の両者に噛合させてサンギヤ１１とリングギヤ１２との間の空間に複数個配置される。 A plurality of the planetary gears 13 are arranged in a space between the sun gear 11 and the ring gear 12 so as to mesh with both the sun gear 11 and the ring gear 12.
　このプラネタリギヤ１３に一体化された支軸１５（＝ギヤアセンブリの支軸３）は、両端がプラネタリキャリア１４に加締め固定されている。 The both ends of the support shaft 15 (= support shaft 3 of the gear assembly) integrated with the planetary gear 13 are fixed to the planetary carrier 14 by caulking.
　図示のプラネタリキャリア１４は、支軸１５の両端を支持する２枚の端板１４ａ、１４ｂが、支軸３を介して互いに連結されているが、端板１４ａ、１４ｂがプラネタリギヤ１３と干渉しない位置に配置されるブリッジ（図示せず）を介して連結されたものであってもよい。 In the illustrated planetary carrier 14, two end plates 14 a and 14 b that support both ends of the support shaft 15 are connected to each other via the support shaft 3, but the end plates 14 a and 14 b do not interfere with the planetary gear 13. It may be connected via a bridge (not shown).
　また、プラネタリキャリア１４には、入力軸１６が一体に形成されているが、入力軸１６は、別加工された軸をプラネタリキャリア１４にボルトでの締結や溶接などの方法で連結したものであってもよい。 The planetary carrier 14 has an input shaft 16 integrally formed. The input shaft 16 is obtained by connecting a separately machined shaft to the planetary carrier 14 by a method such as fastening with a bolt or welding. May be.
　このように構成された図５の遊星歯車機構１０は、図６に示すように、入力軸１６の回転がプラネタリキャリア１４に伝わってプラネタリキャリア１４が回転する。 In the planetary gear mechanism 10 of FIG. 5 configured as described above, the rotation of the input shaft 16 is transmitted to the planetary carrier 14 and the planetary carrier 14 rotates as shown in FIG.
　その回転により、リングギヤが固定された場合、リングギヤ１２に噛み合ったプラネタリギヤ１３が自転しながらサンギヤ１１の周囲を公転し、これにより、プラネタリギヤ１３に噛み合ったサンギヤ１１が回転し、サンギヤ１１を取り付けた出力軸が増速された速度で回転する。
　なお、図５の矢印は、回転の伝達経路を、図６の矢印は各ギヤの回転方向を表す。 When the ring gear is fixed by the rotation, the planetary gear 13 meshed with the ring gear 12 revolves around the sun gear 11 while rotating, whereby the sun gear 11 meshed with the planetary gear 13 rotates and the output to which the sun gear 11 is attached is rotated. The shaft rotates at an increased speed.
In addition, the arrow of FIG. 5 represents the transmission path | route of rotation, and the arrow of FIG. 6 represents the rotation direction of each gear.
　図７の遊星歯車機構１０は、減速機を構成するものであって、増速機と同様に、サンギヤ１１、リングギヤ１２、プラネタリギヤ１３及びプラネタリキャリア１４を有する。 The planetary gear mechanism 10 in FIG. 7 constitutes a speed reducer, and has a sun gear 11, a ring gear 12, a planetary gear 13, and a planetary carrier 14 as in the case of the speed increaser.
　サンギヤ１１は、入力軸（図示せず）に取り付けられる。また、図示のプラネタリキャリア１４には、出力軸１７が一体に形成されている。この２点が図５の増速機と相違し、その他の構成は図５の増速機と同じである。従って、図５と同一要素については、同一符号を付して説明を省く。 The sun gear 11 is attached to an input shaft (not shown). In addition, an output shaft 17 is formed integrally with the illustrated planetary carrier 14. These two points are different from the gearbox of FIG. 5, and other configurations are the same as those of the gearbox of FIG. Therefore, the same elements as those in FIG.
　図７の遊星歯車機構１０は、図８に示すように、サンギヤ１１の回転がプラネタリギヤ１３に伝わってプラネタリギヤ１３が回転する。 7, as shown in FIG. 8, the rotation of the sun gear 11 is transmitted to the planetary gear 13 and the planetary gear 13 rotates.
　その回転により、リングギヤが固定された場合、プラネタリギヤ１３は、リングギヤ１２の内歯に沿って転がり、これにより、プラネタリキャリア１４が回転し、プラネタリキャリア１４に連なった出力軸１７が減速された速度で回転する。
　なお、図７の矢印は、回転の伝達経路を、図８の矢印は各ギヤの回転方向を表す。 When the ring gear is fixed by the rotation, the planetary gear 13 rolls along the inner teeth of the ring gear 12, whereby the planetary carrier 14 rotates and the output shaft 17 connected to the planetary carrier 14 is decelerated at a reduced speed. Rotate.
In addition, the arrow of FIG. 7 represents the rotation transmission path | route, and the arrow of FIG. 8 represents the rotation direction of each gear.
　図５の遊星歯車機構（増速機）１０を内蔵したモータを図９に示す。この歯車機構内蔵モータ２０は、電動式のモータ２１と、既述の遊星歯車機構１０を一体化したものである。 FIG. 9 shows a motor incorporating the planetary gear mechanism (speed increaser) 10 shown in FIG. The gear mechanism built-in motor 20 is an electric motor 21 integrated with the planetary gear mechanism 10 described above.
　モータ２１は、モータケース２２、ステータコア２３、ロータ２４及び回転軸（モータの出力軸）２５を有する。 The motor 21 has a motor case 22, a stator core 23, a rotor 24, and a rotating shaft (motor output shaft) 25.
　遊星歯車機構１０は、モータケース２２の内部に配置されており、回転軸２５の回転を増速して出力する。 The planetary gear mechanism 10 is disposed inside the motor case 22 and accelerates and outputs the rotation of the rotating shaft 25.
　回転軸２５は、図５の入力軸１６に相当する軸であって、図のそれはプラネタリキャリア１４と一体の中空軸になっている。この回転軸２５は、モータケース２２に組み付けた軸受２６によって回転可能に支持されている。 The rotary shaft 25 is an axis corresponding to the input shaft 16 in FIG. 5, which is a hollow shaft integrated with the planetary carrier 14. The rotary shaft 25 is rotatably supported by a bearing 26 assembled to the motor case 22.
　遊星歯車機構１０のリングギヤ１２は、モータケース２２の内面に固定されている。また、サンギヤ１１は、プラネタリキャリア１４の内部に挿入した出力軸２７に一体に形成されている（サンギヤ１１は、図５に示したような独立品が出力軸に取り付けられていてもよい）。 The ring gear 12 of the planetary gear mechanism 10 is fixed to the inner surface of the motor case 22. The sun gear 11 is formed integrally with an output shaft 27 inserted into the planetary carrier 14 (the sun gear 11 may be an independent product as shown in FIG. 5 attached to the output shaft).
　出力軸２７は、モータケース２２に組み付けた軸受２８によって回転可能に支持されている。また、出力軸２７とモータケース２２との間の空間の入口はシール部材２９によって封止されている。 The output shaft 27 is rotatably supported by a bearing 28 assembled to the motor case 22. The entrance of the space between the output shaft 27 and the motor case 22 is sealed with a seal member 29.
　この図９の歯車機構内蔵モータ２０は、ターボチャージャ（エンジン用過給機）のタービン翼車の回転駆動や、アイドリングストップ機能を有する車両に、エンジンの始動直後における無段変速機（ＣＶＴ）のクラッチ係合用の油圧を確保する目的で設けられる電動オイルポンプなどに好適に利用することができる。 The gear mechanism built-in motor 20 in FIG. 9 is used in a continuously variable transmission (CVT) immediately after the engine is started in a vehicle having a rotational drive of an turbocharger (engine supercharger) turbine wheel and an idling stop function. It can be suitably used for an electric oil pump or the like provided for the purpose of securing the hydraulic pressure for clutch engagement.
　ターボチャージャやクラッチ係合用の油圧を発生させるオイルポンプなどは、応答性に優れることが要求される。これ等の機器を、回転の立ち上がりが早いモータで駆動することで応答性の改善を図ることが可能になる。 ∙ Turbochargers and oil pumps that generate hydraulic pressure for clutch engagement are required to have excellent responsiveness. It is possible to improve responsiveness by driving these devices with a motor having a fast rise in rotation.
　図７の遊星歯車機構（減速機）１０を内蔵した電動式のモータを図１０に示す。この歯車機構内蔵モータ２０は、モータケース２２、ステータコア２３、ロータ２４、回転軸２５及び回転軸２５の回転を減速して出力する遊星歯車機構１０を有する。 FIG. 10 shows an electric motor incorporating the planetary gear mechanism (reduction gear) 10 of FIG. The gear mechanism built-in motor 20 includes a motor case 22, a stator core 23, a rotor 24, a rotating shaft 25, and a planetary gear mechanism 10 that decelerates and outputs the rotation of the rotating shaft 25.
　回転軸２５には、遊星歯車機構１０のサンギヤ１１が一体に設けられている（サンギヤ１１は、図７に示したような独立品が出力軸２５に取り付けられていてもよい）。また、遊星歯車機構１０のプラネタリキャリア１４には、中空の出力軸２７（これは図７の出力軸１７に相当する）が一体に形成されている。 The sun gear 11 of the planetary gear mechanism 10 is integrally provided on the rotation shaft 25 (the sun gear 11 may be attached to the output shaft 25 as an independent product as shown in FIG. 7). Further, the planetary carrier 14 of the planetary gear mechanism 10 is integrally formed with a hollow output shaft 27 (this corresponds to the output shaft 17 in FIG. 7).
　その他の構成は、図９の歯車機構内蔵モータ２０と同じであるので、同一要素に同一符号を付して説明を省く。 Other configurations are the same as those of the gear mechanism built-in motor 20 of FIG. 9, and therefore, the same components are denoted by the same reference numerals and description thereof is omitted.
　図１０の歯車機構内蔵モータ２０は、回転の減速により伝達される力が増幅されるので、モータが発生させる回転トルクよりも大きな駆動力を必要とする機器類の駆動源として好適に利用することができる。 The gear mechanism built-in motor 20 in FIG. 10 is suitably used as a drive source for devices that require a driving force larger than the rotational torque generated by the motor because the force transmitted by the deceleration of the rotation is amplified. Can do.
　上記の応用例からわかるように、この発明のギヤアセンブリは、遊星歯車機構のプラネタリギヤ用として好適に利用できるが、その用途はプラネタリギヤに限定されない。 As can be seen from the above application example, the gear assembly of the present invention can be suitably used for a planetary gear of a planetary gear mechanism, but its application is not limited to a planetary gear.
　また、この発明の遊星歯車機構は、モータ用（モータの回転の増速用或いは減速用）として好適に利用できるが、その用途はモータ用に限定されない。 The planetary gear mechanism of the present invention can be suitably used for a motor (for increasing or decreasing the rotation of a motor), but its application is not limited to a motor.
１　　　　　ギヤアセンブリ
２　　　　　ヘリカルギヤ
２ａ　　　　軸穴
３　　　　　支軸
４　　　　　玉軸受
４ａ　　　　転動体
４ｂ、４ｃ　軌道面
４ｄ　　　　保持器
５　　　　　給油孔
５ａ　　　　第１の孔
５ｂ　　　　第２の孔
１０　　　　遊星歯車機構
１１　　　　サンギヤ
１２　　　　リングギヤ
１３　　　　プラネタリギヤ
１４　　　　プラネタリキャリア
１４ａ、１４ｂ　端板
１５　　　　支軸
１６　　　　入力軸
１７　　　　出力軸
２０　　　　歯車機構内蔵モータ
２１　　　　モータ
２２　　　　モータケース
２３　　　　ステータコア
２４　　　　ロータ
２５　　　　回転軸
２６，２８　軸受
２７　　　　出力軸
２９　　　　シール部材 DESCRIPTION OF SYMBOLS 1 Gear assembly 2 Helical gear 2a Shaft hole 3 Support shaft 4 Ball bearing 4a Rolling element 4b, 4c Raceway surface 4d Cage 5 Oil supply hole 5a First hole 5b Second hole 10 Planetary gear mechanism 11 Sun gear 12 Ring gear 13 Planetary gear 14 Planetary Carriers 14a and 14b End plate 15 Support shaft 16 Input shaft 17 Output shaft 20 Gear mechanism built-in motor 21 Motor 22 Motor case 23 Stator core 24 Rotor 25 Rotating shafts 26 and 28 Bearing 27 Output shaft 29 Seal member

Claims (8)

  1. 　軸穴（２ａ）を有するヘリカルギヤ（２）と、前記軸穴（２ａ）に通されて前記ヘリカルギヤ（２）を回転可能に支持する支軸（３）を組み合わせたギヤアセンブリであって、前記ヘリカルギヤ（２）と支軸（３）との間に玉軸受（４）が配置され、前記玉軸受のインナーレースが前記支軸（３）によって、アウターレースが前記ヘリカルギヤ（２）によってそれぞれ構成されたギヤアセンブリ。 A gear assembly in which a helical gear (2) having a shaft hole (2a) and a support shaft (3) that is passed through the shaft hole (2a) and rotatably supports the helical gear (2) are combined. A ball bearing (4) is disposed between (2) and the support shaft (3), and the inner race of the ball bearing is configured by the support shaft (3) and the outer race is configured by the helical gear (2). Gear assembly.
  2. 　前記玉軸受（４）が、単列玉軸受である請求項１に記載のギヤアセンブリ。 The gear assembly according to claim 1, wherein the ball bearing (4) is a single row ball bearing.
  3. 　前記玉軸受（４）が、複列玉軸受である請求項１に記載のギヤアセンブリ。 The gear assembly according to claim 1, wherein the ball bearing (4) is a double row ball bearing.
  4. 　前記玉軸受（４）が、アンギュラ玉軸受である請求項１に記載のギヤアセンブリ。 The gear assembly according to claim 1, wherein the ball bearing (4) is an angular ball bearing.
  5. 　前記支軸（３）が、一端を支軸（３）の端面に開放させて軸心部に設けた第１の孔（５ａ）と、その第１の孔（５ａ）から放射状に延びて支軸（３）の外周に抜ける少なくとも１つの第２の孔（５ｂ）とで構成される給油孔（５）を備えた請求項１～４のいずれかに記載のギヤアセンブリ。 The support shaft (3) has a first hole (5a) provided in the shaft center portion with one end opened to the end surface of the support shaft (3), and the support shaft extends radially from the first hole (5a). The gear assembly according to any one of claims 1 to 4, further comprising an oil supply hole (5) configured with at least one second hole (5b) extending to the outer periphery of the shaft (3).
  6. 　支軸と玉軸受を含んだ、請求項１～５のいずれか１項に記載のギヤアセンブリで構成されたプラネタリギヤ（１３）と、このプラネタリギヤ（１３）を組み付けたプラネタリキャリア（１４）と、前記プラネタリギヤ（１３）がそれぞれ噛合するサンギヤ（１１）及びリングギヤ（１２）を備えた遊星歯車機構。 A planetary gear (13) comprising the gear assembly according to any one of claims 1 to 5 including a support shaft and a ball bearing, a planetary carrier (14) assembled with the planetary gear (13), A planetary gear mechanism comprising a sun gear (11) and a ring gear (12) with which the planetary gear (13) meshes.
  7. 　請求項６に記載の遊星歯車機構（１０）と、モータケース（２２）、ステータコア（２３）、ロータ（２４）及び出力軸となる回転軸（２５）を備えた電動式のモータ（２１）を組み合わせ、前記遊星歯車機構（１０）を、モータケース（２２）に内蔵し、前記回転軸（２５）を、前記遊星歯車機構（１０）のプラネタリキャリア（１４）に連結し、前記遊星歯車機構（１０）を増速機となした歯車機構内蔵モータ。 An electric motor (21) comprising the planetary gear mechanism (10) according to claim 6, a motor case (22), a stator core (23), a rotor (24), and a rotary shaft (25) serving as an output shaft. In combination, the planetary gear mechanism (10) is built in the motor case (22), the rotating shaft (25) is connected to the planetary carrier (14) of the planetary gear mechanism (10), and the planetary gear mechanism ( 10) A gear mechanism built-in motor which is a gearbox.
  8. 　請求項６に記載の遊星歯車機構（１０）と、モータケース（２２）、ステータコア（２３）、ロータ（２４）及び出力軸となる回転軸（２５）を備えた電動式のモータ（２１）を組み合わせ、前記遊星歯車機構（１０）を、モータケース（２２）に内蔵し、前記回転軸（２５）を、前記遊星歯車機構（１０）のサンギヤ（１１）に連結し、前記遊星歯車機構（１０）を減速機となした歯車機構内蔵モータ。 An electric motor (21) comprising the planetary gear mechanism (10) according to claim 6, a motor case (22), a stator core (23), a rotor (24), and a rotary shaft (25) serving as an output shaft. In combination, the planetary gear mechanism (10) is built in the motor case (22), the rotating shaft (25) is connected to the sun gear (11) of the planetary gear mechanism (10), and the planetary gear mechanism (10 ) Is a gear mechanism built-in motor.
PCT/JP2017/033333 2016-09-15 2017-09-14 Gear assembly, planetary gear mechanism using gear assembly, and motor with built-in gear mechanism WO2018052092A1 (en)

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JP2016-180693 2016-09-15
JP2016180693A JP2018044638A (en) 2016-09-15 2016-09-15 Gear assembly and planetary gear mechanism using the same and gear mechanism incorporated motor

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Publication number Priority date Publication date Assignee Title
JP7006568B2 (en) * 2018-11-20 2022-01-24 トヨタ自動車株式会社 Electric motor

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63139353U (en) * 1987-03-05 1988-09-13
JPH0530540U (en) * 1991-08-13 1993-04-23 有限会社シー・エス・ユー roller
JP2003301909A (en) * 2002-04-04 2003-10-24 Koyo Seiko Co Ltd Toroidal continuously variable transmission
JP2006083986A (en) * 2004-09-17 2006-03-30 Toyota Motor Corp Planetary gear device
JP2013040665A (en) * 2011-08-18 2013-02-28 Ntn Corp Planetary gear device
JP2015059592A (en) * 2013-09-18 2015-03-30 Ntn株式会社 Bearing structure
JP2015525885A (en) * 2012-08-07 2015-09-07 ケーイーエム クッペルス エレクトロメヒャニーク ゲーエムベーハー Gear flow meter

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63139353U (en) * 1987-03-05 1988-09-13
JPH0530540U (en) * 1991-08-13 1993-04-23 有限会社シー・エス・ユー roller
JP2003301909A (en) * 2002-04-04 2003-10-24 Koyo Seiko Co Ltd Toroidal continuously variable transmission
JP2006083986A (en) * 2004-09-17 2006-03-30 Toyota Motor Corp Planetary gear device
JP2013040665A (en) * 2011-08-18 2013-02-28 Ntn Corp Planetary gear device
JP2015525885A (en) * 2012-08-07 2015-09-07 ケーイーエム クッペルス エレクトロメヒャニーク ゲーエムベーハー Gear flow meter
JP2015059592A (en) * 2013-09-18 2015-03-30 Ntn株式会社 Bearing structure

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